WO2014118945A1 - 冷凍サイクル装置 - Google Patents

冷凍サイクル装置 Download PDF

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Publication number
WO2014118945A1
WO2014118945A1 PCT/JP2013/052222 JP2013052222W WO2014118945A1 WO 2014118945 A1 WO2014118945 A1 WO 2014118945A1 JP 2013052222 W JP2013052222 W JP 2013052222W WO 2014118945 A1 WO2014118945 A1 WO 2014118945A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
refrigeration cycle
pressure
cycle apparatus
upper limit
Prior art date
Application number
PCT/JP2013/052222
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English (en)
French (fr)
Japanese (ja)
Inventor
坪江　宏明
横関　敦彦
福治 塚田
中山　進
野中　正之
Original Assignee
日立アプライアンス株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 日立アプライアンス株式会社 filed Critical 日立アプライアンス株式会社
Priority to JP2014559437A priority Critical patent/JP5964996B2/ja
Priority to CN201380068958.8A priority patent/CN104903661A/zh
Priority to CN201810232146.7A priority patent/CN108469126A/zh
Priority to PCT/JP2013/052222 priority patent/WO2014118945A1/ja
Publication of WO2014118945A1 publication Critical patent/WO2014118945A1/ja

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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
    • 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
    • F25B49/022—Compressor 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
    • 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
    • F25B13/00—Compression machines, plants or systems, with 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
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/025—Compressor control by controlling speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • F25B2600/027—Compressor control by controlling pressure
    • F25B2600/0271—Compressor control by controlling pressure the discharge pressure

Definitions

  • the present invention relates to a refrigeration cycle apparatus such as an air conditioner or a refrigerator using a refrigeration cycle, and more particularly to a refrigeration cycle apparatus using R32 (difluoromethane) as a refrigerant used in the refrigeration cycle.
  • a refrigeration cycle apparatus such as an air conditioner or a refrigerator using a refrigeration cycle
  • R32 difluoromethane
  • the refrigerant R410A is generally employed as a refrigerant sealed in the refrigeration cycle.
  • Refrigerant R410A is a refrigerant with a high GWP (global warming potential), but it can reduce the amount of carbon dioxide generated by reducing the power consumption by improving the efficiency of the equipment, and suppresses refrigerant leakage by measures such as refrigerant leakage This contributes to the prevention of global warming.
  • the refrigerant R32 rises by about 15 ° C. if the discharge temperature of the compressor is the same operating condition (the same standard operating condition) with respect to the refrigerant R410A due to the physical properties of the refrigerant.
  • a high-pressure chamber type compressor that is, a compressor in which the motor is sealed in the compressor chamber and the atmosphere around the motor is cooled by the gas refrigerant discharged from the compression mechanism unit. It is necessary to change the organic material that is an insulating material of the motor to a material that can be used at a higher temperature than the material in the case where R410A is used as the refrigerant.
  • a permanent magnet is employed for the rotor of the motor, there is a problem that the permanent magnet is likely to be demagnetized because of a high temperature.
  • the existing refrigerant connection pipe (existing pipe) connected to the outdoor unit may be reused. Further, when a plurality of indoor units are connected, the existing pipe is branched by a branch pipe in the middle and connected to each indoor unit. This branch pipe may be reused.
  • the maximum pressure (design pressure) at the time of use is 3.0 MPa (absolute pressure)
  • the design pressure in the equipment using the refrigerant R407C is 3.4 MPa (absolute pressure).
  • fill the said design pressure are selected for the said existing refrigerant
  • the design pressure for the refrigerant R407C is 3.4 MPa (absolute pressure).
  • the design pressure in the air conditioner using the refrigerant R32 is 4.2 to 4.3 MPa (absolute pressure), and the existing refrigerant connection pipe in the air conditioner using the refrigerant R22 and R407C There was also a problem that the branch pipe could not be reused.
  • An object of the present invention is to obtain a refrigeration cycle apparatus that can reuse an existing refrigerant connection pipe while adopting R32 as a refrigerant.
  • the present invention provides an outdoor unit including a compressor and a heat source side heat exchanger, an indoor unit including a use side heat exchanger, and a liquid side connection that connects the outdoor unit and the indoor unit.
  • the refrigeration cycle apparatus including a pipe and a gas side connection pipe
  • a control device that uses R32 as a refrigerant to be used in the refrigeration cycle apparatus and that controls the refrigeration cycle apparatus is provided.
  • the upper limit value is configured to be set or set equal to the upper limit value of the control pressure in the refrigeration cycle apparatus using the refrigerant R22 or the refrigerant R407C.
  • strain diagram which shows Example 1 of the refrigeration cycle apparatus of this invention.
  • Example 1 of the refrigeration cycle apparatus of the present invention will be described with reference to FIGS.
  • an example of an air conditioner using a refrigerant R32 as a refrigeration cycle apparatus will be described.
  • the structure of the air conditioner as a refrigeration cycle apparatus of the present embodiment will be described with reference to FIG.
  • FIG. 1 is a refrigeration cycle system diagram showing Embodiment 1 of the refrigeration cycle apparatus of the present invention.
  • the air conditioner of the present embodiment includes an outdoor unit 40 and an indoor unit 20, and the outdoor unit 40 and the indoor unit 20 are connected by a liquid side connection pipe 7 and a gas side connection pipe 8. Yes.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor (sealed compressor) 1 provided in the outdoor unit 40 is discharged from the compressor 1 together with the refrigerating machine oil, and the gas refrigerant passes through the four-way valve 2. It flows into the heat source side heat exchanger 3, where it exchanges heat with a heat source side medium such as outside air (outdoor air) or water to condense and liquefy.
  • the condensed and liquefied refrigerant (liquid refrigerant) passes through the fully opened first expansion device 4, passes through the blocking valve 6, and is sent from the liquid side connection pipe 7 to the indoor unit 20.
  • the liquid refrigerant that has flowed into the indoor unit 20 is reduced to a low pressure in the second expansion device 21 to be in a low-pressure two-phase state, enters the use side heat exchanger 22 and exchanges heat with a use side medium such as indoor air and evaporates. Gasify. Thereafter, the gas refrigerant passes through the gas side connection pipe 8, enters the accumulator 10 through the blocking valve 9 and the four-way valve 2, and is sucked again into the compressor 1 from here to constitute a refrigeration cycle. Excess refrigerant is stored in the accumulator 10 and the operating pressure and temperature of the refrigeration cycle are maintained in a normal state.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor 1 is discharged from the compressor 1 together with the refrigeration oil, passes through the four-way valve 2, the blocking valve 9, and the gas side connection pipe 8, and then the indoor unit 20. It flows into the use side heat exchanger 22 where it heat-exchanges with the use side medium such as room air to heat the use side medium and condensates itself.
  • the condensed and liquefied refrigerant is depressurized by the first expansion device 4 via the liquid side connection pipe 7 and the blocking valve 6, and exchanges heat with a heat source side medium such as outdoor air or water in the heat source side heat exchanger 3. Evaporate and gasify.
  • the evaporated and gasified refrigerant returns to the compressor 1 through the four-way valve 2 and the accumulator 10 to constitute a refrigeration cycle.
  • R32 is used as a refrigerant
  • a control device (not shown) for controlling the refrigeration cycle apparatus is provided.
  • the design pressure (upper limit value of the control pressure) of the refrigeration cycle apparatus is set or set equal to the design pressure (upper limit value of the control pressure) in the refrigeration cycle apparatus employing the refrigerant R22 or the refrigerant R407C. It is configured to be possible. Thus, the maximum value of the discharge pressure is reduced.
  • the discharge temperature that is the temperature of the gas refrigerant discharged from the compressor 1 is expressed by the condensation temperature of the refrigerant at the discharge pressure that is the pressure of the gas refrigerant discharged from the compressor 1 and the degree of superheat of the discharged gas refrigerant. be able to.
  • the expansion devices 4 and 21 are controlled so that the superheat degree of the gas refrigerant discharged from the compressor 1 is constant, the lower the condensation temperature, that is, the lower the discharge pressure, The discharge temperature can be set low.
  • FIG. 2 is a diagram illustrating the relationship between the heat transfer area of the heat source side heat exchanger, the refrigerant circulation amount, and the discharge pressure
  • FIG. 3 illustrates the relationship between the air amount of the heat source side heat exchanger, the refrigerant circulation amount, and the discharge pressure
  • FIG. 4 is a diagram for explaining the relationship among the heat transfer area, the air volume, and the discharge pressure of the heat source side heat exchanger in the same cooling capacity.
  • A represents a standard, the conditions on the indoor unit side are the same, and the heat transfer area, the air volume, and the generation capacity of the heat source side heat exchanger are the same when the refrigerant R410A is used and when the refrigerant R32 is used.
  • the discharge pressure is the same when R410A is used and when R32 is used.
  • the vertical axis of each figure represents the discharge pressure when R32 is used with the discharge pressure at this point A as a reference. 2 and 3 is based on “refrigerant circulation amount ratio ⁇ 1.0” of the refrigerant R32.
  • the refrigerant circulation amount is constant on the curve having the same refrigerant circulation amount ratio.
  • FIG. 2 shows the relationship of the discharge pressure ratio of the compressor 1 to the heat transfer area ratio of the heat source side heat exchanger 3 when the refrigerant R32 is sealed in the refrigeration cycle apparatus.
  • FIG. 3 shows the relationship of the discharge pressure ratio of the compressor 1 with respect to the air volume ratio on the air side of the heat source side heat exchanger 3.
  • Curves a in FIG. 2 and FIG. 3 show the heat transfer area ratio or air flow ratio based on the refrigerant circulation rate (refrigerant circulation rate ratio is 1.0) necessary for generating a capacity of 14 kW, and the discharge rate. The relationship with the pressure ratio is shown. Further, when the refrigerant circulation rate ratio is 0.88 (curve b), and when the refrigerant circulation rate ratio is 0.77 (curve c), the heat transfer area ratio or air flow ratio, the discharge pressure ratio, The relationship is also shown.
  • the air condition at this time is an overload condition in which the discharge pressure rises most in the cooling operation (the dry bulb temperature of the inlet air of the indoor side use side heat exchanger 22 is 32 ° C., the wet bulb temperature is 23 ° C., the outdoor unit side The condition of the dry-bulb temperature of the inlet air of the heat source side heat exchanger 3 is 43 ° C.).
  • the design pressure of the outdoor unit 40 that employs the refrigerant R410A and the refrigerant R32 is 4.2 to 4.3 MPa (absolute pressure).
  • the refrigerant R32 is used.
  • the upper limit value of the control pressure in the refrigeration cycle apparatus is provided, and the upper limit value is set lower than or equal to the design pressure of the refrigerant R32.
  • the upper limit value of the control pressure is 3.8 MPa (absolute pressure)
  • the discharge pressure ratio 1.0 shown in FIGS. 2 and 3 is 3.8 MPa (absolute pressure). Results are shown.
  • the discharge pressure can be reduced, and the upper limit value of the control pressure can be set low.
  • the discharge temperature of the compressor 1 can be reduced accordingly.
  • the working pressure of the liquid side connection pipe 7 and the gas side connection pipe 8 used in the air conditioner using the refrigerant R22 or R407C, which has a lower design pressure than the refrigerant R410A or R32, is the outer diameter of the pipe. It is determined by the wall thickness and the material of the copper pipe that is the material of the pipe.
  • the combination of the outer diameter, thickness and material of the pipe having the lowest operating pressure is a general refrigerant pipe copper pipe (JIS). B 8607), ⁇ 19.05, wall thickness 1.0 mm, O material, the maximum operating pressure is 3.72 MPa (absolute pressure).
  • the transmission of the heat source side heat exchanger 3 is performed so that the operating pressure (upper limit value of the control pressure) of the outdoor unit 40 in the refrigeration cycle apparatus using the refrigerant R32 is 3.7 MPa (absolute pressure) or less.
  • the heat area is set, or the air volume (the amount of air blown by the cooling fan) in the heat source side heat exchanger 3 is set from FIG.
  • the control device controls the compressor 1 so that the upper limit value of the control pressure controlled by the control device mounted on the outdoor unit 40 using the refrigerant R32 is 3.7 MPa (absolute pressure) or less.
  • the operation frequency is controlled to adjust the refrigerant circulation amount, or the operation frequency of the cooling fan in the heat source side heat exchanger 3 is controlled to control the air volume.
  • the liquid-side connection pipe 7 and the gas-side connection pipe 8 used in the air conditioner (old machine) adopting the refrigerant R22 and R407C are replaced with those of the air conditioner (new machine) using the refrigerant R32. It can be reused at the time of introduction. In addition, the discharge temperature of the compressor 1 can be reduced.
  • the middle of the liquid side connection pipe 7 and the gas side connection pipe 8 is branched by a branch pipe.
  • the branch pipe is usually designed corresponding to the design pressure of the refrigerant to be used.
  • the design pressure of the branch pipe is a refrigerant with a high design pressure.
  • the design pressure (3.4 MPa) of the branch pipe is lower than 3.72 MPa (absolute pressure), which is the lower limit value of the maximum operating pressure of the liquid side connection pipe 7 and the gas side connection pipe 8, and the indoor unit 20 It is necessary to operate the air conditioner connected with a plurality of air pressures below the design pressure of the branch pipe.
  • a refrigeration cycle apparatus using a refrigerant R32 in a refrigeration cycle apparatus in which a plurality of indoor units 20 are connected to the liquid side connection pipe 7 and the gas side connection pipe 8 via a branch pipe.
  • the upper limit value of the control pressure of the refrigeration cycle apparatus that is, the operating pressure of the outdoor unit 40 is 3.4 MPa (absolute pressure) or less from FIG.
  • the air volume in the heat source side heat exchanger 3 is set from FIG.
  • the control device controls the compressor 1 so that the upper limit value of the control pressure controlled by the control device mounted on the outdoor unit 40 using the refrigerant R32 is 3.4 MPa (absolute pressure) or less.
  • the operation frequency is controlled to adjust the refrigerant circulation amount, or the operation frequency of the cooling fan in the heat source side heat exchanger 3 is controlled to control the air volume.
  • the liquid side connection pipe 7, the gas side connection pipe 8 and the branch pipe used in the air conditioner (old machine) that employs the refrigerant R22 or R407C are used for the air conditioning using the refrigerant R32. It can be reused when a machine (new machine) is introduced. In addition, the discharge temperature of the compressor 1 can be reduced.
  • the outdoor unit 40 in the refrigeration cycle apparatus using the refrigerant R32 can be connected by reusing the existing connection pipes 7 and 8 used in the air conditioner adopting the refrigerant R22 and R407C.
  • the upper limit value of the control pressure of the outdoor unit 40 is set to the new piping construction method or the existing piping method.
  • the upper limit value of the control pressure of the outdoor unit 40 is set to a design pressure of 3.7 MPa in an outdoor unit employing the refrigerant R22 or the refrigerant R407C, or 3.4 MPa when an existing branch pipe is also reused. .
  • control apparatus is provided in the control base
  • An upper limit value of the control pressure can be arbitrarily selected and set by a control pressure setting unit such as a dip switch or a jumper wire that can be used.
  • control pressure setting unit a control pressure setting unit
  • the control pressure setting unit such as the dip switch or the external control device
  • the new pipe construction method or The upper limit value of the control pressure of the outdoor unit 40 can be set according to the pressure resistance of the connection pipes 7 and 8 and the branch pipe used when the existing pipe utilization method is adopted.
  • the refrigeration cycle apparatus (air conditioner) of the present embodiment can be used for both the new piping construction method and the existing piping utilization method, and the connection pipes 7 and 8 and the branch pipe used.
  • the upper limit value of the control pressure of the outdoor unit 40 can be determined to a pressure corresponding to the design pressure.
  • the discharge temperature of the compressor 1 which becomes a problem when the refrigerant R32 is employed can also be reduced.
  • it can be made substantially the same as the discharge temperature of the compressor in the outdoor unit employing R410A currently used.
  • FIG. 4 is a diagram illustrating the relationship between the heat transfer area, the air volume, and the discharge pressure of the heat source side heat exchanger when controlled to the same cooling capacity. 4, the heat source side when the design pressure (upper limit value of the control pressure) of the outdoor unit 40 in the air conditioner (refrigeration cycle apparatus) using the refrigerant R32 is set to 3.4 MPa (absolute pressure). The relationship between the heat transfer area ratio of the heat exchanger 3 and the lower limit value of the air flow ratio will be described.
  • FIG. 4 shows the results when the control upper limit pressure is set to 3.8 MPa (absolute pressure) as in FIGS. 2 and 4.
  • Curve d in FIG. 4 indicates that the air volume ratio of the heat source side heat exchanger 3 is 1.0
  • curve e indicates that the air volume ratio is 1.3
  • curve f indicates that the air volume ratio is 1.6. The result of the case is shown.
  • the discharge pressure ratio 1.0 on the vertical axis in FIG. 4 corresponds to 3.8 MPa (absolute pressure), and the discharge pressure ratio 0.9 corresponds to 3.4 MPa (absolute pressure).
  • the combination of the heat transfer area ratio and the air flow ratio at a discharge pressure ratio of 0.9, at which the discharge pressure is 3.4 MPa, is 1.6 when the heat transfer area ratio is 1.55 and 2 when the heat transfer area ratio is 2.
  • the air flow ratio is 1.3.
  • the discharge pressure of the compressor 1 can satisfy the discharge pressure ratio of 0.9 or less. That is, the performance of the heat exchanger is proportional to the heat transfer area and further proportional to the power of the flow velocity of the air passing through the heat exchanger. From this and the result shown in FIG. It has been derived.
  • the heat transfer area ratio A 0 cannot be controlled during operation. Therefore, by controlling the air volume ratio Q 0 so as to satisfy the above formula (1), the discharge pressure is controlled to 3.4 MPa or less. can do. As a result, the discharge temperature of the compressor 1 can be reduced.
  • the design pressure of the outdoor unit 40 using the refrigerant R32 can be controlled to the design pressure of the existing branch pipe, for example, 3.4 MPa or less. It can also be used.
  • the design pressure (the upper limit value of the control pressure) is designed in the refrigeration cycle apparatus that employs the refrigerant R22 and the refrigerant R407C. Since the maximum value of the discharge pressure of the compressor, that is, the upper limit value of the control pressure is lowered, the existing refrigerant connection pipe or branch pipe may be reused while adopting R32 as the refrigerant. A refrigeration cycle apparatus that can be obtained can be obtained.
  • the motor used in the outdoor unit of the refrigeration cycle apparatus that employs the refrigerant R410A can be used. Without changing the insulating material, the material of the permanent magnet of the motor rotor, etc. to a high temperature (a magnet that is difficult to demagnetize at a high temperature), it can be used as a compressor part of a refrigeration cycle apparatus employing R32. Therefore, the effect that the refrigerating cycle device using refrigerant R32 which can aim at prevention of global warming with high efficiency can be manufactured cheaply is also acquired.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
PCT/JP2013/052222 2013-01-31 2013-01-31 冷凍サイクル装置 WO2014118945A1 (ja)

Priority Applications (4)

Application Number Priority Date Filing Date Title
JP2014559437A JP5964996B2 (ja) 2013-01-31 2013-01-31 冷凍サイクル装置
CN201380068958.8A CN104903661A (zh) 2013-01-31 2013-01-31 冷冻循环装置
CN201810232146.7A CN108469126A (zh) 2013-01-31 2013-01-31 室外机及采用该室外机的冷冻循环装置
PCT/JP2013/052222 WO2014118945A1 (ja) 2013-01-31 2013-01-31 冷凍サイクル装置

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/052222 WO2014118945A1 (ja) 2013-01-31 2013-01-31 冷凍サイクル装置

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WO2014118945A1 true WO2014118945A1 (ja) 2014-08-07

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JP (1) JP5964996B2 (zh)
CN (2) CN104903661A (zh)
WO (1) WO2014118945A1 (zh)

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WO2019124328A1 (ja) * 2017-12-18 2019-06-27 ダイキン工業株式会社 熱源ユニットおよび冷凍サイクル装置
CN111492186A (zh) * 2017-12-18 2020-08-04 大金工业株式会社 热源单元以及制冷循环装置
US11365335B2 (en) 2017-12-18 2022-06-21 Daikin Industries, Ltd. Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine
US11435118B2 (en) 2017-12-18 2022-09-06 Daikin Industries, Ltd. Heat source unit and refrigeration cycle apparatus
US11441819B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11441802B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Air conditioning apparatus
US11492527B2 (en) 2017-12-18 2022-11-08 Daikin Industries, Ltd. Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator
US11493244B2 (en) 2017-12-18 2022-11-08 Daikin Industries, Ltd. Air-conditioning unit
US11506425B2 (en) 2017-12-18 2022-11-22 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11549041B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator
US11549695B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Heat exchange unit
US11820933B2 (en) 2017-12-18 2023-11-21 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11906207B2 (en) 2017-12-18 2024-02-20 Daikin Industries, Ltd. Refrigeration apparatus

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Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019124328A1 (ja) * 2017-12-18 2019-06-27 ダイキン工業株式会社 熱源ユニットおよび冷凍サイクル装置
CN111492186A (zh) * 2017-12-18 2020-08-04 大金工业株式会社 热源单元以及制冷循环装置
JPWO2019124328A1 (ja) * 2017-12-18 2020-12-24 ダイキン工業株式会社 熱源ユニットおよび冷凍サイクル装置
US11365335B2 (en) 2017-12-18 2022-06-21 Daikin Industries, Ltd. Composition comprising refrigerant, use thereof, refrigerating machine having same, and method for operating said refrigerating machine
US11435118B2 (en) 2017-12-18 2022-09-06 Daikin Industries, Ltd. Heat source unit and refrigeration cycle apparatus
US11441819B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11441802B2 (en) 2017-12-18 2022-09-13 Daikin Industries, Ltd. Air conditioning apparatus
US11492527B2 (en) 2017-12-18 2022-11-08 Daikin Industries, Ltd. Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator
US11493244B2 (en) 2017-12-18 2022-11-08 Daikin Industries, Ltd. Air-conditioning unit
US11506425B2 (en) 2017-12-18 2022-11-22 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11535781B2 (en) 2017-12-18 2022-12-27 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11549041B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Composition containing refrigerant, use of said composition, refrigerator having said composition, and method for operating said refrigerator
US11549695B2 (en) 2017-12-18 2023-01-10 Daikin Industries, Ltd. Heat exchange unit
US11820933B2 (en) 2017-12-18 2023-11-21 Daikin Industries, Ltd. Refrigeration cycle apparatus
US11906207B2 (en) 2017-12-18 2024-02-20 Daikin Industries, Ltd. Refrigeration apparatus

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CN104903661A (zh) 2015-09-09
CN108469126A (zh) 2018-08-31
JPWO2014118945A1 (ja) 2017-01-26
JP5964996B2 (ja) 2016-08-03

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