JP3915538B2 - Water heater - Google Patents

Water heater Download PDF

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Publication number
JP3915538B2
JP3915538B2 JP2002042928A JP2002042928A JP3915538B2 JP 3915538 B2 JP3915538 B2 JP 3915538B2 JP 2002042928 A JP2002042928 A JP 2002042928A JP 2002042928 A JP2002042928 A JP 2002042928A JP 3915538 B2 JP3915538 B2 JP 3915538B2
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Japan
Prior art keywords
hot water
compressor
refrigerant
water
expander
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Expired - Fee Related
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JP2002042928A
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JP2003240341A (en
Inventor
克己 鉾谷
道雄 森脇
日出樹 原
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Daikin Industries Ltd
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Daikin Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
    • 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

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

Description

【０００１】
【発明の属する技術分野】
この発明は、給湯機に関するものである。
【０００２】
【従来の技術】
従来の給湯機としては、図６に示すように、熱源側サイクル８１と、給湯側サイクル８２とを備えるものがある。熱源側サイクル８１は冷媒回路を備え、この冷媒回路は、圧縮機８３に、順次、水熱交換器８４と、膨張弁８５と、空気熱交換器８６等が接続されて構成される。また、給湯側サイクル８２は、貯湯タンク８７と循環路８８とを備える。そして、この循環路８８に水循環用ポンプ８９と熱交換路９０とが介設されている。この場合、熱交換路９０は水熱交換器８４にて構成される。
【０００３】
冷媒回路の冷媒としては、近年、環境上の問題等から、超臨界で使用する超臨界冷媒（例えば、炭酸ガス）を用いる場合がある。従って、この炭酸ガスを使用した単純サイクルでは、モリエル線図が図７に示すものとなる。
【０００４】
【発明が解決しようとする課題】
ところで、上記給湯機では、圧縮機８３を駆動させると共に、ポンプ８９を駆動（作動）させると、給湯側サイクル８２においては、貯湯タンク８７の取水口から貯溜水（温湯）が循環路８８に流出し、これが熱交換路９０を流通して、湯入口から貯湯タンク８７の上部に返流される。
【０００５】
また、熱源側サイクル８１においては、図７に示すように、▲１▼の状態の高圧冷媒が圧縮機８３から吐出され、この高圧冷媒が水熱交換器８４に導入される。水熱交換器８４では、熱交換路９０と通過する水と熱交換を行う。これによって、この通過する水は加熱される（沸き上げられる）。そして、この熱交換により、高圧冷媒は水に対して放熱し、そのエンタルピが▲１▼から▲２▼の状態にまで低下する。この▲２▼の状態の高圧冷媒は、膨張弁８５へ送られる。この膨張弁８５では、高圧冷媒が減圧され、その圧力が▲２▼から▲３▼の状態まで低下する。そして、この▲３▼の状態の冷媒は、空気熱交換器８６へ導入される。空気熱交換器８６では、この低圧冷媒が空気と熱交換を行う。この熱交換により、低圧冷媒は吸熱して蒸発して、そのエンタルピが▲３▼の状態から▲４▼の状態にまで増大する。この▲４▼の状態の低圧冷媒が圧縮機８３へ送られる。
【０００６】
このため、超臨界で使用する超臨界冷媒（例えば、炭酸ガス）を用いる場合には、▲３▼と▲４▼とのエンタルピ差は小さく冷凍サイクル効率が悪いことになっていた。従って、大量の湯の沸き上げを必要とする給湯機では、大型化され、製造コスト及びランニングコスト高となっていた。
【０００７】
この発明は、上記従来の欠点を解決するためになされたものであって、その目的は、ＣＯＰが向上し、省エネ、電気料金の低減を図れる給湯機を提供することにある。
【０００８】
【課題を解決するための手段】
そこで請求項１の給湯機は、冷媒に超臨界で使用する超臨界冷媒を用いた冷媒回路にて、温湯を沸き上げる給湯機であって、下部側に設けた給水口から水道水が供給され、上部側に設けた給湯口から高温の温湯を出湯する貯湯タンク３を設け、貯湯タンク３の取水口４からの貯溜水が循環路６の熱交換路８を流通し、これによって高温冷媒と循環路６の循環水とで熱交換が行われて循環水が加熱されると共に、湯入口５から貯湯タンク３に返流され、また、この貯湯タンク３の湯が床暖パネル５４を加熱して貯湯タンク３に戻る床暖房を行うべく構成して成り、さらに上記冷媒回路に膨張機１２を備え、この膨張機１２で発生した動力の回収を可能としたことを特徴としている。
【０００９】
請求項１の給湯機では、冷媒回路に膨張機１２を備えているので、冷凍サイクルの膨張過程が等エントロピー変化となり、この膨張機１２で発生した動力の回収が可能となると共に、蒸発能力が増大する。これによって、ＣＯＰが向上する。さらに、冷媒に超臨界で使用する超臨界冷媒を用いるので、オゾン層の破壊、環境汚染等の問題がなく、地球環境にやさしい給湯機となる。また、この給湯機では、効率良く沸き上げた湯を、床暖房に使用するので、効率のよい床暖房を行うことができる。
【００１０】
請求項２の給湯機は、上記動力を、上記冷媒回路の圧縮機１０に入力することを特徴としている。
【００１１】
上記請求項２の給湯機では、膨張機１２で発生した動力を、上記冷媒回路の圧縮機に入力することができるので、圧縮機１０を駆動させる外部入力を低減することができる。これによって、膨張機構に膨張弁を使用したものと同一の能力を発揮させる場合には、圧縮機１０の小型化を図ることができる。
【００１２】
請求項３の給湯機は、上記膨張機１２と圧縮機１０とは共通の駆動軸を有し、この膨張機１２で発生した動力を上記駆動軸１９を介して圧縮機１０に伝達することを特徴としている。
【００１３】
上記請求項３の給湯機では、膨張機１２で発生した動力を、膨張機１２と圧縮機１０との共通の駆動軸１９にて圧縮機１０に伝達するので、膨張機１２で発生した動力を圧縮機１０に確実に伝達することができる。
【００１６】
請求項４の給湯機は、上記冷媒回路にて沸き上げられた温湯を、浴槽等への給湯と、床暖房とに使用することを特徴としている。
【００１７】
上記請求項４の給湯機では、効率良く沸き上げた湯を、浴槽等への給湯と、床暖房に使用するので、効率のよい給湯及び床暖房を行うことができる。
【００１８】
【発明の実施の形態】
次に、この発明の給湯機の具体的な実施の形態について、図面を参照しつつ詳細に説明する。図１はこの給湯機の簡略図を示す。この給湯機は、給湯側サイクル１と熱源側サイクル２とを備える。給湯側サイクル１は、貯湯タンク３を備え、この貯湯タンク３に貯湯された温湯が図示省略の浴槽等に供給される。すなわち、貯湯タンク３には、その下部側に給水口（図示省略）が設けられると共に、その上部側に給湯口（図示省略）が設けられている。そして、給水口から貯湯タンク３に水道水が供給され、給湯口から高温の温湯が出湯される。また、貯湯タンク３には、その下部側に取水口４が開設されると共に、その上部側に湯入口５が開設され、取水口４と湯入口５とが循環路６にて連結されている。そして、この循環路６に水循環用ポンプ７と熱交換路８とが介設されている。
【００１９】
そして、加熱側サイクル（ヒートポンプ式加熱源）２は冷媒回路を備え、この冷媒回路は、圧縮機１０と、熱交換路８を構成する水熱交換器１１と、減圧機構としての膨張機１２と、空気熱交換器１３とを順に接続して構成される。すなわち、圧縮機１０の吐出管１４を水熱交換器１１に接続し、水熱交換器１１と膨張機１２とを冷媒通路１５にて接続し、膨張機１２と空気熱交換器１３とを冷媒通路１６にて接続し、空気熱交換器１３と圧縮機１０と冷媒通路１７にて接続している。また、冷媒としては、冷媒に超臨界で使用する超臨界冷媒（例えば、炭酸ガス、その他、エチレン、エタン、酸化窒素等）を用いる。
【００２０】
ところで、上記冷媒回路では、圧縮機１０と膨張機１２とが一体とされた圧縮・膨張ユニット体１８が使用されている。すなわち、圧縮・膨張ユニット体１８は、図２に示すように、冷媒を臨界圧以上に圧縮して送り出す圧縮機１０と、冷媒を膨張させる膨張機１２と、圧縮機１０及び膨張機１２に駆動軸１９を通じて動力を供給する電動機（モータ）２０とがケーシングＡ内に密封状態で収納されたものである。このため、圧縮機１０、電動機２０、及び膨張機１２はこの共通の駆動軸１９により連結されている。
【００２１】
この場合、ケーシングＡの内部が、圧縮機１０及び電動機２０側の第１空間部２１と、膨張機１２側の第２空間部２２とに断熱材２３等にて区画されている。そして、圧縮機１０としては、いわゆる揺動ピストン型ロータリ圧縮機にて構成され、第１・第２シリンダ機構２４、２５を備える。すなわち、第１・第２シリンダ機構２４、２５は、それぞれ、上記駆動軸１９に装着されるクランク軸２６、２７と、このクランク軸２６、２７に外嵌されるピストン２８、２９と、このピストン２８、２９が収納されるシリンダ室３０、３１を有するシリンダ３２、３３とを備える。
【００２２】
第１シリンダ機構２４のシリンダ３２は、シリンダ本体３４と、このシリンダ本体３４の一方の端面に装着される蓋部材３５と、シリンダ本体３４の他方の端面に装着される介在体３６等にて構成される。この蓋部材３５は上記駆動軸１９の一端部を支持している。また、第２シリンダ機構２５のシリンダ３３は、シリンダ本体３８と、上記介在体３６と、シリンダ本体３８のモータ２０側の端面に装着される蓋部材３９等にて構成される。そして、各シリンダ本体３４、３８には吸入ポート４０、４１が連設されている。
【００２３】
次に、膨張機１２は、この場合、揺動ピストン型膨張機にて構成される。すなわち、上記駆動軸１９に装着されるクランク軸４３と、このクランク軸４３に外嵌されるピストン４４と、このピストン４４が収納されるシリンダ室４５を有するシリンダ４６とを備える。シリンダ４６は、シリンダ本体４７と、上記駆動軸１９の他端部を支持する支持体４８と、断熱材２３側の仕切プレート４９等で構成することができる。また、シリンダ本体４７には吐出ポート５０が連設され、さらに、シリンダ室４５には吸入管５１が接続されている。
【００２４】
上記のように構成された圧縮・膨張ユニット体１８の圧縮機１０は、モータ２０によって駆動される。すなわち、駆動軸１９を回転駆動させることによって、この駆動軸１９に連設されたクランク軸２６、２７を回動させて、ピストン２８、２９をシリンダ室３０、３１内で揺動運動をさせる。そのため、この揺動運動に従って吸入ポート４０、４１からシリンダ室３０、３１内に冷媒を吸入し、この冷媒を、このシリンダ室３０、３１でピストン２８、２９が揺動することによって、臨界圧力以上の所定圧力まで圧縮し、この高温高圧となった冷媒を、ケーシングＡに設けられた吐出ポート４２から吐出配管１４へと吐出する。
【００２５】
また、膨張機１２では、駆動軸１９を回転駆動させることによって、この駆動軸１９に連設されたクランク軸４３を回動させて、ピストン４４をシリンダ室４５内で揺動運動をさせる。そのため、この揺動運動に従って吸入管５２からシリンダ室４５内に冷媒を吸入し、この冷媒を、このシリンダ室４５でピストン４４が揺動することによって、冷媒を膨張させ、その膨張した冷媒を吐出ポート５０から冷媒通路１６へ流出させる。
【００２６】
上記のように構成された給湯機によれば、圧縮機１０を駆動させる（モータ２０を通電することによって、駆動軸１９を回転駆動させる）と共に、水循環用ポンプ１３を駆動（作動）させると、圧縮機１０からの高圧高温の冷媒が水熱交換器１１に流入すると共に、貯湯タンク３の取水口４からの貯溜水（低温水）が循環路６の熱交換路８を流通する。これによって、高圧高温の冷媒と循環路６の循環水とで熱交換が行われ、この循環水は加熱され（沸き上げられ）、湯入口５から貯湯タンク３に返流（流入）され、貯湯タンク３に高温の温湯を貯湯することができる。
【００２７】
この際の冷媒回路の冷凍サイクルは図３のようになる。すなわち、▲１▼の状態の高圧冷媒が圧縮機１０から吐出され、この高圧冷媒が水熱交換器１１に導入される。水熱交換器１１では熱交換路１４と通過する水との熱交換を行う。この熱交換により、高圧冷媒は水に対して放熱し、そのエンタルピが▲１▼から▲２▼の状態にまで低下する。この▲２▼の状態の高圧冷媒は、膨張機１２へ送られる。この膨張機１２では、高圧冷媒が減圧され、その圧力が▲２▼から▲３▼´の状態まで低下する。この際、膨張機構として膨張機１２を使用しているので、等エントロピー変化となって、この▲３▼´と▲３▼（▲３▼は、膨張機１２を使用せずに膨張弁を使用した減圧状態である）のエンタルピ差の動力回収が可能となる。そして、この▲３▼´の状態の冷媒は、空気熱交換器１３へ導入される。空気熱交換器１３では、この低圧冷媒が空気と熱交換を行う。この熱交換により、低圧冷媒は吸熱して蒸発してそのエンタルピが▲３▼´の状態から▲４▼の状態にまで増大する。この▲４▼の状態の低圧冷媒が圧縮機１０へ送られる。なお、図３の網掛け部は単純サイクルの場合を示している。
【００２８】
この場合、上記動力回収は、上記駆動軸１９によって圧縮機１０へ伝達され、この圧縮機１０の駆動力に伝達される。すなわち、圧縮機１０としては、図３に示すように、▲４▼から▲１▼までの入力を必要とし、このうち、▲３▼´から▲３▼の差分を、回収して▲４▼から▲４▼´までの入力値として圧縮機１０の入力に使用することができ、圧縮機１０への外部からの入力を低減することができる。このため、ＣＯＰが向上して、省エネ、電気料金の低減を図ることができる。しかも、蒸発能力も増加するので、膨張弁を使用したものよりも小型の圧縮機を使用しても、同一の能力を得ることができ、製造コスト及びランニングコストの低減を図ることができる。
【００２９】
次に、図４は、図１に示した給湯機の簡略図に床暖房ユニット５３を付加したこの発明の実施の形態を示し、この場合、貯湯タンク３に貯湯された湯を、床暖房に使用している。すなわち、この給湯機は、床暖パネル５２を有する床暖房ユニット５３を備える。床暖パネル５２の内部には、循環パイプ５４が配設され、この循環パイプ５４の入口５４ａに往き配管５６が接続され、循環パイプ５４の出口５４ｂに戻り配管５７が接続されている。また、往き配管５６は貯湯タンク３の上部の給湯口５８に接続され、戻り配管５７は貯湯タンク３の下部の返流口５９に接続されている。そして、往き配管５６に循環用ポンプ６０が介設されている。なお、他の構成は、図１に示した空気調和機と同様であるので、同一部分を同一の符号で示してその説明を省略する。
【００３０】
従って、循環用ポンプ６０を駆動することによって、貯湯タンク３の湯が給湯口５８から流出して、往き配管５６を介して循環パイプ５４を流れ、戻り配管５７を介して返流口５９から貯湯タンク３に戻る。この際、この循環パイプ５４を流れる湯によって、床暖パネル５２が暖められ、床暖房を行うことができる。
【００３１】
従って、この図４の給湯機では、給湯側ユニット１及び熱源側ユニット２は図１と同様の構成であるので、給湯機として、ＣＯＰが向上して、省エネ、電気料金の低減を図ることができる。しかも、蒸発能力も増加するので、膨張弁を使用したものよりも小型の圧縮機を使用しても、同一の能力を得ることができ、製造コスト及びランニングコストの低減を図ることができる。そして、このように効率良く沸き上げた湯を床暖房に利用することができ、全体として、高効率のシステムを構成することができる。ところで、現状の電気料金は深夜（例えば、２３時から７時までの時間帯）の電気料金単価が昼間に比べて安価に設定されているので、この貯湯タンク３に湯を貯めるための運転をこの深夜に行えば、節電を図ることができる。
【００３２】
また、図５に示すように、往き配管５６等に浴槽等へ給湯を行う配管６１を接続することによって、床暖房に加え、浴槽等への給湯（以下、単に給湯と呼ぶ場合がある）も可能となる。この場合、往き配管５６において、配管６１の合流部６２よりも下流側に開閉バルブ６３を介設すると共に、配管６１に開閉バルブ６４を介設している。これによって、床暖房のみを行う場合と、給湯のみを行う場合と、床暖房及び給湯を行う場合とに切換ることができる。なお、他の構成は、図１に示した空気調和機と同様であるので、同一部分を同一の符号で示してその説明を省略する。
【００３３】
すなわち、開閉バルブ６３を開状態とすると共に、開閉バルブ６４を閉状態とすれば、床暖房のみを行うことができ、開閉バルブ６３を閉状態とすると共に、開閉バルブ６４を開状態とすれば、給湯のみを行うことができ、開閉バルブ６３、６４を開状態とすれば、床暖房及び給湯を行うことができる。
【００３４】
従って、この図５の給湯機によれば、上記図４の給湯機と同様、給湯機として、ＣＯＰが向上して、省エネ、電気料金の低減を図ることができる。しかも、蒸発能力も増加するので、膨張弁を使用したものよりも小型の圧縮機を使用しても、同一の能力を得ることができ、製造コスト及びランニングコストの低減を図ることができる。しかも、このように効率良く沸き上げた湯を床暖房及び浴槽等への給湯に利用することができ、全体として、きわめて高効率のシステムを構成することができる。そして、この床暖房及び給湯に使用する湯を深夜に沸き上げておけば、電気料金を大幅に節約することができ、ユーザにとっては好適の給湯機となる。なお、図５の給湯機に給湯には、台所や洗面所等への給湯も含まれる。
【００３５】
以上にこの発明の具体的な実施の形態について説明したが、この発明は上記形態に限定されるものではなく、この発明の範囲内で種々変更して実施することができる。例えば、膨張機１２として、圧縮機１０と駆動軸１９が共通化されていないものであってもよい。すなわち、膨張機１２で発生した動力を、一旦、電気エネルギに変換して取出し、この電気エネルギを圧縮機１０の駆動電力として入力する等の構成であってもよい。また、膨張機１２としては、スクロール式の膨張機であってもよい。ここで、スクロール式の膨張機とは、固定スクロールと、旋回スクロールとを備えたものであり、その流入口から高圧の冷媒が流入すると、冷媒は旋回スクロールに旋回動力を生じさせながら次第に減圧膨張し、その流出口から流出する。このため、このようなスクロール式の膨張機でも発生した動力を、圧縮機１へ伝達して、この圧縮機１の駆動に利用することができるようにすればよい。さらに、膨張機１２としては、その他、歯車型、スクリュ−型等の各種の膨張機も使用することができる。なお、圧縮機１０としても、スクロール式やスクリュ−式等の各種の圧縮機を使用することができる。
【００３６】
【発明の効果】
請求項１の給湯機によれば、この膨張機で発生した動力の回収が可能となると共に、蒸発能力が増大する。これによって、ＣＯＰが向上して、無駄のない効率のよい運転が可能となる。さらに、冷媒に超臨界で使用する超臨界冷媒を用いるので、オゾン層の破壊、環境汚染等の問題がなく、地球環境にやさしい給湯機となる。また、この給湯機によれば、効率良く沸き上げた湯を、床暖房に使用するので、効率のよい床暖房を行うことができる。すなわち、給湯機として高効率のシステムを構成することができ、ランニングコストの低減を図ることができる。
【００３７】
請求項２の給湯機によれば、圧縮機を駆動させる外部入力を低減することができる。これによって、膨張機構に膨張弁を使用したものと同一の能力を発揮させる場合には、圧縮機の小型化を図ることができ、製造コスト及びランニングコストの低減を達成できる。
【００３８】
請求項３の給湯機によれば、膨張機で発生した動力を確実に圧縮機に伝達することができる。これによって、より効率の良い運転が可能となって、省エネ、電気料金の低減を図ることができる。
【００４０】
請求項４の給湯機によれば、効率良く沸き上げた湯を、浴槽等への給湯と、床暖房に使用するので、効率のよい給湯及び床暖房を行うことができる。給湯機として高効率のシステムを構成することができ、ランニングコストの低減を図ることができる。しかも、ユーザは給湯及び床暖房にて快適に過ごすことができる。
【図面の簡単な説明】
【図１】この発明の給湯機の実施の形態を示す簡略図である。
【図２】上記給湯機の圧縮機と膨張機の断面図である。
【図３】上記給湯機のモリエル線図である。
【図４】 図１の給湯機に対して床暖房ユニットを付設したこの発明の給湯機の実施の形態を示す簡略図である。
【図５】この発明の給湯機の別の実施の形態を示す簡略図である。
【図６】従来の給湯機の簡略図である。
【図７】従来の給湯機のモリエル線図である。
【符号の説明】
１０ 圧縮機
１２ 膨張機
１９ 駆動軸[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a water heater.
[0002]
[Prior art]
As a conventional hot water heater, there is one provided with a heat source side cycle 81 and a hot water supply side cycle 82 as shown in FIG. The heat source side cycle 81 includes a refrigerant circuit, and this refrigerant circuit is configured by sequentially connecting a water heat exchanger 84, an expansion valve 85, an air heat exchanger 86, and the like to a compressor 83. The hot water supply side cycle 82 includes a hot water storage tank 87 and a circulation path 88. A water circulation pump 89 and a heat exchange path 90 are interposed in the circulation path 88. In this case, the heat exchange path 90 is configured by a water heat exchanger 84.
[0003]
In recent years, a supercritical refrigerant (for example, carbon dioxide gas) used in a supercritical state may be used as a refrigerant in the refrigerant circuit due to environmental problems. Therefore, in a simple cycle using carbon dioxide, the Mollier diagram is as shown in FIG.
[0004]
[Problems to be solved by the invention]
By the way, in the hot water supply apparatus, when the compressor 83 is driven and the pump 89 is driven (actuated), the stored water (hot water) flows out from the water intake port of the hot water storage tank 87 into the circulation path 88 in the hot water supply side cycle 82. Then, this flows through the heat exchange path 90 and is returned from the hot water inlet to the upper part of the hot water storage tank 87.
[0005]
Further, in the heat source side cycle 81, as shown in FIG. 7, the high-pressure refrigerant in the state (1) is discharged from the compressor 83, and this high-pressure refrigerant is introduced into the water heat exchanger 84. The water heat exchanger 84 exchanges heat with the heat exchange path 90 and water passing therethrough. As a result, the passing water is heated (boiled up). By this heat exchange, the high-pressure refrigerant dissipates heat to the water, and the enthalpy decreases from (1) to (2). The high-pressure refrigerant in the state (2) is sent to the expansion valve 85. In the expansion valve 85, the high-pressure refrigerant is depressurized, and the pressure is reduced from the state (2) to the state (3). Then, the refrigerant in the state (3) is introduced into the air heat exchanger 86. In the air heat exchanger 86, the low-pressure refrigerant exchanges heat with air. By this heat exchange, the low-pressure refrigerant absorbs heat and evaporates, and its enthalpy increases from the state (3) to the state (4). The low-pressure refrigerant in the state (4) is sent to the compressor 83.
[0006]
For this reason, when using a supercritical refrigerant (for example, carbon dioxide gas) used in supercriticality, the difference in enthalpy between (3) and (4) is small and the refrigeration cycle efficiency is poor. Therefore, in a water heater that requires boiling a large amount of hot water, the size of the water heater is increased, resulting in high manufacturing costs and running costs.
[0007]
The present invention has been made to solve the above-described conventional drawbacks, and an object of the present invention is to provide a hot water heater capable of improving COP, saving energy, and reducing electricity charges.
[0008]
[Means for Solving the Problems]
Accordingly, the water heater of claim 1 is a water heater for boiling hot water in a refrigerant circuit using a supercritical refrigerant used supercritically as a refrigerant, and tap water is supplied from a water supply port provided on the lower side. The hot water storage tank 3 for discharging hot hot water from the hot water supply port provided on the upper side is provided, and the stored water from the water intake 4 of the hot water storage tank 3 circulates in the heat exchange path 8 of the circulation path 6. Heat is exchanged with the circulating water in the circulation path 6 to heat the circulating water and returned to the hot water storage tank 3 from the hot water inlet 5, and the hot water in the hot water storage tank 3 heats the floor warming panel 54. It is configured to perform floor heating to return to the hot water storage tank 3, and further, the refrigerant circuit is provided with an expander 12, and the power generated by the expander 12 can be recovered.
[0009]
In the hot water heater of claim 1, since the refrigerant circuit is provided with the expander 12, the expansion process of the refrigeration cycle becomes an isentropic change, the power generated in the expander 12 can be recovered, and the evaporation capacity is Increase. This improves COP. Furthermore, since a supercritical refrigerant used supercritically is used as the refrigerant, there is no problem of ozone layer destruction, environmental pollution, and the like, and the water heater becomes friendly to the global environment. Moreover, in this water heater, since the hot water heated up efficiently is used for floor heating, efficient floor heating can be performed.
[0010]
The water heater of claim 2 is characterized in that the power is input to the compressor 10 of the refrigerant circuit.
[0011]
In the hot water supply apparatus of the second aspect, since the power generated in the expander 12 can be input to the compressor of the refrigerant circuit, the external input for driving the compressor 10 can be reduced. Accordingly, the compressor 10 can be reduced in size when the same capability as that using an expansion valve is used for the expansion mechanism.
[0012]
In the water heater of claim 3, the expander 12 and the compressor 10 have a common drive shaft, and the power generated by the expander 12 is transmitted to the compressor 10 via the drive shaft 19. It is a feature.
[0013]
In the hot water supply apparatus according to the third aspect, since the power generated in the expander 12 is transmitted to the compressor 10 by the common drive shaft 19 of the expander 12 and the compressor 10, the power generated in the expander 12 is transmitted. It can be reliably transmitted to the compressor 10.
[0016]
The water heater according to claim 4 is characterized in that the hot water boiled in the refrigerant circuit is used for hot water supply to a bathtub or the like and floor heating.
[0017]
In the hot water supply apparatus according to the fourth aspect, since the hot water that has been efficiently boiled is used for hot water supply to a bathtub or the like and floor heating, efficient hot water supply and floor heating can be performed.
[0018]
DETAILED DESCRIPTION OF THE INVENTION
Next, specific embodiments of the water heater of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a simplified diagram of this water heater. The water heater includes a hot water supply side cycle 1 and a heat source side cycle 2. The hot water supply side cycle 1 includes a hot water storage tank 3, and hot water stored in the hot water storage tank 3 is supplied to a bathtub or the like (not shown). That is, the hot water storage tank 3 is provided with a water supply port (not shown) on the lower side and a hot water supply port (not shown) on the upper side. And tap water is supplied to the hot water storage tank 3 from a water supply port, and hot hot water is discharged from a hot water supply port. In addition, the hot water storage tank 3 is provided with a water intake 4 on the lower side thereof, and a hot water inlet 5 is opened on the upper side thereof, and the water intake 4 and the hot water inlet 5 are connected by a circulation path 6. . The circulation path 6 is provided with a water circulation pump 7 and a heat exchange path 8.
[0019]
And the heating side cycle (heat pump type heat source) 2 is provided with a refrigerant circuit, and this refrigerant circuit includes a compressor 10, a water heat exchanger 11 constituting the heat exchange path 8, and an expander 12 as a pressure reducing mechanism. The air heat exchanger 13 is connected in order. That is, the discharge pipe 14 of the compressor 10 is connected to the water heat exchanger 11, the water heat exchanger 11 and the expander 12 are connected by the refrigerant passage 15, and the expander 12 and the air heat exchanger 13 are connected to the refrigerant. They are connected by a passage 16 and are connected by an air heat exchanger 13, a compressor 10 and a refrigerant passage 17. In addition, as the refrigerant, a supercritical refrigerant (for example, carbon dioxide, other ethylene, ethane, nitrogen oxide, etc.) that is used supercritically as the refrigerant is used.
[0020]
Incidentally, in the refrigerant circuit, a compression / expansion unit body 18 in which the compressor 10 and the expander 12 are integrated is used. That is, as shown in FIG. 2, the compression / expansion unit body 18 is driven by the compressor 10 that compresses and sends out the refrigerant to a critical pressure or higher, the expander 12 that expands the refrigerant, and the compressor 10 and the expander 12. An electric motor (motor) 20 that supplies power through a shaft 19 is housed in a sealed state in the casing A. For this reason, the compressor 10, the electric motor 20, and the expander 12 are connected by this common drive shaft 19.
[0021]
In this case, the inside of the casing A is partitioned by a heat insulating material 23 and the like into a first space 21 on the compressor 10 and electric motor 20 side and a second space 22 on the expander 12 side. The compressor 10 is a so-called oscillating piston type rotary compressor, and includes first and second cylinder mechanisms 24 and 25. That is, the first and second cylinder mechanisms 24 and 25 are respectively provided with crankshafts 26 and 27 mounted on the drive shaft 19, pistons 28 and 29 fitted on the crankshafts 26 and 27, and pistons. And cylinders 32 and 33 having cylinder chambers 30 and 31 in which 28 and 29 are accommodated.
[0022]
The cylinder 32 of the first cylinder mechanism 24 includes a cylinder body 34, a lid member 35 attached to one end surface of the cylinder body 34, an interposer 36 attached to the other end surface of the cylinder body 34, and the like. Is done. The lid member 35 supports one end of the drive shaft 19. The cylinder 33 of the second cylinder mechanism 25 includes a cylinder main body 38, the interposition body 36, a lid member 39 attached to the end surface of the cylinder main body 38 on the motor 20 side, and the like. In addition, suction ports 40 and 41 are connected to the cylinder bodies 34 and 38, respectively.
[0023]
Next, the expander 12 is constituted by a swinging piston type expander in this case. That is, a crankshaft 43 mounted on the drive shaft 19, a piston 44 fitted on the crankshaft 43, and a cylinder 46 having a cylinder chamber 45 in which the piston 44 is accommodated. The cylinder 46 can be composed of a cylinder body 47, a support 48 that supports the other end of the drive shaft 19, a partition plate 49 on the heat insulating material 23 side, and the like. A discharge port 50 is connected to the cylinder body 47, and a suction pipe 51 is connected to the cylinder chamber 45.
[0024]
The compressor 10 of the compression / expansion unit body 18 configured as described above is driven by a motor 20. That is, by rotating the drive shaft 19, the crankshafts 26 and 27 connected to the drive shaft 19 are rotated, and the pistons 28 and 29 are oscillated in the cylinder chambers 30 and 31. Therefore, the refrigerant is sucked into the cylinder chambers 30 and 31 from the suction ports 40 and 41 according to this swinging motion, and the pistons 28 and 29 are swung in the cylinder chambers 30 and 31 so as to exceed the critical pressure. The refrigerant having been compressed to a predetermined pressure and discharged at a high temperature and a high pressure is discharged from the discharge port 42 provided in the casing A to the discharge pipe 14.
[0025]
In the expander 12, the drive shaft 19 is rotationally driven to rotate the crankshaft 43 connected to the drive shaft 19, thereby causing the piston 44 to swing within the cylinder chamber 45. Therefore, the refrigerant is sucked into the cylinder chamber 45 from the suction pipe 52 in accordance with the swing motion, and the piston 44 swings in the cylinder chamber 45 so that the refrigerant is expanded and the expanded refrigerant is discharged. The refrigerant flows out from the port 50 to the refrigerant passage 16.
[0026]
According to the water heater configured as described above, when the compressor 10 is driven (the drive shaft 19 is rotationally driven by energizing the motor 20) and the water circulation pump 13 is driven (actuated), The high-pressure and high-temperature refrigerant from the compressor 10 flows into the water heat exchanger 11, and the stored water (low-temperature water) from the water intake 4 of the hot water storage tank 3 flows through the heat exchange path 8 of the circulation path 6. As a result, heat exchange is performed between the high-pressure and high-temperature refrigerant and the circulating water in the circulation path 6, and this circulating water is heated (boiling) and returned (inflowed) from the hot water inlet 5 to the hot water storage tank 3. High temperature hot water can be stored in the tank 3.
[0027]
The refrigeration cycle of the refrigerant circuit at this time is as shown in FIG. That is, the high-pressure refrigerant in the state (1) is discharged from the compressor 10, and this high-pressure refrigerant is introduced into the water heat exchanger 11. The water heat exchanger 11 performs heat exchange between the heat exchange path 14 and the passing water. By this heat exchange, the high-pressure refrigerant dissipates heat to the water, and its enthalpy decreases from (1) to (2). The high-pressure refrigerant in the state (2) is sent to the expander 12. In the expander 12, the high-pressure refrigerant is depressurized, and the pressure is reduced from (2) to (3) '. At this time, since the expander 12 is used as the expansion mechanism, the isentropic change is caused, and the expansion valve is used without using the expansion machine 12 in (3) ′ and (3) (3). Power recovery of the enthalpy difference of the reduced pressure state). Then, the refrigerant in the state (3) ′ is introduced into the air heat exchanger 13. In the air heat exchanger 13, this low-pressure refrigerant exchanges heat with air. By this heat exchange, the low-pressure refrigerant absorbs heat and evaporates, and the enthalpy increases from the state (3) to the state (4). The low-pressure refrigerant in the state (4) is sent to the compressor 10. The shaded portion in FIG. 3 shows the case of a simple cycle.
[0028]
In this case, the power recovery is transmitted to the compressor 10 by the drive shaft 19 and is transmitted to the driving force of the compressor 10. That is, as shown in FIG. 3, the compressor 10 requires inputs from (4) to (1), and among these, the difference from (3) 'to (3) is recovered and (4) To (4) 'can be used for the input of the compressor 10, and the external input to the compressor 10 can be reduced. For this reason, COP improves and it can aim at energy saving and reduction of an electricity bill. Moreover, since the evaporation capacity is also increased, the same capacity can be obtained even if a compressor smaller than that using an expansion valve is used, and the manufacturing cost and running cost can be reduced.
[0029]
Next, FIG. 4 shows an embodiment of the present invention in which a floor heating unit 53 is added to the simplified diagram of the water heater shown in FIG. 1. In this case, hot water stored in the hot water storage tank 3 is used for floor heating. I use it. That is, the water heater includes a floor heating unit 53 having a floor warming panel 52. A circulation pipe 54 is disposed inside the warm floor panel 52, an outgoing pipe 56 is connected to an inlet 54 a of the circulation pipe 54, and a return pipe 57 is connected to an outlet 54 b of the circulation pipe 54. The forward piping 56 is connected to the hot water supply port 58 at the upper part of the hot water storage tank 3, and the return piping 57 is connected to the return flow port 59 at the lower part of the hot water storage tank 3. A circulation pump 60 is interposed in the outgoing pipe 56. In addition, since the other structure is the same as that of the air conditioner shown in FIG. 1, the same part is shown with the same code | symbol and the description is abbreviate | omitted.
[0030]
Accordingly, by driving the circulation pump 60, hot water in the hot water storage tank 3 flows out from the hot water supply port 58, flows through the circulation pipe 54 through the forward piping 56, and flows from the return flow port 59 through the return piping 57. Return to tank 3. At this time, the warm floor panel 52 is warmed by hot water flowing through the circulation pipe 54, and floor heating can be performed.
[0031]
Therefore, in the water heater of FIG. 4, the hot water supply side unit 1 and the heat source side unit 2 have the same configuration as that of FIG. 1, so that the COP can be improved as a water heater to save energy and reduce the electricity bill. it can. Moreover, since the evaporation capacity is also increased, the same capacity can be obtained even if a compressor smaller than that using an expansion valve is used, and the manufacturing cost and running cost can be reduced. And the hot water heated up efficiently in this way can be utilized for floor heating, and a highly efficient system can be comprised as a whole. By the way, the current electricity rate is set at a lower price than the daytime electricity rate unit in the middle of the night (for example, from 23:00 to 7:00), so the operation to store hot water in this hot water storage tank 3 is performed. You can save power if you go at midnight.
[0032]
Further, as shown in FIG. 5, by connecting a pipe 61 for supplying hot water to the bathtub or the like to the outgoing pipe 56 or the like, in addition to floor heating, hot water to the bathtub or the like (hereinafter sometimes simply referred to as hot water supply) is also provided. It becomes possible. In this case, in the forward piping 56, an opening / closing valve 63 is provided downstream of the joining portion 62 of the piping 61, and an opening / closing valve 64 is provided in the piping 61. Thereby, it is possible to switch between the case where only floor heating is performed, the case where only hot water is supplied, and the case where floor heating and hot water are performed. In addition, since the other structure is the same as that of the air conditioner shown in FIG. 1, the same part is shown with the same code | symbol and the description is abbreviate | omitted.
[0033]
That is, if the opening / closing valve 63 is opened and the opening / closing valve 64 is closed, only floor heating can be performed. If the opening / closing valve 63 is closed and the opening / closing valve 64 is opened, Only hot water can be supplied. If the on-off valves 63 and 64 are opened, floor heating and hot water can be supplied.
[0034]
Therefore, according to the water heater shown in FIG. 5, as with the water heater shown in FIG. 4, the COP can be improved and energy saving and reduction of electricity charges can be achieved. Moreover, since the evaporation capacity is also increased, the same capacity can be obtained even if a compressor smaller than that using an expansion valve is used, and the manufacturing cost and running cost can be reduced. Moreover, the hot water that has been efficiently boiled in this manner can be used for floor heating and hot water supply to a bathtub or the like, and as a whole, an extremely efficient system can be configured. And if the hot water used for this floor heating and hot water supply is boiled in the middle of the night, an electricity bill can be saved greatly and it will become a suitable hot water heater for a user. Note that the hot water supply to the water heater in FIG. 5 includes hot water supply to a kitchen, a washroom, and the like.
[0035]
Although specific embodiments of the present invention have been described above, the present invention is not limited to the above embodiments, and various modifications can be made within the scope of the present invention. For example, as the expander 12, the compressor 10 and the drive shaft 19 may not be shared. That is, the power generated by the expander 12 may be temporarily converted into electric energy and taken out, and this electric energy may be input as driving power for the compressor 10. The expander 12 may be a scroll type expander. Here, the scroll-type expander includes a fixed scroll and a turning scroll. When high-pressure refrigerant flows from the inlet, the refrigerant gradually expands under reduced pressure while generating turning power in the turning scroll. And flows out from the outlet. For this reason, the power generated in such a scroll expander may be transmitted to the compressor 1 and used for driving the compressor 1. Furthermore, as the expander 12, other various expanders such as a gear type and a screw type can be used. As the compressor 10, various types of compressors such as a scroll type and a screw type can be used.
[0036]
【The invention's effect】
According to the hot water supply apparatus of the first aspect, the power generated by the expander can be recovered and the evaporation capacity is increased. As a result, COP is improved and efficient operation without waste is possible. Furthermore, since a supercritical refrigerant used supercritically is used as the refrigerant, there is no problem of ozone layer destruction, environmental pollution, and the like, and the water heater becomes friendly to the global environment. Moreover, according to this water heater, since the hot water heated up efficiently is used for floor heating, efficient floor heating can be performed. That is, a high-efficiency system can be configured as a water heater, and the running cost can be reduced.
[0037]
According to the water heater of claim 2, external input for driving the compressor can be reduced. Accordingly, when the same capability as that using an expansion valve is used for the expansion mechanism, the compressor can be reduced in size, and the manufacturing cost and the running cost can be reduced.
[0038]
According to the water heater of claim 3, the power generated by the expander can be reliably transmitted to the compressor. As a result, more efficient operation is possible, and energy saving and reduction of electricity charges can be achieved.
[0040]
According to the hot water supply apparatus of claim 4, since the hot water boiled up efficiently is used for hot water supply to a bathtub or the like and floor heating, efficient hot water supply and floor heating can be performed. A high-efficiency system can be configured as a water heater, and the running cost can be reduced. Moreover, the user can spend comfortably with hot water and floor heating.
[Brief description of the drawings]
FIG. 1 is a simplified diagram showing an embodiment of a water heater according to the present invention.
FIG. 2 is a cross-sectional view of a compressor and an expander of the water heater.
FIG. 3 is a Mollier diagram of the water heater.
4 is a simplified diagram showing an embodiment of a water heater of the present invention in which a floor heating unit is attached to the water heater of FIG . 1. FIG.
FIG. 5 is a simplified diagram showing another embodiment of the water heater according to the present invention.
FIG. 6 is a simplified diagram of a conventional water heater.
FIG. 7 is a Mollier diagram of a conventional water heater.
[Explanation of symbols]
10 Compressor 12 Expander 19 Drive shaft

Claims (4)

冷媒に超臨界で使用する超臨界冷媒を用いた冷媒回路にて、温湯を沸き上げる給湯機であって、下部側に設けた給水口から水道水が供給され、上部側に設けた給湯口から高温の温湯を出湯する貯湯タンク（３）を設け、貯湯タンク（３）の取水口（４）からの貯溜水が循環路（６）の熱交換路（８）を流通し、これによって高温冷媒と循環路（６）の循環水とで熱交換が行われて循環水が加熱されると共に、湯入口（５）から貯湯タンク（３）に返流され、また、この貯湯タンク（３）の湯が床暖パネル（５４）を加熱して貯湯タンク（３）に戻る床暖房を行うべく構成して成り、さらに上記冷媒回路に膨張機（１２）を備え、この膨張機（１２）で発生した動力の回収を可能としたことを特徴とする給湯機。A hot water heater that boils hot water in a refrigerant circuit that uses a supercritical refrigerant that is used as a supercritical refrigerant, and tap water is supplied from a water supply port provided on the lower side, and from a water supply port provided on the upper side. A hot water storage tank (3) for discharging hot hot water is provided, and the stored water from the water intake (4) of the hot water storage tank (3) flows through the heat exchange path (8) of the circulation path (6), whereby the high temperature refrigerant And the circulating water in the circulation path (6) exchange heat to heat the circulating water and return it from the hot water inlet (5) to the hot water storage tank (3). It is configured to perform floor heating in which hot water heats the floor warming panel (54) and returns to the hot water storage tank (3), and further includes an expander (12) in the refrigerant circuit, which is generated in the expander (12). The hot water heater is characterized in that the recovered power can be recovered. 上記動力を、上記冷媒回路の圧縮機（１０）に入力することを特徴とする請求項１の給湯機。  The hot water heater according to claim 1, wherein the power is input to a compressor (10) of the refrigerant circuit. 上記膨張機（１２）と圧縮機（１０）とは共通の駆動軸（１９）を有し、この膨張機（１２）で発生した動力を上記駆動軸（１９）を介して圧縮機（１０）に伝達することを特徴とする請求項２の給湯機。  The expander (12) and the compressor (10) have a common drive shaft (19), and the power generated by the expander (12) is transferred to the compressor (10) via the drive shaft (19). The water heater according to claim 2, wherein the water heater is transmitted to the water heater. 上記冷媒回路にて沸き上げられた温湯を、浴槽等への給湯に使用することを特徴とする請求項１〜請求項３のいずれかの給湯機。The hot water that has been boiled in the refrigerant circuit, one of the water heater of claim 1 to claim 3, characterized in that used for hot water supply to the tub or the like.
JP2002042928A 2002-02-20 2002-02-20 Water heater Expired - Fee Related JP3915538B2 (en)

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JP4617831B2 (en) * 2004-11-02 2011-01-26 ダイキン工業株式会社 Fluid machinery
JP2006132818A (en) * 2004-11-04 2006-05-25 Matsushita Electric Ind Co Ltd Control method for refrigerating cycle device, and refrigerating cycle device using the same
JP4940632B2 (en) * 2005-11-08 2012-05-30 ダイキン工業株式会社 Heat pump water heater
JP4765910B2 (en) * 2006-11-24 2011-09-07 ダイキン工業株式会社 Fluid machinery
CN101542072B (en) * 2007-01-18 2011-08-31 松下电器产业株式会社 Fluid machine and refrigeration cycle device
JP4755618B2 (en) * 2007-03-12 2011-08-24 パナソニック株式会社 Refrigeration cycle equipment
JP5604454B2 (en) 2012-01-13 2014-10-08 リンナイ株式会社 Heating device and water heater
JP5581361B2 (en) 2012-09-24 2014-08-27 リンナイ株式会社 Heating device and water heater
CN108981160B (en) * 2018-08-10 2020-10-30 大连民族大学 Heat supply method of open type heat pump with air circulation

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