JP4254126B2 - Ejector for vapor compression refrigeration cycle - Google Patents

Ejector for vapor compression refrigeration cycle Download PDF

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Publication number
JP4254126B2
JP4254126B2 JP2002124319A JP2002124319A JP4254126B2 JP 4254126 B2 JP4254126 B2 JP 4254126B2 JP 2002124319 A JP2002124319 A JP 2002124319A JP 2002124319 A JP2002124319 A JP 2002124319A JP 4254126 B2 JP4254126 B2 JP 4254126B2
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pressure
refrigerant
nozzle
chamber
ejector
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JP2003279177A (en
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猛 酒井
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Denso Corp
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Denso Corp
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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
    • 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0012—Ejectors with the cooled primary flow at high 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
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0013—Ejector control arrangements
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/04—Refrigeration circuit bypassing means
    • F25B2400/0407—Refrigeration circuit bypassing means for the ejector
    • 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
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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)
  • Chemical & Material Sciences (AREA)
  • Chemical Kinetics & Catalysis (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (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、蒸気圧縮式冷凍サイクル用のエジェクタに関するものである。
【０００２】
【発明が解決しようとする課題】
【０００４】
本発明は、電気式のアクチュエータを用いた場合に比べて、安価に高圧側冷媒圧力を制御することを目的とする。
【０００５】
【課題を解決するための手段】
本発明は、上記目的を達成するために、請求項１に記載の発明では、圧縮機（１０）にて圧縮された高温高圧の冷媒を放冷する高圧側熱交換器（２０）、及び減圧された低温低圧の冷媒を蒸発させる蒸発器（３０）を有して低温側の熱を高温側に移動させる蒸気圧縮式冷凍サイクルに適用されるエジェクタであって、高圧側熱交換器（２０）から流出した高圧の冷媒の圧力エネルギーを速度エネルギーに変換して冷媒を減圧膨張させるノズル（４１）と、ノズル（４１）から噴射する冷媒と蒸発器（３０）から吸引した冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）と、ノズル（４１）の軸線方向に変位し、ノズル（４１）の絞り開度を調節するニードル弁（４６）と、高圧側熱交換器（２０）から流出してノズル（４１）に流入する高圧の冷媒が充満する駆動室（４７ａ）と、駆動室（４７ａ）に隣接配置され、不活性ガスが封入された作動室（４７ｂ）と、駆動室（４７ａ）と作動室（４７ｂ）とを仕切るとともに、駆動室（４７ａ）内の圧力と作動室（４７ｂ）内の圧力との圧力差に応じて変位してニードル弁（４６）を変位させる仕切部材（４７ｇ）と、駆動室（４７ａ）及び作動室（４７ｂ）の外殻を形成するハウジング（４７ｅ）とを備え、仕切部材は、シール手段（４７ｈ）を介してハウジング（４７ｅ）の内面に摺動可能に配置されたピストン（４７ｇ）であることを特徴とする。
【０００６】
これにより、電気式のアクチュエータを用いた場合に比べて、安価に高圧側冷媒圧力を略一定となるように制御することができる。
【０００９】
請求項２に記載の発明では、仕切部材（４７ｇ）は、駆動室（４７ａ）内の圧力が作動室（４７ｂ）内の圧力より大きくなるとノズル（４１）の絞り開度が大きくなるようにニードル弁（４６）を変位させ、駆動室（４７ａ）内の圧力が作動室（４７ｂ）内の圧力より小さくなるとノズル（４１）の絞り開度が小さくなるようにニードル弁（４６）を変位させるように構成されていることを特徴とする。
【００１０】
また、請求項３に記載の発明のごとく、圧縮機（１０）は冷媒を冷媒の臨界圧力以上まで圧縮してもよい。
【００１１】
また、請求項４に記載の発明のごとく、冷媒として二酸化炭素を用いてもよい。
【００１７】
また、請求項５に記載の発明のごとく、仕切部材（４７ｇ）を駆動室（４７ａ）側に変位させる弾性力を仕切部材（４７ｇ）に作用させる弾性手段（４７ｊ）を備えてもよい。
【００２０】
因みに、上記各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示す一例である。
【００２１】
【発明の実施の形態】
（第１実施形態）
本実施形態は、ヒートポンプユニット１として、エジェクタ方式の減圧装置を有する蒸気圧縮式冷凍サイクルを用いたもので、図１は本実施形態に係る給湯器の模式図である。
【００２２】
圧縮機１０は冷媒を吸入圧縮するものであり、水冷媒熱交換器２０は圧縮機１０から吐出した冷媒と給湯水とを対向流れ状態で熱交換して給湯水を加熱することにより冷媒を冷却する高圧側熱交換器である。
【００２３】
なお、圧縮機１０は電動モータ（図示せず。）により駆動されており、水冷媒熱交換器２０の加熱能力を大きくするときには、圧縮機１０の回転数を増大させて圧縮機１０から吐出する冷媒の流量を増大させ、一方、加熱能力を小さくするときには、圧縮機１０の回転数を低下させて圧縮機１０から吐出する冷媒の流量を減少させる。
【００２４】
因みに、本実施形態では、冷媒として二酸化炭素を用いているので、水冷媒熱交換器２０内の冷媒圧力は冷媒の臨界圧力以上となり、かつ、水冷媒熱交換器２０内で冷媒が凝縮することなく、冷媒入口側から冷媒出口側に向かうほど冷媒温度が低下するような温度分布を有する。
【００２５】
蒸発器３０は室外空気と液相冷媒とを熱交換させて液相冷媒を蒸発させることにより冷媒を蒸発させて室外空気から吸熱する低圧側熱交換器であり、エジェクタ４０は冷媒を減圧膨張させて蒸発器３０にて蒸発した気相冷媒を吸引するとともに、膨張エネルギーを圧力エネルギーに変換して圧縮機１０の吸入圧を上昇させるものである。なお、エジェクタ４０の詳細は、後述する。
【００２６】
また、気液分離器５０はエジェクタ４０から流出した冷媒が流入するとともに、その流入した冷媒を気相冷媒と液相冷媒とに分離して冷媒を蓄える気液分離手段であり、気液分離器５０の気相冷媒流出口は圧縮機１０の吸引側に接続され、液相冷媒流出口は蒸発器３０側の流入側に接続される。
【００２７】
なお、図２はエジェクタサイクルの全体のマクロ的作動を示すｐ−ｈ線図であり、そのマクロ的作動は周知のエジェクタサイクルと同じであるので、本実施形態では、エジェクタサイクル全体のマクロ的作動の説明は省略する。因みに、図２の●で示される符号は、図１に示す●で示される符号位置における冷媒の状態を示すものである。
【００２８】
次に、図３に基づいてエジェクタ４０の構造について述べる。
【００２９】
エジェクタ４０は、流入する高圧冷媒の圧力エネルギーを速度エネルギーに変換して冷媒を減圧膨張させるノズル４１、ノズル４１から噴射する高い速度の冷媒流により蒸発器３０にて蒸発した気相冷媒を吸引しながら、ノズル４１から噴射する冷媒流とを混合する混合部４２、及びノズル４１から噴射する冷媒と蒸発器３０から吸引した冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させるディフューザ４３等からなるものである。
【００３０】
なお、混合部４２においては、ノズル４１から噴射する冷媒流の運動量と、蒸発器３０からエジェクタ４０に吸引される冷媒流の運動量との和が保存されるように混合するので、混合部４２においても冷媒の静圧が上昇する。一方、ディフューザ４３においては、通路断面積を徐々に拡大することにより、冷媒の動圧を静圧に変換するので、エジェクタ４０においては、混合部４２及びディフューザ４３の両者にて冷媒圧力を昇圧する。そこで、混合部４２とディフューザ４３とを総称して昇圧部と呼ぶ。
【００３１】
つまり、理想的なエジェクタ４０においては、混合部４２で２種類の冷媒流の運動量の和が保存されるように冷媒圧力が増大し、ディフューザ４３でエネルギーが保存されるように冷媒圧力が増大することがのぞましい。
【００３２】
因みに、ノズル４１の周りには、ボディ４４により形成された吸引室４５が形成されており、蒸発器３０から吸引された気相冷媒は、吸引室４５を経由して混合部４２に流れる。
【００３３】
また、ノズル４１は、通路途中に通路面積が最も縮小した喉部を有する末広型のノズルであり、ノズル４１の絞り開度、すなわち喉部の開度は、高圧側の冷媒圧力が略一定となるように、ニードル弁４６にて制御される。なお、ニードル弁４６は先端側が尖った円錐テーパ状のもので、ノズル４１内において機械式のアクチュエータ４７により軸線方向に変位させる。
【００３４】
ここで、機械式のアクチュエータ４７は、ノズル４１に流入する高圧冷媒が充満する駆動室４７ａと不活性ガスが封入された作動室４７ｂとを仕切るとともに、駆動室４７ａ内の圧力と作動室４７ｂ内の圧力との圧力差に応じて変位してニードル弁４６を変位させる仕切部材としてのダイヤフラム４７ｃ、ダイヤフラム４７ｃの駆動室４７ａ側に配置されてダイヤフラム４７ｃの最大変位を規制するストッパ４７ｄ等、並びに駆動室４７ａ及び作動室４７ｂの外殻を形成するステンレス製のハウジング４７ｅ等からなるものである。
【００３５】
因みに、本実施形態では、不活性ガスとして窒素ガスを用いているが、ヘリウムガスやアルゴンガス等の不活性ガスを用いてもよい。また、本実施形態では、ダイヤフラム４７ｃ及びニードル弁４６をステンレス製として両者をろう付け接合しているが、本実施形態はこれに限定されるものでない。
【００３６】
次に、ニードル弁４６の作動を中心に本実施形態に係るエジェクタ４０の作動を説明する。
【００３７】
駆動室４７ａと作動室４７ｂとはダイヤフラム４７ｃを挟んで仕切られ、かつ、ニードル弁４６はダイヤフラム４７ｃと一体的に変位するように構成されている。このとき、駆動室４７ａ内の圧力は、ノズル４１の絞り開度が大きくなる向きにニードル弁４６が変位するような力をダイヤフラム４７ｃに対して作用させ、一方、作動室４７ｂ内の圧力は、ノズル４１の絞り開度が小さくなる向きにニードル弁４６が変位するような力をダイヤフラム４７ｃに対して作用させる。
【００３８】
そして、駆動室４７ａ内の圧力が上昇して作動室４７ｂ内の圧力より大きくなると、図３に示すように、ノズル４１の絞り開度が大きくなるようにダイヤフラム４７ｃ及びニードル弁４６が変位するため、駆動室４７ａ内の圧力、すなわち高圧側の冷媒圧力上昇が抑制され、その圧力は、作動室４７ｂ内の圧力と同等となる。
【００３９】
逆に、駆動室４７ａ内の圧力が低下して作動室４７ｂ内の圧力より小さくなると、図４に示すように、ノズル４１の絞り開度が小さくなるようにダイヤフラム４７ｃ及びニードル弁４６が変位するため、駆動室４７ａ内の圧力、すなわち高圧側の冷媒圧力低下が抑制され、その圧力は、作動室４７ｂ内の圧力と同等となる。
【００４０】
したがって、ノズル４１の絞り開度は、高圧側の冷媒圧力と作動室４７ｂ内の圧力と略同一となるように機械的に制御されることとなる。
【００４１】
このとき、作動室４７ｂ内には、不活性ガスが封入されており、封入されたガスが凝縮しないことに加えて、ダイヤフラム４７ｃの変位量、及び駆動室４７ａに流入する冷媒の温度変化に対する封入ガスの圧力変化量は微少であるため、作動室４７ｂ内の圧力は、実用範囲内においては、略一定となる。したがって、機械式のアクチュエータ４７は、高圧側の冷媒圧力が、略一定となるようにノズル４１の絞り開度を調節することとなる。
【００４２】
次に、本実施形態の作用効果を述べる。
【００４３】
「発明が解決しようとする課題」の欄で述べたように、気温の高い夏場には、圧縮機１０に流入する冷媒の温度が上昇して圧縮機１０に吸入される冷媒のエントロピが小さくなるので、図２に示すように、気温の低い冬場と同等の給湯温度を得るためには、高圧側冷媒圧力、すなわち、圧縮機１０の吐出圧を冬場より高くする必要がある。
【００４４】
一方、給湯器に求められる給湯要求、すなわち給湯温度及び給湯水量は、年間を通して一定ではなく、気温の高い夏場における給湯要求は、気温の低い冬場における給湯要求に比べて小さい。
【００４５】
したがって、本実施形態のごとく、年間を通して高圧側冷媒圧力が略一定となるようにヒートポンプユニット１を制御すれば、気温の高い夏場には給湯温度が気温の低い冬場に比べて低下するものの、実用上問題はなく、むしろ、気温の高い夏場に合わせて水冷媒熱交換器２０や圧縮機１０等の高圧側機器の耐圧性を必要以上に高める必要がないので、給湯器の製造原価低減を図りつつ、給湯器の耐圧信頼性を高めることができる。
【００４６】
また、本実施形態では、作動室４７ｂ内に不活性ガスを封入した簡便な構造のアクチュエータ４７によりノズル４１の絞り開度を制御するので、電気式のアクチュエータを用いた場合に比べて、安価に高圧側冷媒圧力を制御することができる。
【００４７】
（第２実施形態）
第１実施形態では、仕切部材を薄膜状のダイヤフラム４７ｃにて構成したが、本実施形態は、図５に示すように、仕切部材を蛇腹状のベローズ４７ｆにて構成したものである。なお、本実施形態では、ベローズ４７ｆの内部が作動室４７ｂとなる。
【００４８】
これにより、第１実施形態に比べてニードル弁４６の変位量、すなわちストロークを大きく設定することが可能となる。
【００４９】
（第３実施形態）
本実施形態は、図６に示すように、仕切部材をＯリング等のシール手段４７ｈを介して摺動可能に配置されたピストン４７ｇにて構成したものである。
【００５０】
これにより、第１実施形態に比べてニードル弁４６の変位量、すなわちストロークを大きく設定することが可能となる。
【００５１】
（第４実施形態）
本実施形態は、図７に示すように、不活性ガスに加えて、仕切部材（この例では、ピストン４７ｇ）を駆動室４７ａ側に押圧する弾性力を仕切部材に作用させる弾性手段としてのコイルバネ４７ｊを作動室４７ｂ内に設けたものである。
【００５２】
なお、図７は第３実施形態に本実施形態を適用したものであるが、本実施形態は、これに限定されるものではなく、第１又は第２実施形態に対して本実施形態を適用することができる。
【００５３】
また、弾性手段としてのコイルバネ４７ｊの配置場所は、作動室４７ｂ内に限定されるものではなく、作動室４７ｂ外、例えば第２実施形態では、ベローズ４７ｆの外側や駆動室４７ａ側に配置してもよい。
【００５４】
（第５実施形態）
本実施形態は、蒸発器３０の除霜運転をすることができるようにしたものである。
【００５５】
具体的には、図８に示すように、エジェクタ４０にて減圧される前の高温・高圧冷媒を蒸発器３０の冷媒入口側（気液分離器５０側）に導く除霜回路６０を開閉する電磁式の開閉弁６１を設けるととともに、除霜回路６０にて導かれた高温・高圧冷媒が気液分離器５０に流れ込むことを防止する逆止弁６２を設けたものである。なお、エジェクタ４０は、第１〜４実施形態のいずれのものであってもよい。
【００５６】
次に、本実施形態の特徴的作動及びその効果を述べる。
【００５７】
１．通常運転（給湯水を加熱する運転）
開閉弁６１を閉じて圧縮機１０を稼動させる。これにより、第１〜４実施形態で述べたように、高圧側の冷媒圧力が略一定となるように制御された状態でヒートポンプユニット１が運転される。
【００５８】
２．除霜運転
開閉弁６１を開いた状態で圧縮機１０を稼動させる。これにより、高圧側の冷媒圧力が低下するので、駆動室４７ａ内の圧力が低下し、図４に示すように、ノズル４１の絞り開度が小さくなり、最終的にはノズル４１は全閉状態となる。
【００５９】
このため、圧縮機１０から吐出された高温の冷媒全量が除霜回路６０を経由して蒸発器３０に流入し、蒸発器３０を加熱して蒸発器３０の表面に付着した霜を融解させる。
【００６０】
そして、蒸発器３０を流出した冷媒は、混合部４２及びディフューザ４３を経由して気液分離器５０に流入し、再び、圧縮機１０にて加圧される。
【００６１】
以上に述べたように、本実施形態では、除霜回路６０及び開閉弁６１を追加するといった簡単な手段にて除霜運転を行うことができ、給湯器の製造原価上昇を抑制できる。
【００６２】
なお、図８では、水冷媒熱交換器２０の出口側から除霜回路６０に高温の冷媒を導入したが、本実施形態はこれに限定されるものではなく、水冷媒熱交換器２０の入口側又は水冷媒熱交換器２０の途中から除霜回路６０に高温の冷媒を導入してもよい。
【００６３】
（その他の実施形態）
上述の実施形態では、冷媒として二酸化炭素を用いたが本発明はこれに限定されるものではなく、例えばフロンを用いてもよい。なお、冷媒をフロンとした場合には、水冷媒熱交換器２０内の冷媒圧力は冷媒の臨界圧力以下であり、水冷媒熱交換器２０にて冷媒が凝縮する。
【００６４】
また、上述の実施形態では、アクチュエータ４７及びエジェクタ４０をステンレスで形成したが、耐食性及び必要な強度を備える材質であれば、本発明はこれに限定されるものではない。
【図面の簡単な説明】
【図１】本発明の第１実施形態に係る給湯器の模式図である。
【図２】エジェクタサイクルのｐ−ｈ線図である。
【図３】本発明の第１実施形態に係るエジェクタの模式図である。
【図４】本発明の第１実施形態に係るエジェクタの模式図である。
【図５】本発明の第２実施形態に係るエジェクタの模式図である。
【図６】本発明の第３実施形態に係るエジェクタの模式図である。
【図７】本発明の第４実施形態に係るエジェクタの模式図である。
【図８】本発明の第５実施形態に係る給湯器の模式図である。
【符号の説明】
４０…エジェクタ、４１…ノズル、４２…混合部、４３…ディフューザ、
４４…ボディ、４５…吸引室、４６…ニードル弁、
４７…アクチュエータ、４７ａ…駆動室、４７ｂ…作動室、
４７ｃ…ダイヤフラム、４７ｄ…ストッパ。[0001]
BACKGROUND OF THE INVENTION
The present invention relates to an ejector for vapor compression refrigeration cycle.
[0002]
[Challenges inventions to be Solved]
[0004]
An object of the present invention is to control the high-pressure-side refrigerant pressure at a lower cost than when an electric actuator is used .
[0005]
[Means for Solving the Problems]
In order to achieve the above object, according to the present invention, in the invention described in claim 1, a high-pressure side heat exchanger (20) that cools a high-temperature and high-pressure refrigerant compressed by the compressor (10), and a reduced pressure An ejector that has an evaporator (30) for evaporating the low-temperature and low-pressure refrigerant that is applied to a vapor compression refrigeration cycle that moves low-temperature heat to a high-temperature side, and is a high-pressure heat exchanger (20) The nozzle (41) that converts the pressure energy of the high-pressure refrigerant that has flowed out of the refrigerant into velocity energy and decompresses and expands the refrigerant, and the refrigerant that is injected from the nozzle (41) and the refrigerant that is sucked from the evaporator (30) are mixed. A pressure increasing unit (42, 43) that converts the velocity energy into pressure energy to increase the pressure of the refrigerant, and a needle valve (46) that is displaced in the axial direction of the nozzle (41) and adjusts the throttle opening of the nozzle (41). ) And high A drive chamber (47a) filled with high-pressure refrigerant flowing out from the side heat exchanger (20) and flowing into the nozzle (41), and a working chamber disposed adjacent to the drive chamber (47a) and filled with an inert gas (47b), the drive chamber (47a) and the working chamber (47b) are partitioned, and the needle valve is displaced according to the pressure difference between the pressure in the drive chamber (47a) and the pressure in the working chamber (47b). a partition member for displacing the (46) (4 7g), and a housing forming an outer shell of the drive chamber (47a) and working chamber (47b) (47e), the partition member via the sealing means (47h) The piston (47g) is slidably disposed on the inner surface of the housing (47e) .
[0006]
As a result, the high-pressure side refrigerant pressure can be controlled to be substantially constant at a lower cost than when an electric actuator is used.
[0009]
In the invention described in claim 2, the partition member (4 7 g), as the pressure in the driving chamber (47a) is greater than the pressure in the working chamber (47b) aperture size of the nozzle (41) increases The needle valve (46) is displaced, and when the pressure in the drive chamber (47a) becomes smaller than the pressure in the working chamber (47b), the needle valve (46) is displaced so that the throttle opening of the nozzle (41) becomes smaller. It is comprised as follows.
[0010]
Further, as in the third aspect of the invention, the compressor (10) may compress the refrigerant to a critical pressure or higher.
[0011]
Further, as in the invention described in claim 4, carbon dioxide may be used as the refrigerant.
[0017]
Also, as in the invention described in claim 5, may be provided with elastic means exerting an elastic force for displacing the partition member (47 g) to the drive chamber (47a) side to the partition member (47 g) (47j) .
[0020]
Incidentally, the reference numerals in parentheses of each means described above are an example showing the correspondence with the specific means described in the embodiments described later.
[0021]
DETAILED DESCRIPTION OF THE INVENTION
(First embodiment)
In the present embodiment, a vapor compression refrigeration cycle having an ejector-type decompression device is used as the heat pump unit 1, and FIG. 1 is a schematic diagram of a water heater according to the present embodiment.
[0022]
The compressor 10 sucks and compresses the refrigerant, and the water-refrigerant heat exchanger 20 cools the refrigerant by heating the hot-water supply by exchanging heat between the refrigerant discharged from the compressor 10 and the hot-water supply in an opposed flow state. It is a high-pressure side heat exchanger.
[0023]
The compressor 10 is driven by an electric motor (not shown), and when the heating capacity of the water-refrigerant heat exchanger 20 is increased, the rotation speed of the compressor 10 is increased and discharged from the compressor 10. When increasing the flow rate of the refrigerant and reducing the heating capacity, the flow rate of the refrigerant discharged from the compressor 10 is decreased by decreasing the rotational speed of the compressor 10.
[0024]
Incidentally, in the present embodiment, since carbon dioxide is used as the refrigerant, the refrigerant pressure in the water refrigerant heat exchanger 20 is equal to or higher than the critical pressure of the refrigerant, and the refrigerant is condensed in the water refrigerant heat exchanger 20. The temperature distribution is such that the refrigerant temperature decreases from the refrigerant inlet side toward the refrigerant outlet side.
[0025]
The evaporator 30 is a low-pressure side heat exchanger that evaporates the liquid phase refrigerant by evaporating the liquid phase refrigerant by exchanging heat between the outdoor air and the liquid phase refrigerant, and the ejector 40 decompresses and expands the refrigerant. The vapor phase refrigerant evaporated by the evaporator 30 is sucked and the expansion energy is converted into pressure energy to increase the suction pressure of the compressor 10. Details of the ejector 40 will be described later.
[0026]
The gas-liquid separator 50 is a gas-liquid separator that stores the refrigerant by flowing the refrigerant flowing out from the ejector 40 into the vapor-phase refrigerant and the liquid-phase refrigerant. The 50 gas-phase refrigerant outlets are connected to the suction side of the compressor 10 and the liquid-phase refrigerant outlets are connected to the inflow side on the evaporator 30 side.
[0027]
FIG. 2 is a ph diagram showing the entire macro operation of the ejector cycle. Since the macro operation is the same as the known ejector cycle, in this embodiment, the macro operation of the entire ejector cycle is performed. Description of is omitted. Incidentally, the symbol indicated by ● in FIG. 2 indicates the state of the refrigerant at the symbol position indicated by ● in FIG.
[0028]
Next, the structure of the ejector 40 will be described based on FIG.
[0029]
The ejector 40 sucks the vapor phase refrigerant evaporated in the evaporator 30 by the nozzle 41 that converts the pressure energy of the high-pressure refrigerant that flows into velocity energy to decompress and expand the refrigerant, and the high-speed refrigerant flow that is injected from the nozzle 41. While mixing the refrigerant flow injected from the nozzle 41 and the refrigerant injected from the nozzle 41 and the refrigerant sucked from the evaporator 30, the velocity energy is converted into pressure energy to change the pressure of the refrigerant. It consists of a diffuser 43 and the like for boosting.
[0030]
In the mixing unit 42, since the sum of the momentum of the refrigerant flow injected from the nozzle 41 and the momentum of the refrigerant flow sucked into the ejector 40 from the evaporator 30 is preserved, the mixing unit 42 However, the static pressure of the refrigerant increases. On the other hand, in the diffuser 43, the dynamic pressure of the refrigerant is converted into a static pressure by gradually increasing the passage cross-sectional area. Therefore, in the ejector 40, the refrigerant pressure is increased by both the mixing unit 42 and the diffuser 43. . Therefore, the mixing unit 42 and the diffuser 43 are collectively referred to as a boosting unit.
[0031]
That is, in the ideal ejector 40, the refrigerant pressure increases so that the sum of the momentums of the two refrigerant flows is stored in the mixing unit 42, and the refrigerant pressure increases so that energy is stored in the diffuser 43. I want to see that.
[0032]
Incidentally, a suction chamber 45 formed by the body 44 is formed around the nozzle 41, and the gas-phase refrigerant sucked from the evaporator 30 flows to the mixing unit 42 via the suction chamber 45.
[0033]
The nozzle 41 is a divergent nozzle having a throat portion with the smallest passage area in the middle of the passage. The throttle opening degree of the nozzle 41, that is, the throat opening degree is such that the refrigerant pressure on the high pressure side is substantially constant. It is controlled by the needle valve 46 so as to be. The needle valve 46 has a conical taper shape with a sharp tip, and is displaced in the axial direction by a mechanical actuator 47 in the nozzle 41.
[0034]
Here, the mechanical actuator 47 partitions the driving chamber 47a filled with the high-pressure refrigerant flowing into the nozzle 41 from the working chamber 47b filled with inert gas, and the pressure in the driving chamber 47a and the working chamber 47b. A diaphragm 47c as a partitioning member that displaces the needle valve 46 by displacing it according to a pressure difference with the pressure of the nozzle 47, a stopper 47d that is disposed on the drive chamber 47a side of the diaphragm 47c and restricts the maximum displacement of the diaphragm 47c, and the like The housing 47a and the working chamber 47b are made of a stainless housing 47e that forms the outer shell.
[0035]
Incidentally, although nitrogen gas is used as the inert gas in the present embodiment, an inert gas such as helium gas or argon gas may be used. Moreover, in this embodiment, the diaphragm 47c and the needle valve 46 are made of stainless steel, and both are brazed and joined. However, the present embodiment is not limited to this.
[0036]
Next, the operation of the ejector 40 according to the present embodiment will be described focusing on the operation of the needle valve 46.
[0037]
The drive chamber 47a and the working chamber 47b are partitioned with the diaphragm 47c interposed therebetween, and the needle valve 46 is configured to be displaced integrally with the diaphragm 47c. At this time, the pressure in the drive chamber 47a applies a force to the diaphragm 47c so that the needle valve 46 is displaced in the direction in which the throttle opening of the nozzle 41 increases, while the pressure in the working chamber 47b is A force is applied to the diaphragm 47c so that the needle valve 46 is displaced in a direction in which the throttle opening of the nozzle 41 becomes smaller.
[0038]
When the pressure in the drive chamber 47a rises and becomes larger than the pressure in the working chamber 47b, the diaphragm 47c and the needle valve 46 are displaced so that the throttle opening of the nozzle 41 is increased as shown in FIG. The pressure in the drive chamber 47a, that is, the increase in the refrigerant pressure on the high pressure side is suppressed, and the pressure is equivalent to the pressure in the working chamber 47b.
[0039]
On the contrary, when the pressure in the drive chamber 47a decreases and becomes smaller than the pressure in the working chamber 47b, as shown in FIG. 4, the diaphragm 47c and the needle valve 46 are displaced so that the throttle opening of the nozzle 41 becomes small. Therefore, the pressure in the drive chamber 47a, that is, the refrigerant pressure drop on the high pressure side is suppressed, and the pressure is equivalent to the pressure in the working chamber 47b.
[0040]
Therefore, the throttle opening degree of the nozzle 41 is mechanically controlled so as to be substantially the same as the refrigerant pressure on the high pressure side and the pressure in the working chamber 47b.
[0041]
At this time, an inert gas is sealed in the working chamber 47b, and in addition to the sealed gas not condensing, the amount of displacement of the diaphragm 47c and the temperature change of the refrigerant flowing into the driving chamber 47a are sealed. Since the amount of gas pressure change is very small, the pressure in the working chamber 47b is substantially constant within the practical range. Therefore, the mechanical actuator 47 adjusts the throttle opening of the nozzle 41 so that the refrigerant pressure on the high pressure side is substantially constant.
[0042]
Next, the function and effect of this embodiment will be described.
[0043]
As described in the section “Problems to be Solved by the Invention”, in summer when the temperature is high, the temperature of the refrigerant flowing into the compressor 10 rises and the entropy of the refrigerant sucked into the compressor 10 decreases. Therefore, as shown in FIG. 2, in order to obtain a hot water supply temperature equivalent to that in winter when the temperature is low, the high-pressure side refrigerant pressure, that is, the discharge pressure of the compressor 10 needs to be higher than that in winter.
[0044]
On the other hand, the hot water supply requirement required for the water heater, that is, the hot water supply temperature and the amount of hot water supply is not constant throughout the year, and the hot water supply requirement in summer when the temperature is high is smaller than the hot water requirement in winter when the temperature is low.
[0045]
Therefore, as in the present embodiment, by controlling the heat pump unit 1 as the high-pressure side refrigerant pressure throughout the year is substantially constant, although the hot water supply temperature is high summer of temperature is reduced as compared with the low temperature winter, practical There is no problem, rather, it is not necessary to increase the pressure resistance of the high-pressure side equipment such as the water-refrigerant heat exchanger 20 and the compressor 10 in accordance with the summertime when the temperature is high. However, the pressure resistance reliability of the water heater can be improved.
[0046]
Further, in this embodiment, the throttle opening degree of the nozzle 41 is controlled by the actuator 47 having a simple structure in which the inert gas is sealed in the working chamber 47b, so that it is less expensive than the case where an electric actuator is used. The high-pressure side refrigerant pressure can be controlled.
[0047]
(Second Embodiment)
In the first embodiment, the partition member is configured by a thin film diaphragm 47c, but in the present embodiment, the partition member is configured by a bellows-shaped bellows 47f as shown in FIG. In the present embodiment, the inside of the bellows 47f is the working chamber 47b.
[0048]
Thereby, it becomes possible to set the displacement amount of the needle valve 46, that is, the stroke larger than that of the first embodiment.
[0049]
(Third embodiment)
In the present embodiment, as shown in FIG. 6, the partition member is configured by a piston 47 g slidably disposed via a sealing means 47 h such as an O-ring.
[0050]
Thereby, it becomes possible to set the displacement amount of the needle valve 46, that is, the stroke larger than that of the first embodiment.
[0051]
(Fourth embodiment)
In this embodiment, as shown in FIG. 7, in addition to the inert gas, a coil spring as an elastic means that acts on the partition member with an elastic force that presses the partition member (in this example, the piston 47g) toward the drive chamber 47a. 47j is provided in the working chamber 47b.
[0052]
FIG. 7 shows the case where the present embodiment is applied to the third embodiment. However, the present embodiment is not limited to this, and the present embodiment is applied to the first or second embodiment. can do.
[0053]
Further, the arrangement location of the coil spring 47j as the elastic means is not limited to the inside of the working chamber 47b, and is arranged outside the working chamber 47b, for example, outside the bellows 47f or the driving chamber 47a side in the second embodiment. Also good.
[0054]
(Fifth embodiment)
In the present embodiment, the evaporator 30 can be defrosted.
[0055]
Specifically, as shown in FIG. 8, the defrosting circuit 60 that opens the high-temperature / high-pressure refrigerant before being decompressed by the ejector 40 to the refrigerant inlet side (gas-liquid separator 50 side) of the evaporator 30 is opened and closed. An electromagnetic on-off valve 61 is provided, and a check valve 62 for preventing the high-temperature / high-pressure refrigerant introduced by the defrosting circuit 60 from flowing into the gas-liquid separator 50 is provided. The ejector 40 may be any one of the first to fourth embodiments.
[0056]
Next, the characteristic operation of this embodiment and its effect will be described.
[0057]
1. Normal operation (operation to heat hot water)
The on-off valve 61 is closed and the compressor 10 is operated. Thereby, as described in the first to fourth embodiments, the heat pump unit 1 is operated in a state in which the refrigerant pressure on the high pressure side is controlled to be substantially constant.
[0058]
2. The compressor 10 is operated with open Joshimoun rolling-off valve 61. As a result, the refrigerant pressure on the high pressure side decreases, so the pressure in the drive chamber 47a decreases, and as shown in FIG. 4, the throttle opening of the nozzle 41 decreases, and finally the nozzle 41 is fully closed. It becomes.
[0059]
For this reason, the entire amount of the high-temperature refrigerant discharged from the compressor 10 flows into the evaporator 30 via the defrost circuit 60, and heats the evaporator 30 to melt the frost attached to the surface of the evaporator 30.
[0060]
Then, the refrigerant that has flowed out of the evaporator 30 flows into the gas-liquid separator 50 via the mixing unit 42 and the diffuser 43, and is pressurized again by the compressor 10.
[0061]
As described above, in the present embodiment, the defrosting operation can be performed by simple means such as adding the defrosting circuit 60 and the on-off valve 61, and an increase in the manufacturing cost of the water heater can be suppressed.
[0062]
In FIG. 8, the high-temperature refrigerant is introduced into the defrosting circuit 60 from the outlet side of the water-refrigerant heat exchanger 20, but this embodiment is not limited to this, and the inlet of the water-refrigerant heat exchanger 20. A high-temperature refrigerant may be introduced into the defrosting circuit 60 from the side or in the middle of the water refrigerant heat exchanger 20.
[0063]
(Other embodiments)
In the above-described embodiment, carbon dioxide is used as the refrigerant. However, the present invention is not limited to this, and for example, chlorofluorocarbon may be used. When the refrigerant is chlorofluorocarbon, the refrigerant pressure in the water refrigerant heat exchanger 20 is equal to or lower than the critical pressure of the refrigerant, and the water refrigerant heat exchanger 20 condenses the refrigerant.
[0064]
In the above embodiment, the actuator 47 and the ejector 40 are made of stainless steel. However, the present invention is not limited to this as long as the material has corrosion resistance and necessary strength.
[Brief description of the drawings]
FIG. 1 is a schematic view of a water heater according to a first embodiment of the present invention.
FIG. 2 is a ph diagram of an ejector cycle.
FIG. 3 is a schematic diagram of an ejector according to the first embodiment of the present invention.
FIG. 4 is a schematic diagram of an ejector according to the first embodiment of the present invention.
FIG. 5 is a schematic diagram of an ejector according to a second embodiment of the present invention.
FIG. 6 is a schematic diagram of an ejector according to a third embodiment of the present invention.
FIG. 7 is a schematic diagram of an ejector according to a fourth embodiment of the present invention.
FIG. 8 is a schematic view of a water heater according to a fifth embodiment of the present invention.
[Explanation of symbols]
40 ... ejector, 41 ... nozzle, 42 ... mixing section, 43 ... diffuser,
44 ... Body, 45 ... Suction chamber, 46 ... Needle valve,
47 ... Actuator, 47a ... Drive chamber, 47b ... Working chamber,
47c: Diaphragm, 47d: Stopper.

Claims (5)

圧縮機（１０）にて圧縮された高温高圧の冷媒を放冷する高圧側熱交換器（２０）、及び減圧された低温低圧の冷媒を蒸発させる蒸発器（３０）を有して低温側の熱を高温側に移動させる蒸気圧縮式冷凍サイクルに適用されるエジェクタであって、
前記高圧側熱交換器（２０）から流出した高圧の冷媒の圧力エネルギーを速度エネルギーに変換して冷媒を減圧膨張させるノズル（４１）と、
前記ノズル（４１）から噴射する冷媒と前記蒸発器（３０）から吸引した冷媒とを混合させながら速度エネルギーを圧力エネルギーに変換して冷媒の圧力を昇圧させる昇圧部（４２、４３）と、
前記ノズル（４１）の軸線方向に変位し、前記ノズル（４１）の絞り開度を調節するニードル弁（４６）と、
前記高圧側熱交換器（２０）から流出して前記ノズル（４１）に流入する高圧の冷媒が充満する駆動室（４７ａ）と、
前記駆動室（４７ａ）に隣接配置され、不活性ガスが封入された作動室（４７ｂ）と、 前記駆動室（４７ａ）と前記作動室（４７ｂ）とを仕切るとともに、前記駆動室（４７ａ）内の圧力と前記作動室（４７ｂ）内の圧力との圧力差に応じて変位して前記ニードル弁（４６）を変位させる仕切部材（４７ｇ）と、
前記駆動室（４７ａ）及び前記作動室（４７ｂ）の外殻を形成するハウジング（４７ｅ）とを備え、
前記仕切部材は、シール手段（４７ｈ）を介して前記ハウジング（４７ｅ）の内面に摺動可能に配置されたピストン（４７ｇ）であることを特徴とするエジェクタ。A high-pressure side heat exchanger (20) that cools the high-temperature and high-pressure refrigerant compressed by the compressor (10), and an evaporator (30) that evaporates the decompressed low-temperature and low-pressure refrigerant, An ejector applied to a vapor compression refrigeration cycle for transferring heat to a high temperature side,
A nozzle (41) for converting the pressure energy of the high-pressure refrigerant flowing out of the high-pressure side heat exchanger (20) into velocity energy to decompress and expand the refrigerant;
A pressure increasing section (42, 43) for increasing the pressure of the refrigerant by converting the velocity energy into pressure energy while mixing the refrigerant injected from the nozzle (41) and the refrigerant sucked from the evaporator (30);
A needle valve (46) that is displaced in the axial direction of the nozzle (41) and adjusts a throttle opening of the nozzle (41);
A drive chamber (47a) filled with high-pressure refrigerant flowing out of the high-pressure side heat exchanger (20) and flowing into the nozzle (41);
The working chamber (47b) disposed adjacent to the driving chamber (47a) and filled with an inert gas is partitioned from the driving chamber (47a) and the working chamber (47b), and the driving chamber (47a) of pressure and the working chamber and the partition displaces the needle valve is displaced according to the pressure difference (46) between the pressure in (47b) members (4 7 g),
A housing (47e) forming an outer shell of the drive chamber (47a) and the working chamber (47b);
The ejector according to claim 1, wherein the partition member is a piston (47g) slidably disposed on an inner surface of the housing (47e) via a sealing means (47h) . 前記仕切部材（４７ｇ）は、前記駆動室（４７ａ）内の圧力が前記作動室（４７ｂ）内の圧力より大きくなると前記ノズル（４１）の絞り開度が大きくなるように前記ニードル弁（４６）を変位させ、前記駆動室（４７ａ）内の圧力が前記作動室（４７ｂ）内の圧力より小さくなると前記ノズル（４１）の絞り開度が小さくなるように前記ニードル弁（４６）を変位させるように構成されていることを特徴とする請求項１に記載の蒸気圧縮式冷凍サイクル。The partition member (4 7 g), the drive chamber (47a) in pressure the working chamber (47b) in said needle valve such that the diaphragm opening of the larger and the nozzle (41) from the pressure increases in (46 ) And the needle valve (46) is displaced so that the throttle opening of the nozzle (41) becomes smaller when the pressure in the drive chamber (47a) becomes smaller than the pressure in the working chamber (47b). The vapor compression refrigeration cycle according to claim 1, wherein the vapor compression refrigeration cycle is configured as described above. 前記圧縮機（１０）は冷媒を冷媒の臨界圧力以上まで圧縮することを特徴とする請求項１又は２に記載のエジェクタ。  The ejector according to claim 1 or 2, wherein the compressor (10) compresses the refrigerant to a critical pressure or higher of the refrigerant. 冷媒として二酸化炭素を用いたことを特徴とする請求項１又は２に記載のエジェクタ。  The ejector according to claim 1 or 2, wherein carbon dioxide is used as a refrigerant. 前記仕切部材（４７ｇ）を前記駆動室（４７ａ）側に変位させる弾性力を前記仕切部材（４７ｇ）に作用させる弾性手段（４７ｊ）を備えることを特徴とする請求項１ないし４のいずれか１つに記載のエジェクタ。Any of the partition member (47 g) the drive chamber claims 1, characterized in that it comprises an elastic means exerting an elastic force for displacing the (47a) side to the partition member (47 g) (47j) 4 The ejector as described in one.
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