JP3755422B2 - Heat pump water heater - Google Patents

Heat pump water heater Download PDF

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Publication number
JP3755422B2
JP3755422B2 JP2001149076A JP2001149076A JP3755422B2 JP 3755422 B2 JP3755422 B2 JP 3755422B2 JP 2001149076 A JP2001149076 A JP 2001149076A JP 2001149076 A JP2001149076 A JP 2001149076A JP 3755422 B2 JP3755422 B2 JP 3755422B2
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Japan
Prior art keywords
hot water
temperature
water
refrigerant
set temperature
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Expired - Fee Related
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JP2001149076A
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Japanese (ja)
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JP2002340400A (en
Inventor
竹司 渡辺
昌宏 尾浜
松本　　聡
吉継 西山
誠一 安木
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Panasonic Corp
Panasonic Holdings Corp
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Panasonic Corp
Matsushita Electric Industrial Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24D—DOMESTIC- OR SPACE-HEATING SYSTEMS, e.g. CENTRAL HEATING SYSTEMS; DOMESTIC HOT-WATER SUPPLY SYSTEMS; ELEMENTS OR COMPONENTS THEREFOR
    • F24D19/00—Details
    • F24D19/10—Arrangement or mounting of control or safety devices
    • F24D19/1006—Arrangement or mounting of control or safety devices for water heating systems
    • F24D19/1051—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water
    • F24D19/1054—Arrangement or mounting of control or safety devices for water heating systems for domestic hot water the system uses a heat pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/10—Control of fluid heaters characterised by the purpose of the control
    • F24H15/174—Supplying heated water with desired temperature or desired range of temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/212—Temperature of the water
    • F24H15/215—Temperature of the water before heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/20—Control of fluid heaters characterised by control inputs
    • F24H15/212—Temperature of the water
    • F24H15/219—Temperature of the water after heating
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/38—Control of compressors of heat pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H15/00—Control of fluid heaters
    • F24H15/30—Control of fluid heaters characterised by control outputs; characterised by the components to be controlled
    • F24H15/375—Control of heat pumps
    • F24H15/385—Control of expansion valves of heat pumps
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
    • F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
    • 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
    • F25B2309/00—Gas cycle refrigeration machines
    • F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
    • F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
    • 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
    • F25B2339/00—Details of evaporators; Details of condensers
    • F25B2339/04—Details of condensers
    • F25B2339/047—Water-cooled condensers
    • 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
    • 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
    • F25B2600/17—Control issues by controlling the pressure of the condenser

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明はヒートポンプ利用給湯装置に関するものである。
【０００２】
【従来の技術】
従来、この種のヒートポンプ利用給湯装置としては、例えば、特開昭５９−１５７７８号公報に記載されているようなものがあった。図１１は前記公報に記載された従来のヒートポンプ利用給湯装置を示すものである。
【０００３】
図１１において、１は圧縮機、２は凝縮器、３は減圧装置、４は蒸発器、５は貯湯槽、６は循環ポンプであり、圧縮機１、凝縮器２、減圧弁３、蒸発器４と連結してヒートポンプ装置を形成する。
【０００４】
【発明が解決しようとする課題】
しかしながら、前記従来の構成では、沸き上げ運転時間の経過とともに貯湯槽５内の湯と水の接する部分で湯水混合層が生じ、その湯水混合層が次第に拡大していく。図１２は、貯湯層内の湯と水の混合層の温度分布を示す。これは、高温湯と低温水の熱伝導および対流により発生するものであり、高温湯から低温水へ伝熱され、その境界部分で高温湯は温度低下し、逆に低温水は温度上昇する。従って、沸き上げ完了近くになると、前記給湯熱交換器に流入する水温は高くなる。そのため、圧縮機の吐出冷媒圧力、吐出冷媒温度が高くなり、モータの巻線温度の上昇など圧縮機の耐久性が課題となるため運転を停止しなくてはならない。よって、貯湯槽の下部は中低温の水を貯水する状態となるため、貯湯槽容量を有効に利用して貯湯することができない。
【０００５】
本発明は、前記従来の課題を解決するもので、運転中に給湯熱交換器に流入する水温が設定温度より高くなったことを検出して、圧縮機の吐出冷媒温度の設定温度を低くして、給湯熱交換器に流入する水温が高温となるまで運転を継続できるようにして、貯湯槽の容積全体に高温水を貯湯するものである。
【０００６】
【課題を解決するための手段】
前記従来の課題を解決するために、本発明のヒートポンプ給湯機は、圧縮機、放熱器、減圧装置、蒸発器を順次接続した冷媒回路と、下部の水を冷媒回路で加熱して上部から貯湯する貯湯槽、循環ポンプ、放熱器と熱交換関係を有する給湯熱交換器を順次接続した給湯回路と、圧縮機の吐出冷媒温度が設定温度Ａとなるように減圧装置の弁開度を制御する冷媒制御手段と、給湯熱交換器出口の湯温が設定温度Ｂとなるように給湯回路の水循環流量を制御する水量制御手段とを有し、前記貯湯槽に給水された水を沸き上げる運転中の沸き上げ完了近くにおいて、前記給湯熱交換器入口の水温が上昇して設定温度Ｃに達すると前記圧縮機の吐出冷媒温度が上昇する場合は、設定温度Ａを低温側へ変更するものである。
【０００７】
これによって、運転中に湯水混合層の中低温水が給湯熱交換器へ流入しはじめると、それにつれて冷媒温度、冷媒圧力が上昇する。そして、給湯熱交換器へ流入する中低温水の温度が急激に上昇するため、圧縮機の吐出冷媒温度も急激に上昇する。従って、給湯熱交換器へ流入しはじめる温水が設定温度Ｃに達すると、圧縮機の吐出冷媒温度の設定温度Ａを下げて、給湯熱交換器に流入する水温が高温となるまで運転して、貯湯槽の容積全体に高温水を貯湯する。
【０００８】
【発明の実施の形態】
請求項１に記載の発明は、圧縮機、放熱器、減圧装置、蒸発器を順次接続した冷媒回路と、下部の水を冷媒回路で加熱して上部から貯湯する貯湯槽、循環ポンプ、放熱器と熱交換関係を有する給湯熱交換器を順次接続した給湯回路と、圧縮機の吐出冷媒温度が設定温度Ａとなるように減圧装置の弁開度を制御する冷媒制御手段と、給湯熱交換器出口の湯温が設定温度Ｂとなるように給湯回路の水循環流量を制御する水量制御手段とを有し、前記貯湯槽に給水された水を沸き上げる運転中の沸き上げ完了近くにおいて、前記給湯熱交換器入口の水温が上昇して設定温度Ｃに達すると前記圧縮機の吐出冷媒温度が上昇する場合は、設定温度Ａを低温側へ変更するものである。運転中に給湯熱交換器入口の水温が設定温度Ｃに達したことを検出して、運転中に設定温度Ｃの湯水混合層の温水が給湯熱交換器へ流入しはじめると、圧縮機の吐出冷媒温度の設定温度Ａを下げて、給湯熱交換器に流入する水温が高温となるまで運転を継続できるようにして、貯湯槽の容積全体に高温水を貯湯する。
【０００９】
請求項２に記載の発明は、前述の構成に加え、給湯熱交換器入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に低温側へ変更する時間間隔を短くするようにしたものであり、夏季などの沸き上げ運転時間が短い場合には、貯湯槽内の湯水の熱交換時間が短いため湯水混合層領域が少ない。そのため、給湯熱交換器に流入する水温が急激に上昇するけれども、圧縮機の吐出冷媒温度の設定温度Ａを低温側に設定変更する時間間隔を短くして圧縮機の吐出冷媒温度の上昇を抑え、給湯熱交換器に流入する水温が高温となるまで運転を継続できるようにして、貯湯槽の容積全体に高温水を貯湯する。
【００１０】
請求項３に記載の発明は、前述の構成に加え、給湯熱交換器入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に下げ、温度低下の幅を大きくするようにしたものであり、沸き上げ完了直後に少量出湯して、再度沸き上げ運転する場合など、貯湯槽下部に給水された水温と沸き上げ湯温の温度差が大きくなるため給湯熱交換器に流入する水温が不連続に急激に変化する。このような急激な水温変化に対して、圧縮機の吐出冷媒温度の設定温度Ａを下げ、その温度低下の幅を大きくして、圧縮機の吐出冷媒温度の異常上昇を防止し、給湯熱交換器に流入する水温が高温となるまで運転を継続できるようにする。
【００１１】
請求項４に記載の発明は、圧縮機、放熱器、減圧装置、蒸発器を順次接続した冷媒回路と、下部の水を前記冷媒回路で加熱して上部から貯湯する貯湯槽、循環ポンプ、前記放熱器と熱交換関係を有する給湯熱交換器を順次接続した給湯回路と、前記圧縮機の吐出冷媒温度が設定温度Ａとなるように前記減圧装置の弁開度を制御する冷媒制御手段と、前記給湯熱交換器出口の湯温が設定温度Ｂとなるように前記給湯回路の水循環流量を制御する水量制御手段とを有し、前記貯湯槽に給水された水を沸き上げる運転中の沸き上げ完了近くにおいて、前記給湯熱交換器入口の水温が上昇して設定温度Ｃに達すると前記圧縮機の吐出冷媒温度が低くなる場合は、設定温度Ａを高温側へ変更することを特徴とするヒートポンプ給湯機であり、この場合には、高圧側は臨界圧力以上で動作して、高効率高温沸き上げの運転をおこなうためには、圧縮機の吐出冷媒温度と吐出冷媒圧力をかなり高温高圧化で運転する。そして、湯水混合層の温水が給湯熱交換器に流入すると、放熱器から流出する冷媒温度が高くなって冷媒の放熱量が低下する。そのため、冷媒と水の平均温度差が小さくなるため、給湯熱交換器出口の湯温を一定とする場合には、放熱器に流入する冷媒温度が低下する。従って、給湯熱交換器に流入する水温が高温になるまで運転を継続して貯湯槽の容積全体に高温水を貯湯することができる。
【００１２】
請求項５に記載の発明は、前述の構成に加え、圧縮機の駆動周波数を可変する駆動制御手段と、給湯熱交換器入口の水温が設定温度Ｃに達したことを検出して、圧縮機の駆動周波数を大きくする制御をおこなう圧縮機制御手段を備え、給湯熱交換器入口の水温が設定温度Ｃに達したことを検出して、圧縮機の駆動周波数を大きくして、吐出冷媒温度を高めて高効率、かつ給湯加熱能力を大きくして貯湯槽の容積全体に高温水を貯湯する。
【００１３】
請求項６に記載の発明は、冷媒回路に封入する冷媒を二酸化炭素とする場合、前述の構成に加え、給湯熱交換器入口の水温が設定温度Ｃに達したことを検出して、圧縮機の冷媒吐出温度の設定温度Ａを高温側に変更し、さらに高温湯で貯湯槽の容積全体を貯湯する。
【００１４】
【実施例】
以下、本発明の実施例について、図面を参照しながら説明する。なお、従来例および各実施例において、同じ構成、同じ動作をするものについては同一符号を付し、一部説明を省略する。
【００１５】
（実施例１）
図１は本発明の実施例１におけるヒートポンプ給湯機の構成図を示すものである。図１において、１は圧縮機、２は放熱器、３は減圧装置、４は蒸発器であり、大気熱あるいは太陽熱を集熱する。そして、圧縮機１、放熱器２、減圧装置３、蒸発器４は順次接続され、フロンＨＦＣ冷媒を封入する冷媒回路を構成する。５は貯湯槽、６は循環ポンプ、７は給湯熱交換器であり、放熱器２と熱交換関係を有する。そして、貯湯５の下部から循環ポンプ６、給湯熱交換器７、貯湯槽５の上部を順次接続した給湯回路を構成する。８は冷媒温度検出手段であり、圧縮機１の吐出冷媒温度を検出する。９は冷媒制御手段であり、冷媒温度検出手段８の検出信号から圧縮機１の吐出冷媒温度が予め設定された設定温度Ａとなるように減圧装置３の弁開度を制御する。１０は湯温検出手段であり、給湯熱交換器７の出口湯温を検出する。１１は水量制御手段であり、給湯熱交換器７出口の湯温が設定温度Ｂとなるように湯温検出手段１０の検出信号と比較しながら給湯回路の水循環流量を制御する。例えば、循環ポンプ６の回転数を可変して水循環流量を制御する。１２は水温検出手段であり、給湯熱交換器７に流入する水温を検出するものであり、給湯熱交換器７の入口、あるいは給湯熱交換器７へ流出する貯湯槽５の下部出口近傍に設けられている。１３は設定温度制御手段であり、運転中に給湯熱交換器７入口の水温が設定温度Ｃに達した後、設定温度Ａを変更する。
【００１６】
以上のように構成されたヒートポンプ給湯機について、以下その動作、作用を説明する。図１において、最初に、貯湯槽５に給水された水を沸き上げる運転について述べる。この場合、圧縮機１から吐出された高温高圧の冷媒は放熱器２に流入し、ここで循環ポンプ６から送られてきた水を加熱する。そして、減圧装置３で減圧されて蒸発器４に流入する。そして、大気熱を吸熱して蒸発ガス化し、圧縮機１にもどる。このサイクルにおいて、外気温度条件、あるいは太陽日射量、給水温度などに対して、圧縮機１の吐出冷媒温度が予め設定された設定温度Ａとなるように冷媒制御手段９が減圧装置３の弁開度を制御する。本発明では、設定温度Ａをおよそ１００℃とする。一方、貯湯槽５の下部から流出した水は循環ポンプ６を介して給湯熱交換器７に流入し、放熱器２を介して設定温度Ｂとなるように昇温して貯湯槽５の上部にたくわえられる。ここで、給湯熱交換器７の出口湯温を湯温検出手段１０が検知し、水量制御手段１１が設定温度Ｂとなるように湯温検出手段１０の検出信号と比較しながら給湯回路の水循環流量を制御する。そして、この運転を継続しながら、貯湯槽５の上部から貯湯し、湯面がしだいに貯湯槽５の下部に下がってくる。この運転中に貯湯槽５内では、上部の湯と下部の低温水の境界で熱伝導による熱交換がおこなわれ、上部の湯温は下がり、下部の水温は上昇する湯水混合層を形成し、この混合層は時間経過とともに拡大する。そして、沸き上げ完了近くになると貯湯槽５内の湯水混合層の水が給湯熱交換器７に流入しはじめて、圧縮機１の吐出冷媒温度が上昇する。そして、水温検出手段１２の検出信号から流入温度が設定温度Ｃに達したことを認識して、設定温度制御手段１３が圧縮機１の吐出冷媒温度の設定温度Ａを下げる。そして、圧縮機１の吐出冷媒温度が変更された設定温度となるように冷媒制御手段９が減圧措置３を制御する。よって、圧縮機の吐出冷媒温度を下げて運転するため、給湯熱交換器に流入する水温が高温になるまで運転できるようになる。従って、圧縮機の耐久性を確保しつつ、貯湯槽の容積全体に高温水を貯湯できる。
【００１７】
また、図２のように、水量制御手段１１は給湯回路に流量制御弁１４を備えて弁開度を可変し、水循環流量を制御しても設定温度Ｂの湯を貯湯することができ、同様の効果が得られる。但し、この場合には、循環ポンプの定格循環流量から弁最小絞りまで流量変化幅は大きくなる利点がある。しかし、低流量時も定格消費電力を費やすため、消費電力量が大きくなる課題がある。
【００１８】
（実施例２）
図３は本発明の実施例２のヒートポンプ給湯機の構成図である。図４は実施例２のヒートポンプ給湯機運転中の貯湯槽内の湯温分布を表わす。図５は湯水混合層域に達した時の圧縮機の吐出冷媒温度、給湯熱交換器出口水温の経時変化を表わし、実線は本発明の温度変化を表わし、破線は従来制御の温度変化を表わすグラフである。図３において、１５は設定温度制御手段であり、給湯熱交換器７入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に低温側へ変更する時間の間隔を短くする。
【００１９】
以上の構成において、その動作、作用について説明する。夏季などの沸き上げ運転時間が短い場合には、図４に表わす如く、湯水の熱交換時間が短いため湯水混合層領域が少ない。そのため、給湯熱交換器７に流入する水温が急激に上昇する。そして、水温検出手段１２の検出信号から給湯熱交換器７への流入温度が設定温度Ｃに達したことを認識して、設定温度制御手段１５が圧縮機１の吐出冷媒温度の設定温度Ａを下げる。そして、図５に表わす如く、圧縮機１の吐出冷媒温度の設定値を下げる設定温度Ａの設定変更をおこなう時間間隔をしだいに短くするため急激な水温上昇に追随できるようになり、吐出冷媒温度の異常上昇が生じない。従って、圧縮機の耐久性を確保しつつ給湯熱交換器に流入する水温が高温となるまで運転を継続でき、貯湯槽の容積全体に高温水を貯湯する。
【００２０】
（実施例３）
図６は本発明の実施例３のヒートポンプ給湯機の構成図である。図７は湯水混合層域に達した時の圧縮機の吐出冷媒温度、給湯熱交換器出口水温の経時変化を表わし、実線は本発明の温度変化を表わし、破線は従来制御の温度変化を表わすグラフである。図６において、１６は設定温度制御手段であり、給湯熱交換器７入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に下げ、温度低下の幅を大きくする。
【００２１】
以上の構成において、その動作、作用について説明する。
【００２２】
沸き上げ完了直後に少量出湯して、再度沸き上げ運転する場合について説明する。この場合、少量出湯すると水道の圧力によって出湯量と同じ水量が貯湯槽下部に給水される。そして、再度沸き上げ運転をおこなうと、給水した水温と沸き上げ直後の湯温の差が大きいため、給湯熱交換器に流入する水温は不連続的に急激に上昇変化する。そのため、水温検出手段１２の検出信号から給湯熱交換器７への流入温度が設定温度Ｃに達したことを認識して、設定温度制御手段１６が圧縮機１の吐出冷媒温度の設定温度Ａを下げる。そして、圧縮機の吐出冷媒温度の設定温度Ａを下げる変更幅を大きくして、急激な水温変化に対しても圧縮機の吐出冷媒温度の異常上昇を防止する。従って、圧縮機の耐久性を確保しつつ給湯熱交換器に流入する水温が高温となるまで運転を継続できるようにする。
【００２３】
（実施例４）
図８は本発明の実施例４のヒートポンプ給湯機の動作を表わす二酸化炭素冷媒の圧力と比エンタルピのグラフである。図９は放熱器で熱交換する際の冷媒温度と水温を表わし、実線が低温の給水温度を加熱する場合を表わし、破線が湯水混合層域に達した中温度の水を加熱する場合を表わす。
【００２４】
以上の構成において、その動作、作用について説明する。
【００２５】
冷媒回路に封入する冷媒を二酸化炭素とするヒートポンプ給湯機は図８で示す如く、高圧側は臨界圧力以上で動作する。そして、圧縮機１が吸入冷媒ａ点から吐出冷媒ｂ点まで圧縮して高温高圧冷媒にして、放熱器２に流入する。ここで循環ポンプ６を介して貯湯槽５から送られてきた水を加熱する。その際、放熱器２を通過する冷媒は放熱しながらｂ点から、給水温度より高温のｃ点まで温度低下する。そして、減圧装置３でｄ点まで減圧されて臨界圧力以下となり蒸発器４に流入する。そして、大気熱を吸熱して蒸発ガス化し、圧縮機１のａ点にもどる。一方、貯湯槽５の下部から流出した水は循環ポンプ６を介して給湯熱交換器７に流入し、放熱器２を介して加熱されて貯湯槽５の上部にたくわえられる。ここで、給湯熱交換器７の出口湯温を湯温検出手段１０が検知し、水量制御手段１１が設定温度Ｂとなるように湯温検出手段１０の検出信号と比較しながら給湯回路の水循環流量を制御する。そして、この運転を継続しながら、貯湯槽５の上部から貯湯し、湯面がしだいに貯湯槽５の下部に下がってくる。この運転中に貯湯槽５内では、上部の湯と下部の低温水の境界で熱伝導による熱交換がおこなわれ、上部の湯温は下がり、下部の水温は上昇する湯水混合層を形成し、この混合層は時間経過とともに拡大する。そして、貯湯槽５内の湯水混合層の水が給湯熱交換器７に流入すると、放熱器２から流出する冷媒温度がｃ’点まで上昇する。ｃ’点の冷媒温度は給湯熱交換器７に流入する水温より当然高い。そのため、放熱量が図８中のＱｃからＱｃ’へ低下する。よって、図９のグラフに表わす如く、冷媒と水の平均温度差がΔｔ１からΔｔ２に小さくなるため、給湯熱交換器７出口の湯温を一定とする場合には、放熱器２に流入する冷媒温度が低下する。すなわち、圧縮機１の吐出冷媒温度が低くなっても設定温度Ｂの湯温が確保できる。例えば、放熱量が約６０％に低下する場合、冷媒と水の温度差が２０ｄｅｇから１２ｄｅｇとなり、放熱器に流入する冷媒温度が８ｄｅｇ低下する。従って、給湯熱交換器に流入する水温が高温になるまで運転を継続できるため貯湯槽の容積全体に高温水を貯湯できる。
【００２６】
そして、給湯熱交換器７入口の水温が設定温度Ｃに達したことを検出して、圧縮機１の吐出冷媒の設定温度Ａの設定値を高温側に変更することによって、圧縮機１の冷媒吐出温度を上げて、さらに高温湯で貯湯槽の容積全体に高温水を貯湯する。
【００２７】
（実施例５）
図１０は本発明の実施例５の冷媒として二酸化炭素を用いたヒートポンプ給湯機の構成図である。図１０において、１７は駆動制御手段であり、圧縮機１の駆動周波数を可変する。１８は圧縮機制御手段であり、給湯熱交換器７入口の水温が設定温度Ｃに達したことを検出して、圧縮機１の駆動周波数を大きくするように駆動制御手段１７に指令する。
【００２８】
以上の構成において、その動作、作用について説明する。給湯熱交換器７入口の水温が設定温度Ｃに達したことを検出して、圧縮機１の駆動周波数が大きくなる。そのため、圧縮機１の圧縮比が大きくなるため吐出冷媒温度が高くなり、給湯熱交換器７の出口水温を高めることができる。また、放熱量（給湯加熱能力）が増大する。従って、短時間で高温の湯を貯湯槽の容積全体に貯湯できるようになる。
【００２９】
【発明の効果】
以上のように、本発明によれば、フロン系の冷媒、あるいは高圧側が臨界圧力以上となる二酸化炭素の冷媒を用いたヒートポンプ給湯機において、沸き上げ完了直前の湯水混合層域の水が高温水になっても給湯運転できるようにして、貯湯槽の容積全体に高温水を貯湯するものである。
【図面の簡単な説明】
【図１】 本発明の実施例１のヒートポンプ給湯機の構成図
【図２】 本発明の実施例１の他のヒートポンプ給湯機の構成図
【図３】 本発明の実施例２のヒートポンプ給湯機の構成図
【図４】 本発明の実施例２のヒートポンプ給湯機運転中の貯湯槽内の湯温分布を表わす図
【図５】 本発明の実施例２のヒートポンプ給湯機の圧縮機の吐出冷媒温度変化を表わすグラフ
【図６】 本発明の実施例３のヒートポンプ給湯機の構成図
【図７】 本発明の実施例３のヒートポンプ給湯機の圧縮機の吐出冷媒温度変化を表わすグラフ
【図８】 本発明の実施例４のヒートポンプ給湯機の冷媒圧力と比エンタルピ線のグラフ
【図９】 本発明の実施例４のヒートポンプ給湯機の放熱器内の冷媒と水の温度変化のグラフ
【図１０】 本発明の実施例５のヒートポンプ給湯機の構成図
【図１１】 従来のヒートポンプ給湯機の構成図
【図１２】 従来のヒートポンプ給湯機運転中の貯湯槽内の湯温分布を表わす図
【符号の説明】
１ 圧縮機
２ 放熱器
３ 減圧装置
４ 蒸発器
５ 貯湯槽
６ 循環ポンプ
７ 給湯熱交換器
８ 冷媒温度検出手段
９ 冷媒制御手段
１０ 湯温検出手段
１１ 水量制御手段
１２ 水温検出手段
１３、１５、１６ 設定温度制御手段
１４ 流量制御弁
１７ 駆動制御手段
１８ 圧縮機制御手段[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat pump hot water supply apparatus.
[0002]
[Prior art]
Conventionally, as this type of heat pump hot water supply apparatus, there has been one as described in, for example, Japanese Patent Application Laid-Open No. 59-15778. FIG. 11 shows a conventional heat pump hot water supply apparatus described in the publication.
[0003]
In FIG. 11, 1 is a compressor, 2 is a condenser, 3 is a pressure reducing device, 4 is an evaporator, 5 is a hot water tank, 6 is a circulation pump, and the compressor 1, the condenser 2, the pressure reducing valve 3, and the evaporator. 4 to form a heat pump device.
[0004]
[Problems to be solved by the invention]
However, in the conventional configuration, as the boiling operation time elapses, a hot and cold mixed layer is formed at a portion where hot water in the hot water tank 5 is in contact with water, and the hot and cold mixed layer gradually expands. FIG. 12 shows the temperature distribution of the mixed layer of hot water and water in the hot water storage layer. This occurs due to heat conduction and convection in hot and cold water, and heat is transferred from the hot water to the low temperature water, and the temperature of the hot water drops at the boundary, and the temperature of the low temperature water rises. Therefore, the temperature of the water flowing into the hot water supply heat exchanger becomes higher when the boiling is near completion. Therefore, since the discharge refrigerant pressure and the discharge refrigerant temperature of the compressor become high and the durability of the compressor becomes a problem such as an increase in the winding temperature of the motor, the operation must be stopped. Therefore, since the lower part of the hot water storage tank is in a state of storing medium-low temperature water, the hot water storage tank capacity cannot be used effectively to store hot water.
[0005]
The present invention solves the above-mentioned conventional problems, and detects that the temperature of the water flowing into the hot water supply heat exchanger during operation is higher than the set temperature, and lowers the set temperature of the discharge refrigerant temperature of the compressor. Thus, the operation can be continued until the temperature of the water flowing into the hot water supply heat exchanger becomes high, and hot water is stored in the entire volume of the hot water storage tank.
[0006]
[Means for Solving the Problems]
In order to solve the above-described conventional problems, the heat pump water heater of the present invention includes a refrigerant circuit in which a compressor, a radiator, a decompression device, and an evaporator are sequentially connected, and water in the lower part is heated by the refrigerant circuit to store hot water from the upper part. A hot water storage circuit that sequentially connects hot water storage tanks, circulation pumps, and heat exchangers that have a heat exchange relationship with a radiator, and the valve opening of the decompression device so that the refrigerant discharge refrigerant temperature becomes a set temperature A During the operation of boiling water supplied to the hot water storage tank, it has refrigerant control means and water amount control means for controlling the water circulation flow rate of the hot water supply circuit so that the hot water temperature at the outlet of the hot water supply heat exchanger becomes the set temperature B. When the water temperature at the inlet of the hot water supply heat exchanger rises and reaches the set temperature C near the completion of boiling, the set temperature A is changed to the low temperature side when the discharged refrigerant temperature of the compressor rises. .
[0007]
Thus, when in the hot and cold water mixing layer in OPERATION begins to flow into the low temperature water to the hot water supply heat exchanger, the refrigerant temperature, the refrigerant pressure rises as it. And since the temperature of the medium-low temperature water which flows into a hot water supply heat exchanger rises rapidly, the discharge refrigerant | coolant temperature of a compressor also rises rapidly. Therefore, when the hot water that starts to flow into the hot water supply heat exchanger reaches the set temperature C, the set temperature A of the refrigerant discharge refrigerant temperature is lowered, and the water temperature flowing into the hot water supply heat exchanger is increased until the temperature becomes high, Hot water is stored in the entire volume of the hot water tank.
[0008]
DETAILED DESCRIPTION OF THE INVENTION
The invention according to claim 1 is a refrigerant circuit in which a compressor, a radiator, a decompression device, and an evaporator are sequentially connected, a hot water storage tank that heats water in the lower part by the refrigerant circuit, and stores hot water from the upper part, a circulation pump, and a radiator A hot water supply circuit sequentially connecting hot water supply heat exchangers having a heat exchange relationship with each other, a refrigerant control means for controlling the valve opening of the decompression device so that the refrigerant discharge temperature of the compressor becomes a set temperature A, and a hot water heat exchanger Water amount control means for controlling the water circulation flow rate of the hot water supply circuit so that the hot water temperature at the outlet becomes the set temperature B, and the hot water supply is near the completion of boiling during the operation of boiling the water supplied to the hot water tank When the coolant temperature of the compressor rises when the water temperature at the heat exchanger inlet rises and reaches the preset temperature C, the preset temperature A is changed to the low temperature side . Detects that the water temperature of the hot water supply heat exchanger inlet has reached the set temperature C during operation, the hot water of the hot and cold water mixing layer of the set temperature C during OPERATION begins to flow into the hot water supply heat exchanger, the compressor The set temperature A of the discharge refrigerant temperature is lowered so that the operation can be continued until the temperature of the water flowing into the hot water supply heat exchanger becomes high, and hot water is stored in the entire volume of the hot water tank.
[0009]
In addition to the above-described configuration, the invention according to claim 2 shortens the time interval for gradually changing the set temperature A to the low temperature side after the water temperature at the hot water supply heat exchanger inlet reaches the set temperature C. However, when the boiling operation time is short such as in summer, the hot water mixing layer region is small because the heat exchange time of the hot water in the hot water tank is short. Therefore, although the temperature of the water flowing into the hot water supply heat exchanger rises rapidly, the time interval for changing the setting temperature A of the compressor discharge refrigerant temperature to the low temperature side is shortened to suppress the rise in the compressor discharge refrigerant temperature. The hot water is stored in the entire volume of the hot water storage tank so that the operation can be continued until the temperature of the water flowing into the hot water heat exchanger becomes high.
[0010]
In addition to the above-described configuration, the invention described in claim 3 is such that after the water temperature at the hot water supply heat exchanger inlet reaches the set temperature C, the set temperature A is lowered stepwise to increase the temperature drop. The temperature difference between the water temperature supplied to the lower part of the hot water storage tank and the boiling water temperature becomes large, such as when a small amount of hot water is discharged immediately after the completion of boiling and the boiling operation is performed again. It changes rapidly and discontinuously. In response to such a sudden change in water temperature, the set temperature A of the refrigerant discharged from the compressor is lowered and the range of the temperature drop is increased to prevent an abnormal rise in the refrigerant discharged from the compressor, and hot water supply heat exchange The operation can be continued until the temperature of the water flowing into the vessel becomes high.
[0011]
The invention according to claim 4 is a refrigerant circuit in which a compressor, a radiator, a decompression device, and an evaporator are sequentially connected, a hot water tank that heats water in the lower part by the refrigerant circuit, and stores hot water from the upper part, a circulation pump, A hot water supply circuit that sequentially connects hot water supply heat exchangers that have a heat exchange relationship with a radiator, and refrigerant control means that controls the valve opening of the decompression device so that the refrigerant discharge temperature of the compressor becomes a set temperature A; Boiling during operation of boiling water supplied to the hot water storage tank, having water amount control means for controlling the water circulation flow rate of the hot water supply circuit so that the hot water temperature at the outlet of the hot water supply heat exchanger becomes a set temperature B Near the completion, when the water temperature at the inlet of the hot water supply heat exchanger rises and reaches a set temperature C, the set temperature A is changed to a high temperature side when the discharged refrigerant temperature of the compressor decreases. In this case , High-pressure side operating in a critical pressure or higher, in order to perform a highly efficient operation hot boiling is to operate the discharged refrigerant temperature and the refrigerant discharge pressure of the compressor significantly at elevated temperature and pressure reduction. And when the hot water of a hot-water mixed layer flows in into a hot-water supply heat exchanger, the refrigerant | coolant temperature which flows out out of a radiator will become high and the thermal radiation amount of a refrigerant | coolant will fall. Therefore, since the average temperature difference between the refrigerant and the water becomes small, the temperature of the refrigerant flowing into the radiator decreases when the hot water temperature at the hot water supply heat exchanger outlet is kept constant. Accordingly, the operation can be continued until the temperature of the water flowing into the hot water supply heat exchanger becomes high, and hot water can be stored in the entire volume of the hot water storage tank.
[0012]
The invention described in claim 5, in addition to the before mentioned construction, a drive control means for varying the driving frequency of the compressor, it is detected that the temperature of the hot water supply heat exchanger inlet has reached the set temperature C, compression Compressor control means for performing control to increase the drive frequency of the compressor, detecting that the water temperature at the inlet of the hot water supply heat exchanger has reached the set temperature C, increasing the drive frequency of the compressor, and discharging refrigerant temperature The hot water is stored in the entire volume of the hot water tank by increasing the efficiency of the hot water supply and increasing the hot water heating capacity.
[0013]
When the refrigerant to be sealed in the refrigerant circuit is carbon dioxide, the invention described in claim 6 detects that the water temperature at the inlet of the hot water supply heat exchanger has reached the set temperature C in addition to the above-described configuration, The set temperature A of the refrigerant discharge temperature is changed to the high temperature side, and the entire volume of the hot water storage tank is stored with hot water.
[0014]
【Example】
Embodiments of the present invention will be described below with reference to the drawings. In addition, in a prior art example and each Example, the same code | symbol is attached | subjected about what has the same structure and the same operation | movement, and description is partially abbreviate | omitted.
[0015]
Example 1
FIG. 1 shows a configuration diagram of a heat pump water heater in Embodiment 1 of the present invention. In FIG. 1, 1 is a compressor, 2 is a radiator, 3 is a decompression device, 4 is an evaporator, and collects atmospheric heat or solar heat. The compressor 1, the radiator 2, the decompressor 3, and the evaporator 4 are sequentially connected to form a refrigerant circuit that encloses the chlorofluorocarbon HFC refrigerant. 5 is a hot water storage tank, 6 is a circulation pump, 7 is a hot water supply heat exchanger, and has a heat exchange relationship with the radiator 2. And the hot water supply circuit which connected the circulation pump 6, the hot water supply heat exchanger 7, and the upper part of the hot water storage tank 5 in order from the lower part of the hot water storage 5 is comprised. Reference numeral 8 denotes a refrigerant temperature detecting means for detecting the refrigerant temperature discharged from the compressor 1. Reference numeral 9 denotes refrigerant control means, which controls the valve opening degree of the decompression device 3 so that the discharge refrigerant temperature of the compressor 1 becomes a preset set temperature A from the detection signal of the refrigerant temperature detection means 8. Reference numeral 10 denotes hot water temperature detection means for detecting the hot water temperature at the outlet of the hot water supply heat exchanger 7. 11 is a water amount control means for controlling the water circulation flow rate of the hot water supply circuit while comparing it with the detection signal of the hot water temperature detection means 10 so that the hot water temperature at the outlet of the hot water supply heat exchanger 7 becomes the set temperature B. For example, the water circulation flow rate is controlled by changing the rotation speed of the circulation pump 6. A water temperature detecting means 12 detects the temperature of the water flowing into the hot water heat exchanger 7 and is provided near the inlet of the hot water heat exchanger 7 or the lower outlet of the hot water tank 5 flowing out of the hot water heat exchanger 7. It has been. Reference numeral 13 denotes a set temperature control means that changes the set temperature A after the water temperature at the inlet of the hot water supply heat exchanger 7 reaches the set temperature C during operation.
[0016]
About the heat pump water heater comprised as mentioned above, the operation | movement and an effect | action are demonstrated below. In FIG. 1, first, an operation for boiling water supplied to the hot water tank 5 will be described. In this case, the high-temperature and high-pressure refrigerant discharged from the compressor 1 flows into the radiator 2 and heats the water sent from the circulation pump 6 here. Then, the pressure is reduced by the pressure reducing device 3 and flows into the evaporator 4. Then, it absorbs atmospheric heat to evaporate and returns to the compressor 1. In this cycle, the refrigerant control means 9 opens the valve of the decompression device 3 so that the discharge refrigerant temperature of the compressor 1 becomes a preset temperature A with respect to the outside air temperature condition, the solar radiation amount, the feed water temperature, or the like. Control the degree. In the present invention, the set temperature A is about 100 ° C. On the other hand, the water flowing out from the lower part of the hot water tank 5 flows into the hot water supply heat exchanger 7 through the circulation pump 6, rises in temperature to the set temperature B through the radiator 2, and enters the upper part of the hot water tank 5. Can be saved. Here, the hot water temperature detecting means 10 detects the hot water temperature at the outlet of the hot water heat exchanger 7, and the water circulation of the hot water supply circuit is compared with the detection signal of the hot water temperature detecting means 10 so that the water amount control means 11 becomes the set temperature B. Control the flow rate. And while continuing this driving | operation, hot water is stored from the upper part of the hot water tank 5, and the hot water surface gradually falls to the lower part of the hot water tank 5. During this operation, in the hot water storage tank 5, heat exchange is carried out at the boundary between the upper hot water and the lower low temperature water, forming a hot water mixing layer in which the upper hot water temperature falls and the lower water temperature rises, This mixed layer expands over time. And when it is near the completion of boiling, the water of the hot water mixed layer in the hot water storage tank 5 begins to flow into the hot water supply heat exchanger 7, and the discharge refrigerant temperature of the compressor 1 rises. Then, it is recognized from the detection signal of the water temperature detection means 12 that the inflow temperature has reached the set temperature C, and the set temperature control means 13 decreases the set temperature A of the discharge refrigerant temperature of the compressor 1. And the refrigerant | coolant control means 9 controls the pressure reduction means 3 so that the discharge refrigerant | coolant temperature of the compressor 1 may become set temperature changed. Therefore, since it operates by lowering the refrigerant discharge refrigerant temperature, it can be operated until the temperature of the water flowing into the hot water supply heat exchanger becomes high. Therefore, hot water can be stored in the entire volume of the hot water tank while ensuring the durability of the compressor.
[0017]
In addition, as shown in FIG. 2, the water amount control means 11 includes a flow rate control valve 14 in the hot water supply circuit to vary the valve opening, and can store hot water at the set temperature B even if the water circulation flow rate is controlled. The effect is obtained. However, in this case, there is an advantage that the flow rate change width increases from the rated circulation flow rate of the circulation pump to the minimum valve throttle. However, since the rated power consumption is consumed even at a low flow rate, there is a problem that the power consumption becomes large.
[0018]
(Example 2)
FIG. 3 is a configuration diagram of a heat pump water heater according to a second embodiment of the present invention. FIG. 4 shows the hot water temperature distribution in the hot water storage tank during operation of the heat pump water heater of the second embodiment. FIG. 5 shows changes over time in the refrigerant discharge refrigerant temperature and the hot water supply heat exchanger outlet water temperature when reaching the hot water / mixing layer region, the solid line shows the temperature change of the present invention, and the broken line shows the temperature change of the conventional control. It is a graph. In FIG. 3, 15 is a set temperature control means, and shortens the time interval for changing the set temperature A to the low temperature stepwise after the water temperature at the inlet of the hot water supply heat exchanger 7 reaches the set temperature C.
[0019]
The operation and action of the above configuration will be described. When the boiling operation time is short in summer and the like, as shown in FIG. Therefore, the temperature of the water flowing into the hot water supply heat exchanger 7 rises rapidly. Then, it is recognized from the detection signal of the water temperature detection means 12 that the inflow temperature to the hot water supply heat exchanger 7 has reached the set temperature C, and the set temperature control means 15 sets the set temperature A of the discharge refrigerant temperature of the compressor 1. Lower. Then, as shown in FIG. 5, the time interval for changing the setting of the set temperature A that lowers the set value of the discharge refrigerant temperature of the compressor 1 is gradually shortened, so that it becomes possible to follow a sudden rise in water temperature. The abnormal rise of the does not occur. Therefore, the operation can be continued until the temperature of the water flowing into the hot water supply heat exchanger becomes high while ensuring the durability of the compressor, and hot water is stored in the entire volume of the hot water tank.
[0020]
Example 3
FIG. 6 is a configuration diagram of a heat pump water heater according to a third embodiment of the present invention. FIG. 7 shows the change over time in the refrigerant discharge refrigerant temperature and the hot water supply heat exchanger outlet water temperature when reaching the hot water / mixing layer region, the solid line shows the temperature change of the present invention, and the broken line shows the temperature change of the conventional control. It is a graph. In FIG. 6, reference numeral 16 denotes a set temperature control means, which lowers the set temperature A step by step after the water temperature at the inlet of the hot water supply heat exchanger 7 reaches the set temperature C, thereby increasing the width of the temperature drop.
[0021]
The operation and action of the above configuration will be described.
[0022]
A case will be described in which a small amount of hot water is discharged immediately after the completion of boiling and the boiling operation is performed again. In this case, when a small amount of hot water is discharged, the same amount of hot water as the amount of hot water is supplied to the lower part of the hot water tank by the pressure of the water supply. When the boiling operation is performed again, the temperature difference between the supplied water temperature and the hot water temperature immediately after the boiling is large, so that the water temperature flowing into the hot water supply heat exchanger changes rapidly and discontinuously. Therefore, it is recognized from the detection signal of the water temperature detection means 12 that the inflow temperature to the hot water supply heat exchanger 7 has reached the set temperature C, and the set temperature control means 16 sets the set temperature A of the discharge refrigerant temperature of the compressor 1. Lower. Then, the change range for lowering the set temperature A of the compressor discharge refrigerant temperature is increased to prevent an abnormal increase in the compressor discharge refrigerant temperature even for a sudden water temperature change. Therefore, the operation can be continued until the temperature of the water flowing into the hot water supply heat exchanger becomes high while ensuring the durability of the compressor.
[0023]
(Example 4)
FIG. 8 is a graph of carbon dioxide refrigerant pressure and specific enthalpy representing the operation of the heat pump water heater of Example 4 of the present invention. FIG. 9 shows the refrigerant temperature and the water temperature when heat is exchanged with a radiator, the solid line represents the case where the low-temperature feed water temperature is heated, and the broken line represents the case where the medium-temperature water reaching the hot and cold mixed layer region is heated. .
[0024]
The operation and action of the above configuration will be described.
[0025]
As shown in FIG. 8, the heat pump water heater using carbon dioxide as the refrigerant sealed in the refrigerant circuit operates on the high pressure side above the critical pressure. Then, the compressor 1 compresses from the suction refrigerant a point to the discharge refrigerant b point to form a high-temperature and high-pressure refrigerant and flows into the radiator 2. Here, the water sent from the hot water tank 5 through the circulation pump 6 is heated. At that time, the temperature of the refrigerant passing through the radiator 2 decreases from the point b to the point c higher than the feed water temperature while radiating heat. Then, the pressure is reduced to point d by the pressure reducing device 3, becomes a critical pressure or less, and flows into the evaporator 4. Then, it absorbs atmospheric heat to evaporate and returns to point a of the compressor 1. On the other hand, the water flowing out from the lower part of the hot water tank 5 flows into the hot water supply heat exchanger 7 through the circulation pump 6, is heated through the radiator 2, and is stored in the upper part of the hot water tank 5. Here, the hot water temperature detecting means 10 detects the hot water temperature at the outlet of the hot water heat exchanger 7, and the water circulation of the hot water supply circuit is compared with the detection signal of the hot water temperature detecting means 10 so that the water amount control means 11 becomes the set temperature B. Control the flow rate. And while continuing this driving | operation, hot water is stored from the upper part of the hot water tank 5, and the hot water surface gradually falls to the lower part of the hot water tank 5. During this operation, in the hot water storage tank 5, heat exchange is carried out at the boundary between the upper hot water and the lower low temperature water, forming a hot water mixing layer in which the upper hot water temperature falls and the lower water temperature rises, This mixed layer expands over time. And if the water of the hot-water mixed layer in the hot water storage tank 5 flows into the hot water supply heat exchanger 7, the refrigerant temperature flowing out from the radiator 2 rises to the point c '. The refrigerant temperature at the point c ′ is naturally higher than the water temperature flowing into the hot water supply heat exchanger 7. Therefore, the amount of heat radiation decreases from Qc in FIG. 8 to Qc ′. Therefore, as shown in the graph of FIG. 9, the average temperature difference between the refrigerant and water decreases from Δt1 to Δt2, so that when the hot water temperature at the outlet of the hot water supply heat exchanger 7 is constant, the refrigerant flowing into the radiator 2 The temperature drops. That is, the hot water temperature of the set temperature B can be secured even when the discharge refrigerant temperature of the compressor 1 is lowered. For example, when the heat dissipation amount is reduced to about 60%, the temperature difference between the refrigerant and water is changed from 20 deg to 12 deg, and the refrigerant temperature flowing into the radiator is reduced by 8 deg. Therefore, since the operation can be continued until the temperature of the water flowing into the hot water heat exchanger becomes high, hot water can be stored in the entire volume of the hot water tank.
[0026]
Then, by detecting that the water temperature at the inlet of the hot water supply heat exchanger 7 has reached the set temperature C, and changing the set value of the set temperature A of the refrigerant discharged from the compressor 1 to the high temperature side, the refrigerant of the compressor 1 Raise the discharge temperature and store hot water in the entire volume of the hot water tank with hot water.
[0027]
(Example 5)
FIG. 10 is a configuration diagram of a heat pump water heater using carbon dioxide as a refrigerant in Example 5 of the present invention. In FIG. 10, reference numeral 17 denotes drive control means, which varies the drive frequency of the compressor 1. Reference numeral 18 denotes compressor control means that detects that the water temperature at the inlet of the hot water supply heat exchanger 7 has reached the set temperature C and instructs the drive control means 17 to increase the drive frequency of the compressor 1.
[0028]
The operation and action of the above configuration will be described. By detecting that the water temperature at the inlet of the hot water supply heat exchanger 7 has reached the set temperature C, the drive frequency of the compressor 1 increases. Therefore, since the compression ratio of the compressor 1 is increased, the discharge refrigerant temperature is increased, and the outlet water temperature of the hot water supply heat exchanger 7 can be increased. Moreover, the amount of heat release (hot water supply heating capacity) increases. Therefore, hot water can be stored in the entire volume of the hot water tank in a short time.
[0029]
【The invention's effect】
As described above, according to the present invention, in a heat pump water heater using a CFC-based refrigerant or a carbon dioxide refrigerant whose high pressure side is equal to or higher than the critical pressure, the water in the hot water / mixed layer area immediately before the completion of boiling is high-temperature water. The hot water supply operation can be performed even if it becomes, and hot water is stored in the entire volume of the hot water tank.
[Brief description of the drawings]
1 is a configuration diagram of a heat pump water heater according to a first embodiment of the present invention. FIG. 2 is a configuration diagram of another heat pump water heater according to the first embodiment of the present invention. FIG. 3 is a heat pump water heater according to a second embodiment of the present invention. FIG. 4 is a view showing a hot water temperature distribution in a hot water storage tank during operation of the heat pump water heater of Embodiment 2 of the present invention. FIG. 5 is a refrigerant discharged from a compressor of the heat pump water heater of Embodiment 2 of the present invention. FIG. 6 is a configuration diagram of a heat pump water heater according to a third embodiment of the present invention. FIG. 7 is a graph illustrating a change in refrigerant temperature discharged from the compressor of the heat pump water heater according to the third embodiment of the present invention. FIG. 9 is a graph of refrigerant pressure and specific enthalpy line of the heat pump water heater of Example 4 of the present invention. FIG. 9 is a graph of temperature change of refrigerant and water in the radiator of the heat pump water heater of Example 4 of the present invention. A heat pump according to a fifth embodiment of the present invention Fig. 11 is a block diagram of a conventional heat pump water heater. Fig. 12 is a diagram showing the temperature distribution in a hot water tank during operation of a conventional heat pump water heater.
DESCRIPTION OF SYMBOLS 1 Compressor 2 Radiator 3 Pressure reducing device 4 Evaporator 5 Hot water storage tank 6 Circulation pump 7 Hot water supply heat exchanger 8 Refrigerant temperature detection means 9 Refrigerant control means 10 Hot water temperature detection means 11 Water quantity control means 12 Water temperature detection means 13, 15, 16 Setting temperature control means 14 Flow rate control valve 17 Drive control means 18 Compressor control means

Claims (6)

圧縮機、放熱器、減圧装置、蒸発器を順次接続した冷媒回路と、下部の水を前記冷媒回路で加熱して上部から貯湯する貯湯槽、循環ポンプ、前記放熱器と熱交換関係を有する給湯熱交換器を順次接続した給湯回路と、前記圧縮機の吐出冷媒温度が設定温度Ａとなるように前記減圧装置の弁開度を制御する冷媒制御手段と、前記給湯熱交換器出口の湯温が設定温度Ｂとなるように前記給湯回路の水循環流量を制御する水量制御手段とを有し、前記貯湯槽に給水された水を沸き上げる運転中の沸き上げ完了近くにおいて、前記給湯熱交換器入口の水温が上昇して設定温度Ｃに達すると前記圧縮機の吐出冷媒温度が上昇する場合は、設定温度Ａを低温側へ変更することを特徴とするヒートポンプ給湯機。A refrigerant circuit in which a compressor, a radiator, a decompression device, and an evaporator are sequentially connected, a hot water storage tank that heats water in the lower part by the refrigerant circuit and stores hot water from the upper part, a circulation pump, and a hot water supply having a heat exchange relationship with the radiator A hot water supply circuit in which heat exchangers are sequentially connected, a refrigerant control means for controlling the valve opening of the decompression device so that the discharge refrigerant temperature of the compressor becomes a set temperature A, and the hot water temperature at the outlet of the hot water supply heat exchanger Water amount control means for controlling the water circulation flow rate of the hot water supply circuit so that the water temperature becomes a set temperature B, and the hot water supply heat exchanger is near the completion of boiling during the operation of boiling the water supplied to the hot water storage tank A heat pump water heater characterized by changing the set temperature A to a low temperature side when the discharge refrigerant temperature of the compressor rises when the water temperature at the inlet rises and reaches a set temperature C. 設定温度制御手段は給湯熱交換器入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に低温側へ変更する時間の間隔を短くする請求項１記載のヒートポンプ給湯機。  The heat pump water heater according to claim 1, wherein the set temperature control means shortens the time interval for changing the set temperature A to the low temperature stepwise after the water temperature at the inlet of the hot water supply heat exchanger reaches the set temperature C. 設定温度制御手段は給湯熱交換器入口の水温が設定温度Ｃに達してから設定温度Ａを段階的に下げ、温度低下の幅を大きくする請求項１または２記載のヒートポンプ給湯機。  The heat pump water heater according to claim 1 or 2, wherein the set temperature control means lowers the set temperature A stepwise after the water temperature at the inlet of the hot water supply heat exchanger reaches the set temperature C to increase the width of the temperature drop. 圧縮機、放熱器、減圧装置、蒸発器を順次接続した冷媒回路と、下部の水を前記冷媒回路で加熱して上部から貯湯する貯湯槽、循環ポンプ、前記放熱器と熱交換関係を有する給湯熱交換器を順次接続した給湯回路と、前記圧縮機の吐出冷媒温度が設定温度Ａとなるように前記減圧装置の弁開度を制御する冷媒制御手段と、前記給湯熱交換器出口の湯温が設定温度Ｂとなるように前記給湯回路の水循環流量を制御する水量制御手段とを有し、前記貯湯槽に給水された水を沸き上げる運転中の沸き上げ完了近くにおいて、前記給湯熱交換器入口の水温が上昇して設定温度Ｃに達すると前記圧縮機の吐出冷媒温度が低くなる場合は、設定温度Ａを高温側へ変更することを特徴とするヒートポンプ給湯機。A refrigerant circuit in which a compressor, a radiator, a decompression device, and an evaporator are sequentially connected, a hot water storage tank that heats water in the lower part by the refrigerant circuit and stores hot water from the upper part, a circulation pump, and a hot water supply having a heat exchange relationship with the radiator A hot water supply circuit in which heat exchangers are sequentially connected, a refrigerant control means for controlling the valve opening of the decompression device so that the discharge refrigerant temperature of the compressor becomes a set temperature A, and the hot water temperature at the outlet of the hot water supply heat exchanger Water amount control means for controlling the water circulation flow rate of the hot water supply circuit so that the water temperature becomes a set temperature B, and the hot water supply heat exchanger is near the completion of boiling during the operation of boiling the water supplied to the hot water storage tank A heat pump water heater characterized by changing the set temperature A to a high temperature side when the discharge refrigerant temperature of the compressor decreases when the water temperature at the inlet rises and reaches a set temperature C. 圧縮機の駆動周波数を可変する駆動制御手段と、給湯熱交換器入口の水温が設定温度Ｃに達したことを検出して、前記圧縮機の駆動周波数を大きくする制御をおこなう圧縮機制御手段を備えた請求項１または４記載のヒートポンプ給湯機。  Drive control means for varying the drive frequency of the compressor, and compressor control means for performing control to increase the drive frequency of the compressor by detecting that the water temperature at the inlet of the hot water supply heat exchanger has reached the set temperature C The heat pump water heater of Claim 1 or 4 provided. 冷媒回路に封入する冷媒を二酸化炭素とする請求項１〜５いずれか１項に記載のヒートポンプ給湯機。  The heat pump water heater according to any one of claims 1 to 5, wherein the refrigerant sealed in the refrigerant circuit is carbon dioxide.
JP2001149076A 2001-05-18 2001-05-18 Heat pump water heater Expired - Fee Related JP3755422B2 (en)

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KR100770375B1 (en) 2005-04-21 2007-10-25 주식회사 누리앤텍 Chiller
JP4533393B2 (en) * 2007-03-06 2010-09-01 三菱電機株式会社 Water heater
JP5536013B2 (en) 2011-11-11 2014-07-02 三菱重工業株式会社 Hot water heating system, control device and control method
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