JP3615475B2 - Heat pump water heater - Google Patents

Heat pump water heater Download PDF

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Publication number
JP3615475B2
JP3615475B2 JP2000296338A JP2000296338A JP3615475B2 JP 3615475 B2 JP3615475 B2 JP 3615475B2 JP 2000296338 A JP2000296338 A JP 2000296338A JP 2000296338 A JP2000296338 A JP 2000296338A JP 3615475 B2 JP3615475 B2 JP 3615475B2
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refrigerant
radiator
heat
compression element
water
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JP2002106988A (en
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修 桑原
洋 向山
寿和 石原
俊行 江原
博和 井崎
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Sanyo Electric Co Ltd
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Sanyo Electric Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Domestic Hot-Water Supply Systems And Details Of Heating Systems (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Air Conditioning Control Device (AREA)

Description

【０００１】
【発明の属する技術分野】
本発明は、二酸化炭素冷媒を動作冷媒として用いたヒートポンプ給湯機に関する。
【０００２】
【従来の技術】
従来、給湯機としてはガスや電気ヒータを熱源とするものが大勢的であるが、近年におけるエネルギ−利用の効率化の要望やガスや電気ヒータによる火災等の防止の観点からヒートポンプ給湯機が提案されている。
【０００３】
このようなヒートポンプ給湯機は図３に示すように、冷媒を圧縮する圧縮機１１１、該圧縮機１１１からの冷媒と給湯用の水とを熱交換させる凝縮器１１２、冷媒を膨張させる膨張弁１１３、冷媒と機外空気とを熱交換させる蒸発器１１４、該蒸発器１１４からの冷媒の気液分離を行ってガス冷媒が圧縮機１１１に戻るようにするアキュムレータ１１５等を有している。以下、この凝縮器１１２を放熱器１１２という。
【０００４】
そして、冷媒は圧縮機１１１で圧縮されて高温高圧になって放熱器１１２に供給される。放熱器１１２には給湯用の水が循環しているので、冷媒の熱はこの水を加熱するために用いられる。
【０００５】
水を加熱した冷媒は膨張弁１１３で絞られ、蒸発器１１４で機外空気と熱交換して圧縮機１１１に戻る。
【０００６】
このとき冷媒は機外空気から熱を汲上げて蒸発するので、電気ヒータ等による給湯機に比べエネルギー効率が高くなっている。
【０００７】
このような冷媒回路には従来Ｒ−２２等の冷媒が用いられてきたが、かかる冷媒には塩素が含まれオゾン層を破壊する原因となることが判明し規制対象となり、これに代わる冷媒が望まれている。
【０００８】
そこで、自然冷媒であるため環境破壊等の恐れが無い二酸化炭素冷媒の利用が検討されている。
【０００９】
しかし、二酸化炭素冷媒は従来用いられていたＲ−２２等の冷媒に比べ動作圧力及び温度が高くなるため、従来構成の圧縮機１１１等をそのまま用いるとサイクル効率が低下すると共に、圧縮器の容器内圧力が高くなりすぎて耐圧特性が不足したり、圧縮機に用いられている潤滑油の劣化やモータの巻線の絶縁劣化が起る問題が生じる。
【００１０】
かかる問題に対処すべく、図４に示すような２つの圧縮要素を備える圧縮機１１１を用いたヒートポンプ給湯機が提案されている。
【００１１】
図４において、圧縮機１１１は、前段圧縮要素１１１ａ及び後段圧縮要素１１１ｂから構成され、その間に中間熱交換器１１６が設けられている。
【００１２】
このように圧縮機１１１を２段構成にすることにより、各圧縮要素における吸気側と吐出側との差圧が小さくでき、圧縮効率が向上し、また中間熱交換器１１６により前段圧縮要素１１１ａからの冷媒の熱を機外空気や他の冷却材に熱放出することにより、圧縮機１１１の容器内に吐出される冷媒の温度が下げることができて潤滑油等の劣化を防止することが可能になる。
【００１３】
【発明が解決しようとする課題】
しかしながら、このような構成の場合には、中間熱交換器１１６で外気等に冷媒の熱が放熱されるので、その分だけ熱の無駄が発生する問題がある。
【００１４】
また、中間熱交換器１１６で一律な放熱を行う場合、給湯機では少なくとも給湯温度より高い温度（例えば、〜１０℃）の冷媒が後段圧縮要素１１１ｂから吐出される必要があるので、圧縮比が低く吸込み過熱度も小さい夏季に中間熱交換器１１６で放出される熱が多過ぎると吐出温度が低下してしまい、所望温度の湯を給湯できない場合が生じる問題がある。
【００１５】
この場合、無理に圧縮比を上げて圧縮機からの吐出温度を高くしようとするとサイクル効率が低下してしまう。
【００１６】
一方、冬季には逆に圧縮比が高く吸込み過熱度も大きいので、上述したように中間冷却を行わないと後段圧縮要素１１１ｂからの吐出温度が高すぎて、熱力学的な損失が増大するばかりではなく潤滑油の劣化等の問題が生じる。
【００１７】
そこで、本発明は、蒸発器における冷媒の蒸発温度や前段圧縮要素に吸気される冷媒の過熱度等を考慮して中間熱交換器での放熱量を調整可能にすると共に、当該中間熱交換器での廃熱を回収できるようにしてサイクル効率を向上させたヒートポンプ給湯機を提供することを目的とする。
【００１８】
【課題を解決するための手段】
上記課題を解決するため、請求項１にかかる発明は、冷媒を圧縮する前段圧縮要素及び後段圧縮要素を備えた圧縮機と、給湯用の水が給水されて冷媒と熱交換させる第３放熱器と、該第３放熱器からの水を流量の大きい主流とその残りの副流とに所定流量比で分流させる分流量制御弁と、主流をなす水と後段圧縮要素からの冷媒とを熱交換させ、当該熱交換した冷媒が第３放熱器に流入するように接続された第２放熱器と、副流をなす水と前段圧縮要素からの冷媒とを熱交換させ、当該水が第２放熱器からの水と合流して給湯され、熱交換した冷媒は後段圧縮要素に流入するように接続された第１放熱器と、第３放熱器からの冷媒を膨張させる膨張弁と、該膨張弁で膨張した冷媒を機外空気と熱交換させる蒸発器とを有して、圧縮機に供給される冷媒の状態に応じて第１放熱器での放熱量を調整可能にして後段圧縮機から吐出される冷媒の温度が常に所望の温度範囲になるようにすると共に当該第１放熱器での廃熱を回収できるようにして、サイクル効率の向上維持を図るようにしたことを特徴とする。
【００１９】
請求項２にかかる発明は、第３放熱器から膨張弁に供給される冷媒と、蒸発器から前段圧縮要素に戻る冷媒とを熱交換させる内部熱交換器を設けて、蒸発器で外気から汲上げる熱量を増大させると共に、圧縮機に戻る冷媒を加熱することにより熱回収が行えるようにしたことを特徴とする。
【００２０】
請求項３にかかる発明は、分流制御弁の開弁度を蒸発器における冷媒の蒸発温度や前段圧縮要素に吸気される冷媒の過熱度等に応じて制御するようにして、後段圧縮要素から吐出される冷媒の温度が常に最適な温度になるようにしたことを特徴とする。
【００２１】
請求項４にかかる発明は、冷媒として二酸化炭素冷媒を用いて、自然環境に優しい装置にすると共に、高温給湯が可能にしたことを特徴とする。
【００２２】
【発明の実施の形態】
本発明の第１の実施の形態を図を参照して説明する。図１は、本発明にかかるヒートポンプ給湯機の冷媒回路図である。
【００２３】
なお、本発明にかかるヒートポンプ給湯機では、冷媒として自然冷媒である二酸化炭素冷媒を用いる場合について説明する。
【００２４】
ヒートポンプ給湯機は、冷媒を圧縮する圧縮機１１、冷媒と水と熱交換させる放熱器１２、冷媒を膨張させる膨張弁１４、冷媒と外気等とを熱交換させる蒸発器１５、冷媒の気液分離を行うアキュムレータ１６、放熱器１２から膨張弁１４に向う冷媒により圧縮機１１に戻る冷媒を加熱する内部熱交換器１３等を有している。
【００２５】
圧縮機１１は前段圧縮要素１１ａ及び後段圧縮要素１１ｂから構成され、また放熱器１２は第１放熱器１２ａ、第２放熱器１２ｂ及び第３放熱器１２ｃにより構成されて、各放熱器１２には冷媒と給湯用の水が循環してこれらの間で熱交換するようになっている。
【００２６】
即ち、冷媒は前段圧縮要素１１ａ、第１放熱器１２ａ、後段圧縮要素１１ｂ、第２放熱器１２ｂ、第３放熱器１２ｃを順次流動し、給湯用の水は第３放熱器１２ｃに供給され、そこから第２放熱器１２ｂと第１放熱器１２ａとに所定の流量比で分流し、第２放熱器１２ｂと第１放熱器１２ａとで加熱された後は合流して給湯用に取出されるようになっている。
【００２７】
このように第３放熱器１２ｃからの水を第１放熱器１２ａと第２放熱器１２ｂとに所定の流量比で分流させるために、第３放熱器１２ｃと第１放熱器１２ａとを接続する水配管には分流量制御弁１７が設けられている。
【００２８】
この分流量制御弁１７の開弁度は、第１放熱器１２ａに流入する水量（副流と記載する）は第２放熱器１２ｂに流入する水量（主流と記載する）より少なくし、サイクル効率を勘案すると副流は全水量の半分以下に設定することが好ましい。
【００２９】
なお、これまでの説明から解るように、冷媒と水とは各放熱器１２で対向流をなすように構成されている。このように対向流で循環させることにより、放熱器１２での循環方向に沿った冷媒の温度勾配と給湯用の水の温度勾配とが逆の温度勾配になって効率的に熱交換ができるようになっている。
【００３０】
このような構成のヒートポンプ給湯機は、図２に示すような温度（Ｔ）−エンタルピー（ｈ）線図に従い動作する。
【００３１】
前段圧縮要素１１ａで圧縮された冷媒（ａ→ｂ）は、第１放熱器１２ａに供給されて、当該第１放熱器１２ａで給湯用の水に放熱し（ｂ→ｃ）、水は冷媒からの熱により加熱されて温度上昇する（Ａ→Ｂ）。
【００３２】
第１放熱器１２ａに循環する水の量は、分流量制御弁１７の開弁度を設定することにより調整され、当該分流量制御弁１７の開弁度は、蒸発器１５における冷媒の蒸発温度や前段圧縮要素１１ａに吸気される冷媒の過熱度等に応じて設定される。
【００３３】
従って、外気温等の運転条件に依存することなく常に最適な吐出温度で運転することが可能になってサイクル効率が向上する。
【００３４】
また、前段圧縮要素１１ａからの冷媒は第１放熱器１２ａで放熱するが、その熱は給湯用の水の加熱に用いられるので（熱回収される）、従来のように外気等への廃熱と言った無駄が省けて、この意味からもサイクル効率の向上が図られている。
【００３５】
後段圧縮要素１１ｂから吐出される冷媒の温度は、例えば夏季のように過熱度が小さい場合等には開弁度を絞り、当該第１放熱器１２ａに供給される水量を少なくして前段圧縮要素１１ａからの冷媒が失う熱量を押えることにより所望値に調整する。また、過熱度が大きくなった場合等には、上記手順と逆の手順が行われる。
【００３６】
このようにして、第１放熱器１２ａからの冷媒は後段圧縮要素１１ｂで更に圧縮されて（ｃ→ｄ）、第２放熱器１２ｂに供給され、当該第２放熱器１２ｂで分流された給湯用の水を加熱し（Ｄ→Ｅ）、第３放熱器１２ｃへと循環する。そして、第３放熱器１２ｃで水を加熱し（Ｃ→Ｄ）て内部熱交換器に循環する。
【００３７】
この内部熱交換器には、アキュムレータから圧縮機１１に戻る冷媒が流動しているので、第３放熱器１２ｃからの冷媒は当該圧縮機１１に戻る冷媒を加熱して温度が下がる（ｅ）。
【００３８】
そして、膨張弁１４で膨張し（ｅ→ｆ→ｇ）、蒸発器で機外空気と熱交換して蒸発（ｈ→ｉ）した後、アキュムレータで気液分離が行われてガス冷媒が前段圧縮要素１１ａに戻る。
【００３９】
内部熱交換器で第３放熱器１２ｃからの冷媒が熱を失うことにより、蒸発器１５で効率的に熱の汲上を行うことが可能になると共に、蒸発器から圧縮機１１に戻る冷媒が加熱される（熱回収される）ので圧縮機１１に戻る冷媒の温度が上昇して（ｊ→ａ）、サイクル効率を高めることができるようになっている。
【００４０】
【発明の効果】
以上説明したように請求項１にかかる発明によれば、冷媒を圧縮する前段圧縮要素及び後段圧縮要素を備えた圧縮機と、給湯用の水が給水されて冷媒と熱交換させる第３放熱器と、該第３放熱器からの水を流量の大きい主流とその残りの副流とに所定流量比で分流させる分流量制御弁と、主流をなす水と後段圧縮要素からの冷媒とを熱交換させ、当該熱交換した冷媒が第３放熱器に流入するように接続された第２放熱器と、副流をなす水と前段圧縮要素からの冷媒とを熱交換させ、当該水が第２放熱器からの水と合流して給湯され、熱交換した冷媒は後段圧縮要素に流入するように接続された第１放熱器と、第３放熱器からの冷媒を膨張させる膨張弁と、該膨張弁で膨張した冷媒を機外空気と熱交換させる蒸発器とを設けて圧縮機に供給される冷媒の状態に応じて第１放熱器での放熱量を調整可能にしたので、後段圧縮機から吐出される冷媒の温度が常に所望の温度範囲になるようにできると共に当該第１放熱器での廃熱を回収できるようになり、サイクル効率の向上維持が図れる。
【００４１】
請求項２にかかる発明によれば、第３放熱器から膨張弁に供給される冷媒と、蒸発器から前段圧縮要素に戻る冷媒とを熱交換させる内部熱交換器を設けて、蒸発器で外気から汲上げる熱量を増大させると共に、圧縮機に戻る冷媒を加熱することにより熱回収が行えるようになり、サイクル効率の向上が図れる。
【００４２】
請求項３にかかる発明によれば、分流制御弁の開弁度を蒸発器における冷媒の蒸発温度や前段圧縮要素に吸気される冷媒の過熱度等に応じて制御するようにしたので、後段圧縮要素から吐出される冷媒の温度が常に最適な温度になる。
【００４３】
請求項４にかかる発明によれば、冷媒として二酸化炭素冷媒を用いたので自然環境に優しい装置にすると共に、高温給湯が可能になる。
【図面の簡単な説明】
【図１】本発明の実施の形態の説明に適用されるヒートポンプ給湯機の概略構成図である。
【図２】図１のヒートポンプ給湯機の温度−エンタルピー線図である。
【図３】従来の技術の説明に適用される１つの圧縮要素を持つ圧縮機を備えたヒートポンプ給湯機の概略構成図である。
【図４】従来の技術の説明に適用される２つの圧縮要素を持つ圧縮機を備えたヒートポンプ給湯機の概略構成図である。
【符号の説明】
１１ 圧縮機
１１ａ 前段圧縮要素
１１ｂ 後段圧縮要素
１２ 放熱器
１２ａ 第１放熱器
１２ｂ 第２放熱器
１２ｃ 第３放熱器
１３ 内部熱交換器
１４ 膨張弁
１５ 蒸発器
１６ アキュムレータ
１７ 分流量制御弁[0001]
BACKGROUND OF THE INVENTION
The present invention relates to a heat pump water heater using carbon dioxide refrigerant as an operating refrigerant.
[0002]
[Prior art]
Conventionally, there are many hot water heaters that use gas or electric heaters as heat sources, but in recent years heat pump water heaters have been proposed from the standpoint of increasing the efficiency of energy use and preventing fires caused by gas and electric heaters. Has been.
[0003]
As shown in FIG. 3, such a heat pump water heater includes a compressor 111 that compresses the refrigerant, a condenser 112 that exchanges heat between the refrigerant from the compressor 111 and water for hot water supply, and an expansion valve 113 that expands the refrigerant. An evaporator 114 that exchanges heat between the refrigerant and outside air, and an accumulator 115 that performs gas-liquid separation of the refrigerant from the evaporator 114 so that the gas refrigerant returns to the compressor 111. Hereinafter, the condenser 112 is referred to as a radiator 112.
[0004]
Then, the refrigerant is compressed by the compressor 111, becomes high temperature and high pressure, and is supplied to the radiator 112. Since water for hot water supply circulates in the radiator 112, the heat of the refrigerant is used to heat the water.
[0005]
The refrigerant that has heated the water is throttled by the expansion valve 113, exchanges heat with the outside air by the evaporator 114, and returns to the compressor 111.
[0006]
At this time, the refrigerant pumps heat from the outside air and evaporates, so that the energy efficiency is higher than that of a water heater using an electric heater or the like.
[0007]
Conventionally, a refrigerant such as R-22 has been used in such a refrigerant circuit. However, it has been found that such a refrigerant contains chlorine and causes the destruction of the ozone layer. It is desired.
[0008]
Therefore, the use of carbon dioxide refrigerant, which is a natural refrigerant and has no fear of environmental destruction, has been studied.
[0009]
However, since the operating pressure and temperature of carbon dioxide refrigerant are higher than those of conventionally used refrigerants such as R-22, if the conventional compressor 111 or the like is used as it is, the cycle efficiency is lowered and the compressor container is used. There are problems that the internal pressure becomes too high and the pressure resistance is insufficient, or the lubricating oil used in the compressor is deteriorated and the insulation of the motor winding is deteriorated.
[0010]
In order to cope with such a problem, a heat pump water heater using a compressor 111 having two compression elements as shown in FIG. 4 has been proposed.
[0011]
In FIG. 4, the compressor 111 is comprised from the front | former stage compression element 111a and the back | latter stage compression element 111b, and the intermediate heat exchanger 116 is provided among them.
[0012]
By thus configuring the compressor 111 in a two-stage configuration, the differential pressure between the intake side and the discharge side in each compression element can be reduced, compression efficiency can be improved, and the intermediate heat exchanger 116 can reduce the pressure from the previous stage compression element 111a. By releasing the heat of the refrigerant to the outside air or other coolant, the temperature of the refrigerant discharged into the container of the compressor 111 can be lowered and deterioration of the lubricating oil or the like can be prevented. become.
[0013]
[Problems to be solved by the invention]
However, in the case of such a configuration, since the heat of the refrigerant is radiated to the outside air or the like by the intermediate heat exchanger 116, there is a problem that waste of heat is generated accordingly.
[0014]
In addition, when uniform heat dissipation is performed by the intermediate heat exchanger 116, the water heater needs to discharge a refrigerant having a temperature (for example, 10 ° C.) higher than the hot water supply temperature from the rear-stage compression element 111b. There is a problem that the discharge temperature may be lowered and hot water at a desired temperature may not be supplied if too much heat is released by the intermediate heat exchanger 116 in the summer when the suction is low and the degree of superheat is low.
[0015]
In this case, if the compression ratio is forcibly increased to increase the discharge temperature from the compressor, the cycle efficiency is lowered.
[0016]
On the other hand, on the other hand, since the compression ratio is high and the suction superheat degree is large in winter, the discharge temperature from the subsequent compression element 111b is too high unless the intermediate cooling is performed as described above, and the thermodynamic loss increases. Instead, problems such as deterioration of the lubricating oil occur.
[0017]
Therefore, the present invention makes it possible to adjust the heat radiation amount in the intermediate heat exchanger in consideration of the evaporation temperature of the refrigerant in the evaporator, the degree of superheat of the refrigerant sucked into the upstream compression element, and the like, and the intermediate heat exchanger An object of the present invention is to provide a heat pump water heater capable of recovering the waste heat in the factory and improving the cycle efficiency.
[0018]
[Means for Solving the Problems]
In order to solve the above-mentioned problem, the invention according to claim 1 includes a compressor provided with a front-stage compression element and a rear-stage compression element for compressing a refrigerant, and a third radiator that is supplied with hot water and exchanges heat with the refrigerant. A flow control valve for diverting the water from the third radiator to a main flow having a large flow rate and the remaining sub flow at a predetermined flow rate ratio, and heat exchange between the main flow water and the refrigerant from the subsequent compression element Heat exchange is performed between the second radiator connected so that the heat-exchanged refrigerant flows into the third radiator, the water forming the secondary flow, and the refrigerant from the previous compression element. A first radiator that is joined to the water from the radiator to supply hot water and exchanges heat and flows into the subsequent compression element; an expansion valve that expands the refrigerant from the third radiator; and the expansion valve And an evaporator that exchanges heat between the refrigerant expanded in the machine and outside air and is supplied to the compressor. The amount of heat released from the first radiator can be adjusted according to the state of the refrigerant to be discharged so that the temperature of the refrigerant discharged from the rear stage compressor is always within a desired temperature range, and the waste from the first radiator is discarded. It is characterized in that heat can be recovered to improve and maintain cycle efficiency.
[0019]
The invention according to claim 2 is provided with an internal heat exchanger for exchanging heat between the refrigerant supplied from the third radiator to the expansion valve and the refrigerant returning from the evaporator to the preceding compression element. The amount of heat to be increased is increased, and heat recovery can be performed by heating the refrigerant returning to the compressor.
[0020]
In the invention according to claim 3, the degree of opening of the flow dividing control valve is controlled from the evaporation temperature of the refrigerant in the evaporator, the degree of superheat of the refrigerant sucked into the upstream compression element, etc., and discharged from the downstream compression element. It is characterized in that the temperature of the refrigerant used is always the optimum temperature.
[0021]
The invention according to claim 4 is characterized in that a carbon dioxide refrigerant is used as the refrigerant to make the apparatus friendly to the natural environment and high-temperature hot water supply is possible.
[0022]
DETAILED DESCRIPTION OF THE INVENTION
A first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a refrigerant circuit diagram of a heat pump water heater according to the present invention.
[0023]
In addition, in the heat pump water heater concerning this invention, the case where the carbon dioxide refrigerant which is a natural refrigerant | coolant is used as a refrigerant | coolant is demonstrated.
[0024]
The heat pump water heater includes a compressor 11 that compresses refrigerant, a radiator 12 that exchanges heat between the refrigerant and water, an expansion valve 14 that expands the refrigerant, an evaporator 15 that exchanges heat between the refrigerant and outside air, and gas-liquid separation of the refrigerant. An accumulator 16 that performs the above operation, an internal heat exchanger 13 that heats the refrigerant returning to the compressor 11 by the refrigerant from the radiator 12 toward the expansion valve 14, and the like.
[0025]
The compressor 11 includes a front-stage compression element 11a and a rear-stage compression element 11b, and the radiator 12 includes a first radiator 12a, a second radiator 12b, and a third radiator 12c. The refrigerant and hot water supply water circulate and exchange heat between them.
[0026]
That is, the refrigerant sequentially flows through the front-stage compression element 11a, the first radiator 12a, the rear-stage compression element 11b, the second radiator 12b, and the third radiator 12c, and water for hot water supply is supplied to the third radiator 12c. From there, it is diverted to the second radiator 12b and the first radiator 12a at a predetermined flow rate ratio, and after being heated by the second radiator 12b and the first radiator 12a, they are merged and taken out for hot water supply. It is like that.
[0027]
In this way, the third radiator 12c and the first radiator 12a are connected in order to divert the water from the third radiator 12c to the first radiator 12a and the second radiator 12b at a predetermined flow rate ratio. A water flow control valve 17 is provided in the water pipe.
[0028]
The degree of opening of the flow control valve 17 is such that the amount of water flowing into the first radiator 12a (described as a secondary flow) is less than the amount of water flowing into the second radiator 12b (described as main flow), and the cycle efficiency In consideration of the above, it is preferable to set the side flow to half or less of the total water amount.
[0029]
In addition, as understood from the description so far, the refrigerant and water are configured so as to counterflow with each radiator 12. By circulating in the counterflow in this manner, the temperature gradient of the refrigerant along the circulation direction in the radiator 12 and the temperature gradient of the hot water supply water become opposite temperature gradients so that heat can be exchanged efficiently. It has become.
[0030]
The heat pump water heater having such a configuration operates according to a temperature (T) -enthalpy (h) diagram as shown in FIG.
[0031]
The refrigerant (a → b) compressed by the pre-stage compression element 11a is supplied to the first radiator 12a and radiates heat to the hot water supply water (b → c), and the water is discharged from the refrigerant. The temperature rises by being heated by the heat of (A → B).
[0032]
The amount of water circulating in the first radiator 12a is adjusted by setting the opening degree of the divided flow control valve 17, and the opening degree of the divided flow control valve 17 is determined by the evaporation temperature of the refrigerant in the evaporator 15. Or is set according to the degree of superheat of the refrigerant sucked into the pre-stage compression element 11a.
[0033]
Therefore, it becomes possible to always operate at the optimum discharge temperature without depending on the operating conditions such as the outside air temperature, and the cycle efficiency is improved.
[0034]
Moreover, although the refrigerant | coolant from the front | former stage compression element 11a thermally radiates with the 1st heat radiator 12a, since the heat | fever is used for the heating of the water for hot water supply (heat is collect | recovered), waste heat to external air etc. conventionally In this sense, the cycle efficiency is improved.
[0035]
The temperature of the refrigerant discharged from the rear-stage compression element 11b is reduced, for example, when the degree of superheat is small, such as in summer, and the amount of water supplied to the first radiator 12a is reduced to reduce the amount of water supplied to the front-stage compression element. By adjusting the amount of heat lost by the refrigerant from 11a, it is adjusted to a desired value. Further, when the degree of superheat becomes large, the procedure opposite to the above procedure is performed.
[0036]
In this way, the refrigerant from the first radiator 12a is further compressed by the rear-stage compression element 11b (c → d), supplied to the second radiator 12b, and divided into the second radiator 12b for hot water supply. The water is heated (D → E) and circulated to the third radiator 12c. And water is heated with the 3rd radiator 12c (C-> D), and it circulates to an internal heat exchanger.
[0037]
Since the refrigerant returning from the accumulator to the compressor 11 flows in the internal heat exchanger, the refrigerant from the third radiator 12c heats the refrigerant returning to the compressor 11 and the temperature decreases (e).
[0038]
Then, the gas is expanded by the expansion valve 14 (e → f → g), heat exchanged with the outside air by the evaporator and evaporated (h → i), and then gas-liquid separation is performed by the accumulator, and the gas refrigerant is compressed in the previous stage. Return to element 11a.
[0039]
When the refrigerant from the third radiator 12c loses heat in the internal heat exchanger, it becomes possible to efficiently pump the heat in the evaporator 15, and the refrigerant returning from the evaporator to the compressor 11 is heated. Thus, the temperature of the refrigerant returning to the compressor 11 rises (j → a), and the cycle efficiency can be increased.
[0040]
【The invention's effect】
As described above, according to the first aspect of the present invention, the compressor including the pre-stage compression element and the post-stage compression element for compressing the refrigerant, and the third radiator for supplying water to the hot water supply and exchanging heat with the refrigerant. A flow control valve for diverting the water from the third radiator to a main flow having a large flow rate and the remaining sub flow at a predetermined flow rate ratio, and heat exchange between the main flow water and the refrigerant from the subsequent compression element Heat exchange is performed between the second radiator connected so that the heat-exchanged refrigerant flows into the third radiator, the water forming the secondary flow, and the refrigerant from the previous compression element. A first radiator that is joined to the water from the radiator to supply hot water and exchanges heat and flows into the subsequent compression element; an expansion valve that expands the refrigerant from the third radiator; and the expansion valve An evaporator that exchanges heat between the refrigerant expanded in the machine and outside air is provided and supplied to the compressor. Since the amount of heat released by the first radiator can be adjusted according to the state of the refrigerant, the temperature of the refrigerant discharged from the rear stage compressor can always be in a desired temperature range, and the first radiator Waste heat can be recovered and cycle efficiency can be improved and maintained.
[0041]
According to the second aspect of the present invention, an internal heat exchanger is provided for exchanging heat between the refrigerant supplied from the third radiator to the expansion valve and the refrigerant returning from the evaporator to the preceding compression element. In addition to increasing the amount of heat pumped up, the heat recovery can be performed by heating the refrigerant returning to the compressor, thereby improving cycle efficiency.
[0042]
According to the invention of claim 3, since the degree of opening of the shunt control valve is controlled in accordance with the evaporation temperature of the refrigerant in the evaporator, the degree of superheat of the refrigerant sucked into the front stage compression element, etc. The temperature of the refrigerant discharged from the element is always the optimum temperature.
[0043]
According to the invention of claim 4, since carbon dioxide refrigerant is used as the refrigerant, the apparatus is friendly to the natural environment and high-temperature hot water supply is possible.
[Brief description of the drawings]
FIG. 1 is a schematic configuration diagram of a heat pump water heater applied to the description of an embodiment of the present invention.
FIG. 2 is a temperature-enthalpy diagram of the heat pump water heater of FIG.
FIG. 3 is a schematic configuration diagram of a heat pump water heater provided with a compressor having one compression element applied to the description of the prior art.
FIG. 4 is a schematic configuration diagram of a heat pump water heater provided with a compressor having two compression elements applied to the description of the conventional technology.
[Explanation of symbols]
11 compressor 11a front stage compression element 11b rear stage compression element 12 radiator 12a first radiator 12b second radiator 12c third radiator 13 internal heat exchanger 14 expansion valve 15 evaporator 16 accumulator 17 minute flow control valve

Claims (4)

冷媒を圧縮する前段圧縮要素及び該前段圧縮要素からの冷媒を更に圧縮する後段圧縮要素を備えた圧縮機と、
給湯用の水が給水されて冷媒と熱交換させる第３放熱器と、
該第３放熱器からの水を流量の大きい主流とその残りの副流とに所定流量比で分流させる分流量制御弁と、
前記主流をなす水と後段圧縮要素からの冷媒とを熱交換させ、当該熱交換した冷媒が前記第３放熱器に流入するように接続された第２放熱器と、
前記副流をなす水と前段圧縮要素からの冷媒とを熱交換させ、当該水が前記第２放熱器からの水と合流して給湯され、熱交換した冷媒は後段圧縮要素に流入するように接続された第１放熱器と、
前記第３放熱器からの冷媒を膨張させる膨張弁と、
該膨張弁で膨張した冷媒を機外空気と熱交換させる蒸発器とを有することを特徴とするヒートポンプ給湯機。A compressor including a first-stage compression element that compresses the refrigerant and a second-stage compression element that further compresses the refrigerant from the first-stage compression element;
A third radiator for supplying hot water and exchanging heat with the refrigerant;
A diversion flow control valve for diverting water from the third radiator to a main flow having a large flow rate and a remaining sub flow at a predetermined flow rate ratio;
Heat exchange between the mainstream water and the refrigerant from the subsequent compression element, and a second radiator connected so that the heat exchanged refrigerant flows into the third radiator;
Heat exchange is performed between the water that forms the side flow and the refrigerant from the front-stage compression element, and the water merges with water from the second radiator to supply hot water, so that the heat-exchanged refrigerant flows into the rear-stage compression element. A connected first radiator,
An expansion valve for expanding the refrigerant from the third radiator;
A heat pump water heater having an evaporator for exchanging heat between the refrigerant expanded by the expansion valve and outside air. 前記第３放熱器から膨張弁に供給される冷媒と、蒸発器から前段圧縮要素に戻る冷媒とを熱交換させる内部熱交換器を有することを特徴とする請求項１記載のヒートポンプ給湯機。The heat pump water heater according to claim 1, further comprising an internal heat exchanger for exchanging heat between the refrigerant supplied from the third radiator to the expansion valve and the refrigerant returning from the evaporator to the preceding compression element. 前記分流制御弁の開弁度が、前記蒸発器における蒸発温度及び前記前段圧縮要素に吸気される冷媒の過熱度に応じて制御するようにしたことを特徴とする請求項１又は２記載のヒートポンプ給湯機。The heat pump according to claim 1 or 2, wherein the degree of opening of the branch flow control valve is controlled in accordance with an evaporation temperature in the evaporator and a superheat degree of the refrigerant sucked into the upstream compression element. Water heater. 前記冷媒が二酸化炭素冷媒であることを特徴とする請求項１乃至３いずれか１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 3, wherein the refrigerant is a carbon dioxide refrigerant.
JP2000296338A 2000-09-28 2000-09-28 Heat pump water heater Expired - Fee Related JP3615475B2 (en)

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