EP3290825B1 - Kühlvorrichtung - Google Patents

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Publication number
EP3290825B1
EP3290825B1 EP16786103.8A EP16786103A EP3290825B1 EP 3290825 B1 EP3290825 B1 EP 3290825B1 EP 16786103 A EP16786103 A EP 16786103A EP 3290825 B1 EP3290825 B1 EP 3290825B1
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EP
European Patent Office
Prior art keywords
refrigerant
expansion valve
pipe
degree
heat exchanger
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Active
Application number
EP16786103.8A
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English (en)
French (fr)
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EP3290825A1 (de
EP3290825A4 (de
Inventor
Masaaki Takegami
Azuma Kondou
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Daikin Industries Ltd
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Daikin Industries Ltd
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Publication of EP3290825A1 publication Critical patent/EP3290825A1/de
Publication of EP3290825A4 publication Critical patent/EP3290825A4/de
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Classifications

    • 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
    • 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
    • F25B31/00—Compressor arrangements
    • F25B31/002—Lubrication
    • F25B31/004—Lubrication oil recirculating 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
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2509—Economiser valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2101—Temperatures in a bypass
    • 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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the injection refrigerant temperature sensor (82) is installed on a portion of the second main injection pipe (54n) between the junction (P6) and the intermediate expansion valves (36a, 36b, 36c) to sense the temperature of a refrigerant at its installation site as the temperature of a refrigerant flowing through a portion of the second main injection pipe (54n) between the junction (P6) and the intermediate expansion valves (36a, 36b, 36c) (hereinafter referred to as the injection refrigerant temperature (Tinj)).
  • the refrigerant circuit (20) performs a refrigeration cycle in which the heat-source-side heat exchanger (33) functions as a condenser, the supercooling heat exchanger (34) functions as a supercooler, and the utilization-side heat exchangers (61) function as evaporators.
  • a refrigerant discharged from the compressors (31a, 31b, 31c) passes through the oil separator (41) in the discharge refrigerant pipe (51), then flows through the four-way valve (32) into the heat-source-side heat exchanger (33), dissipates heat to the heat-source-side air (e.g., outdoor air) in the heat-source-side heat exchanger (33), and condenses.
  • the heat-source-side air e.g., outdoor air
  • the flow rate (injection amount) of the refrigerant flowing into the intermediate port of the compressor (31a, 31b, 31c) can be adjusted by adjusting the degree of opening of the intermediate expansion valve (36a, 36b, 36c).
  • the degree of opening of the intermediate expansion valve (36a, 36b, 36c) can be adjusted.
  • the degree of opening of the heat-source-side expansion valve (38) is adjusted such that the degree of superheat of the refrigerant at the outlet of the heat-source-side heat exchanger (33) is equal to a predetermined target degree of superheat.
  • the oil return expansion valve (42) is placed in a fully-closed state.
  • the utilization-side open/close valve (62) is placed in the open state, and the utilization-side expansion valve (63) is placed in the fully-open state.
  • the refrigerant discharged from the compressors (31a, 31b, 31c) passes through the oil separator (41) in the discharge refrigerant pipe (51), then passes through the four-way valve (32) and the gas stop valve (V2) in this order, and flows into the gas interconnecting pipe (15).
  • the refrigerant that has flowed into the gas interconnecting pipe (15) flows into the utilization-side gaseous refrigerant pipes (72) of the utilization-side units (12).
  • the refrigerant that has flowed into the utilization-side gaseous refrigerant pipe (72) flows into the utilization-side heat exchanger (61), and dissipates heat in the utilization-side heat exchanger (61) to condense.
  • the refrigerant that has flowed into the liquid interconnecting pipe (14) flows through the liquid stop valve (VI) into the third heat-source-side liquid pipe (53c).
  • the refrigerant that has flowed into the third heat-source-side liquid pipe (53c) flows into the first connection pipe (55), passes through the third check valve (CV3) in the first connection pipe (55), and flows into the first heat-source-side liquid pipe (53a).
  • the refrigerant that has flowed into the first heat-source-side liquid pipe (53a) passes through the receiver (37), the second heat-source-side liquid pipe (53b), the first channels (34a) of the supercooling heat exchanger (34) in this order, and flows into the third heat-source-side liquid pipe (53c).
  • the refrigerant that has flowed out of the heat-source-side heat exchanger (33) passes through the four-way valve (32) and the suction refrigerant pipe (52) in this order, and is sucked into the suction ports of the compressors (31a, 31b, 31c).
  • the controller (13) performs a first degree-of-opening adjusting operation (steps (ST11-ST13)) every time a predetermined operating time elapses in the cooling mode.
  • the controller (13) adjusts the degree of opening of the intermediate expansion valve (36a, 36b, 36c) such that the discharged refrigerant temperature (Td) is below a predetermined higher discharged refrigerant temperature threshold (Tdth).
  • the controller (13) performs the first degree-of-opening adjusting operation for each of the first through third intermediate expansion valves (36a-36c). For example, the controller (13) performs the first degree-of-opening adjusting operation for the first intermediate expansion valve (36a) associated with the first compressor (31a), based on the value sensed by the first discharged refrigerant temperature sensor (81a). In the first degree-of-opening adjusting operation, processes indicated below are performed.
  • the degree of opening of the intermediate expansion valve (36a, 36b, 36c) is adjusted such that the degree of superheat of the refrigerant discharged from the compressor (31a, 31b, 31c) is equal to the predetermined target degree of superheat, the flow rate (injection amount) of the refrigerant flowing into the intermediate port of the compressor (31a, 31b, 31c) can be appropriately adjusted.
  • the controller (13) performs the process shown in FIG. 5 (steps (ST20-ST24)) every time a predetermined operating time elapses in the cooling mode.
  • the controller (13) determines whether or not the injection refrigerant temperature (Tinj) is above the freezing temperature threshold (Tfth). If the injection refrigerant temperature (Tinj) is above the freezing temperature threshold (Tfth), the process proceeds to step (ST22). If not, the process proceeds to step (ST23).
  • the controller (13) reduces the degree of opening of the supercooling expansion valve (35) by a predetermined amount (step (ST22)). This can reduce the pressure of the refrigerant flowing from the supercooling expansion valve (35) into the second channels (34b) of the supercooling heat exchanger (34) in the injection pipe (54). As a result, the degree of subcooling of the refrigerant in the supercooling heat exchanger (34) can be increased.
  • step (ST22) If, in step (ST22), the supercooling expansion valve (35) has a minimum degree of opening (e.g., a fully-closed state), the controller (13) keeps the degree of opening of the supercooling expansion valve (35) at the minimum degree of opening. If, in steps (ST23, ST24), the supercooling expansion valve (35) has a maximum degree of opening (e.g., a fully-open state), the controller (13) keeps the degree of opening of the supercooling expansion valve (35) at the maximum degree of opening.
  • a minimum degree of opening e.g., a fully-closed state
  • the controller (13) keeps the degree of opening of the supercooling expansion valve (35) at the maximum degree of opening.
  • the controller (13) intermittently places the oil return expansion valve (42) in an open state, so that the flow rate of refrigerating machine oil passing through the oil return pipe (57) within a predetermined unit period of time (i.e., the oil return amount) increases by a predetermined rate (step (ST33)).
  • the controller (13) intermittently places the oil return expansion valve (42) in the open state so that the period of time during which the oil return expansion valve (42) is placed in the open state within a predetermined period of time increases.
  • the controller (13) may increase the degree of opening of the open oil return expansion valve (42).
  • Increasing the flow rate of the refrigerating machine oil (relatively high-temperature refrigerating machine oil) passing through the oil return pipe (57) within a predetermined unit period of time can increase the temperature of the refrigerant flowing through the portion of the injection pipe (54) between the junction (P6) of the injection pipe (54) and the oil return pipe (57) and the intermediate expansion valves (36a, 36b, 36c) (in this example, the injection refrigerant temperature (Tinj)).
  • step (ST33) If, in step (ST33), the flow rate of the refrigerating machine oil passing through the oil return pipe (57) within a predetermined unit period of time (i.e., the oil return amount) is highest, the controller (13) controls the opening/closing of the oil return expansion valve (42) to keep the oil return amount at the highest flow rate. Specifically, if a period of time during which the oil return expansion valve (42) is in the open state within a predetermined unit period of time is longest (e.g., equal to the unit period of time), the controller (13) controls the opening/closing of the oil return expansion valve (42) to keep the period of time during which the valve is in the open state at the longest period of time.
  • the controller (13) may control the opening/closing of the oil return expansion valve (42) to keep the degree of opening of the open oil return expansion valve (42) at the highest degree of opening.
  • the above-mentioned refrigeration apparatus is useful as a refrigeration apparatus which cools an internal space, etc.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Claims (6)

  1. Kältegerät, das umfasst:
    einen Kühlkreis (20), der einen Kompressor (31a, 31b, 31c), einen wärmequellenseitigen Wärmetauscher (33), einen nutzungsseitigen Wärmetauscher (61), ein Flüssigkältemittelrohr (50), das ein Flüssigkeitsende des wärmequellenseitigen Wärmetauschers (33) mit einem Flüssigkeitsende des nutzungsseitigen Wärmetauschers (61) verbindet, ein Einspritzrohr (54), das einen Zwischenabschnitt (P1) des Flüssigkältemittelrohrs (50) mit einer Zwischenöffnung des Kompressors (31a, 31b, 31c) verbindet, einen Unterkühlungswärmetauscher (34), der mit dem Flüssigkältemittelrohr (50) und dem Einspritzrohr (54) verbunden ist, um Wärme zwischen einem Kältemittel, das durch das Flüssigkältemittelrohr (50) fließt, und einem Kältemittel, das durch das Einspritzrohr (54) fließt, auszutauschen, ein Unterkühlungsexpansionsventil (35), das auf einem Abschnitt des Einspritzrohrs (54) zwischen dem Zwischenabschnitt (P1) des Flüssigkältemittelrohrs (50) und dem Unterkühlungswärmetauscher (34) bereitgestellt ist, und ein Zwischenexpansionsventil (36a, 36b, 36c), das auf einem Abschnitt des Einspritzrohrs (54) zwischen dem Unterkühlungswärmetauscher (34) und der Zwischenöffnung des Kompressors (31a, 31b, 31c) bereitgestellt ist, beinhaltet, umfassend:
    einen Steuerabschnitt (13), der dazu konfiguriert ist, einen ersten und einen zweiten Öffnungsgradanpassvorgang in einem Kühlmodus auszuführen, bei dem der Kühlkreis (20) einen Kühlzyklus ausführt, bei dem der wärmequellenseitige Wärmetauscher (33) als ein Kondensator funktioniert, der Unterkühlungswärmetauscher (34) als ein Unterkühler funktioniert, und der nutzungsseitige Wärmetauscher (61) als ein Verdampfer funktioniert, wobei ein Öffnungsgrad des Zwischenexpansionsventils (36a, 36b, 36c) bei dem ersten Öffnungsgradanpassvorgang derart angepasst wird, dass eine Temperatur (Td) eines Kältemittels, das aus dem Kompressor (31a, 31b, 31c) ausgelassen wird, unter einem höheren Temperaturschwellenwert des ausgelassenen Kältemittels (Tdth) liegt,
    gekennzeichnet dadurch,
    dass ein Öffnungsgrad des Unterkühlungsexpansionsventils (35) bei dem zweiten Öffnungsgradanpassvorgang derart angepasst wird, dass eine Temperatur eines Kältemittels, das durch einen Abschnitt des Einspritzrohrs (54) zwischen dem Unterkühlungswärmetauscher (34) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, über einem vorbestimmten Gefriertemperaturschwellenwert (Tfth) liegt.
  2. Kältegerät nach Anspruch 1, wobei
    falls die Temperatur (Td) des Kältemittels, das aus dem Kompressor (31a, 31b, 31c) ausgelassen wird, unter dem höheren Temperaturschwellenwert (Tdth) des ausgelassenen Kältemittels liegt, der Steuerabschnitt (13) den zweiten Öffnungsgradanpassvorgang ausführt, und, falls die Temperatur (Td) des Kältemittels, das von dem Kompressor (31a, 31b, 31c) ausgelassen wird, nicht unter dem höheren Temperaturschwellenwert des ausgelassenen Kältemittels (Tdth) liegt, der Steuerabschnitt (13) den Öffnungsgrad des Unterkühlungsexpansionsventil (35) erhöht.
  3. Kältegerät nach Anspruch 1 oder 2, wobei
    bei dem ersten Öffnungsgradanpassvorgang, falls sie Temperatur (Td) des aus dem Kompressor (31a, 31b, 31c) ausgelassenen Kältemittels unter dem höheren Temperaturschwellenwert des ausgelassenen Kältemittels (Tdth) liegt, der Steuerabschnitt (13) den Öffnungsgrad des Zwischenexpansionsventils (36a, 36b, 36c) derart anpasst, dass ein Überhitzegrad des Kältemittels, das aus dem Kompressor (31a, 31b, 31c) ausgelassen wird, gleich einem vorbestimmten Überhitzezielgrad liegt, und falls die Temperatur (Td) des Kältemittels, das aus dem Kompressor (31a, 31b, 31c) ausgelassen wird, nicht unter dem höheren Temperaturschwellenwert des ausgelassenen Kältemittels (Tdth) liegt, der Steuerabschnitt (13) den Öffnungsgrad des Zwischenexpansionsventils (36a, 36b, 36c) erhöht.
  4. Kältegerät nach einem der Ansprüche 1-3, wobei
    bei dem zweiten Öffnungsgradanpassvorgang, falls die Temperatur des Kältemittels, das durch den Abschnitt des Einspritzrohrs (54) zwischen dem Unterkühlungswärmetauscher (34) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, über dem Gefriertemperaturschwellenwert (Tfth) liegt, der Steuerabschnitt (13) den Öffnungsgrad des Unterkühlungsexpansionsventils (35) reduziert, und falls die Temperatur des Kältemittels, das durch den Abschnitt des Einspritzrohrs (54) zwischen dem Unterkühlungswärmetauscher (34) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, nicht über dem Gefriertemperaturschwellenwert (Tfth) liegt, der Steuerabschnitt (13) den Öffnungsgrad des Unterkühlungsexpansionsventils (35) erhöht.
  5. Kältegerät nach einem der Ansprüche 1-4, wobei
    der Kühlkreis (20) einen Ölabscheider (41) beinhaltet, der dazu konfiguriert ist, Kühlmaschinenöl von dem Kältemittel, das aus dem Kompressor (31a, 31b, 31c) ausgelassen wird, abzuscheiden, wobei ein Ölrückflussrohr (57) zwei Enden aufweist, die mit dem Ölabscheider (41) bzw. mit einem Zwischenabschnitt des Einspritzrohrs (54) zwischen dem Unterkühlungswärmetauscher (34) und dem Zwischenexpansionsventil (36a, 36b, 36c) verbunden sind, sowie ein Ölrückflussexpansionsventil (42), das an dem Ölrückflussrohr (57) bereitgestellt ist, aufweist, und
    in dem Kühlmodus der Steuerabschnitt (13) einen dritten Öffnungsgradanpassvorgang ausführt, bei dem ein Öffnungsgrad des Ölrückflussexpansionsventils (42) derart angepasst wird, dass eine Temperatur eines Kältemittels, das durch einen Abschnitt des Einspritzrohrs (54) zwischen einem Übergang (P6) des Einspritzrohrs (54) und dem Ölrückflussrohr (57) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, über dem Gefriertemperaturschwellenwert (Tfth) liegt.
  6. Kältegerät nach Anspruch 5, wobei
    bei dem dritten Öffnungsgradanpassvorgang, falls die Temperatur des Kältemittels, das durch den Abschnitt des Einspritzrohrs (54) zwischen dem Übergang (P6) des Einspritzrohrs (54) und dem Ölrückflussrohr (57) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, über dem Gefriertemperaturschwellenwert (Tfth) liegt, der Steuerabschnitt (13) intermittierend das Ölrückflussexpansionsventil (42) derart in einen offenen Zustand bringt, dass eine Flussrate des Kühlmaschinenöls, das innerhalb einer vorbestimmten Zeitraumeinheit durch das Ölrückflussrohr (57) fließt, gleich einer vorbestimmten Flussrate ist, und, falls die Temperatur des Kältemittels, das durch den Abschnitt des Einspritzrohrs (54) zwischen dem Übergang (P6) des Einspritzrohrs (54) und dem Ölrückflussrohr (57) und dem Zwischenexpansionsventil (36a, 36b, 36c) fließt, nicht über dem Gefriertemperaturschwellenwert (Tfth) liegt, der Steuerabschnitt (13) intermittierend das Ölrückflussexpansionsventil (42) derart in den offenen Zustand bringt, dass die Flussrate des Kühlmaschinenöls, das innerhalb der vorbestimmten Zeitraumeinheit durch das Ölrückflussrohr (57) fließt, zunimmt.
EP16786103.8A 2015-04-28 2016-03-30 Kühlvorrichtung Active EP3290825B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2015092150A JP5971377B1 (ja) 2015-04-28 2015-04-28 冷凍装置
PCT/JP2016/001846 WO2016174822A1 (ja) 2015-04-28 2016-03-30 冷凍装置

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EP3290825A1 EP3290825A1 (de) 2018-03-07
EP3290825A4 EP3290825A4 (de) 2018-12-19
EP3290825B1 true EP3290825B1 (de) 2021-05-19

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WO (1) WO2016174822A1 (de)

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JP6142896B2 (ja) * 2015-04-28 2017-06-07 ダイキン工業株式会社 冷凍装置
JP6319388B2 (ja) * 2016-09-12 2018-05-09 ダイキン工業株式会社 冷凍装置
JP6540666B2 (ja) * 2016-11-24 2019-07-10 ダイキン工業株式会社 冷凍装置
JP6390688B2 (ja) * 2016-11-24 2018-09-19 ダイキン工業株式会社 冷凍装置
CN109373634B (zh) * 2018-10-29 2020-07-31 宁波奥克斯电气股份有限公司 一种回油控制方法、装置及空调器
CN110173934B (zh) * 2019-05-29 2021-02-19 南京天加环境科技有限公司 一种燃气热泵多联机过冷结构的控制方法
IT202200005252A1 (it) * 2022-03-17 2023-09-17 General Gas S R L Metodo di controllo di un impianto di refrigerazione con sottoraffreddamento meccanico e relativo impianto di refrigerazione

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JP2007127302A (ja) * 2005-11-01 2007-05-24 Daikin Ind Ltd 冷凍装置
JP4211847B2 (ja) * 2007-01-17 2009-01-21 ダイキン工業株式会社 冷凍装置
JP5062039B2 (ja) * 2008-05-27 2012-10-31 ダイキン工業株式会社 冷凍装置
WO2011064928A1 (ja) * 2009-11-25 2011-06-03 ダイキン工業株式会社 コンテナ用冷凍装置
JP2012137207A (ja) * 2010-12-24 2012-07-19 Mitsubishi Electric Corp 冷凍サイクル装置
WO2013160966A1 (ja) * 2012-04-27 2013-10-31 三菱電機株式会社 空気調和装置
JP2014016079A (ja) * 2012-07-06 2014-01-30 Daikin Ind Ltd ヒートポンプ
WO2015029220A1 (ja) * 2013-08-30 2015-03-05 三菱電機株式会社 空気調和装置

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EP3290825A1 (de) 2018-03-07
ES2879920T3 (es) 2021-11-23
JP5971377B1 (ja) 2016-08-17
WO2016174822A1 (ja) 2016-11-03
JP2016205792A (ja) 2016-12-08
EP3290825A4 (de) 2018-12-19

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