WO2014155545A1 - 空気調和機 - Google Patents

空気調和機 Download PDF

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Publication number
WO2014155545A1
WO2014155545A1 PCT/JP2013/058900 JP2013058900W WO2014155545A1 WO 2014155545 A1 WO2014155545 A1 WO 2014155545A1 JP 2013058900 W JP2013058900 W JP 2013058900W WO 2014155545 A1 WO2014155545 A1 WO 2014155545A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
indoor
air conditioner
expansion valve
heat exchanger
Prior art date
Application number
PCT/JP2013/058900
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
横関　敦彦
坪江　宏明
松村　賢治
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 CN201380073435.2A priority Critical patent/CN105143786B/zh
Priority to JP2015507754A priority patent/JP6224079B2/ja
Priority to PCT/JP2013/058900 priority patent/WO2014155545A1/ja
Publication of WO2014155545A1 publication Critical patent/WO2014155545A1/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
    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
    • 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
    • F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
    • F25B2313/005—Outdoor unit expansion 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
    • F25B2500/00—Problems to be solved
    • F25B2500/12—Sound
    • 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
    • F25B2600/2513—Expansion 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • 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
    • F25B2700/2116—Temperatures of a condenser
    • F25B2700/21163—Temperatures of a condenser of the refrigerant at the outlet of the condenser
    • 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

Definitions

  • the present invention relates to a control method of an air conditioner, and is particularly suitable for suppressing the flow noise of a refrigerant during heating operation when R32 is employed as the refrigerant.
  • Patent No. 3956589 Patent No. 3435626 gazette
  • the air conditioner can increase the operation efficiency of the refrigeration cycle by controlling the heat exchanger outlet acting as the evaporator near the saturated gas.
  • R32 which is a refrigerant having a relatively low global warming potential, has a refrigerant temperature on the discharge side of the compressor 10 to 15 ° C. higher than that of R410A, which is a conventional refrigerant.
  • R410A which is a conventional refrigerant.
  • the refrigerant on the outlet side of the outdoor heat exchanger which acts as an evaporator during heating operation, is operated in a wet state to reduce the amount of refrigerant on the inlet side of the compressor, the amount of refrigerant stored in the evaporator is large. Become. Then, the degree of supercooling on the outlet side of the indoor heat exchanger acting as a condenser is insufficient, and a gas-liquid two-phase state occurs, so there is a problem that refrigerant flow noise is generated from the indoor unit due to the gas-liquid two-phase state .
  • the present invention is an air conditioner in which a single refrigerant of R32 or a mixed refrigerant containing 70% or more of R32 is enclosed in a refrigerant circulating in a refrigeration cycle, which is comfortable by suppressing the refrigerant flow noise in the indoor expansion valve during heating operation.
  • the purpose is to improve the quality.
  • the present application “connects an outdoor unit equipped with a compressor and an outdoor heat exchanger with an indoor unit equipped with an indoor heat exchanger and an indoor expansion valve using liquid piping and gas piping.
  • a refrigeration cycle in which a refrigeration cycle is configured and a refrigerant circulating R32 alone or a mixed refrigerant containing 70 mass% or more of R32 is enclosed in the refrigerant circulating in the refrigeration cycle, the throttling control by the outdoor expansion valve during heating operation And performing the throttling control by the indoor expansion valve.
  • the refrigerant flow noise in the indoor expansion valve is suppressed during heating operation. It is possible to improve comfort.
  • refrigerating cycle block diagram of an air conditioner It is an explanatory view of a condenser exit state change by compressor discharge temperature control at the time of heating operation. It is an explanatory view of a refrigerant flow style before an indoor expansion valve at the time of heating operation. It is operation
  • FIG. 1 is an example of the refrigerating-cycle block diagram of the multi-room air conditioner of a present Example.
  • the outdoor unit 100 includes an outdoor heat exchanger 101, an outdoor fan 102, an outdoor expansion valve 103, a compressor 104, an accumulator 105, a four-way valve 106, a discharge temperature sensor 107, and a discharge pressure sensor 108.
  • the indoor unit 200 includes an indoor heat exchanger 201, an indoor fan 202, an indoor expansion valve 203, and a refrigerant liquid temperature sensor 204.
  • the outdoor unit 100 and the indoor unit 200 are connected by a liquid pipe 121 and a gas pipe 122.
  • the high temperature gas refrigerant discharged from the compressor 104 is sent to the outdoor heat exchanger 101 through the four-way valve 106.
  • the high temperature gas refrigerant that has entered the outdoor heat exchanger 101 exchanges heat with the outdoor air sent by the outdoor fan 102, condenses, and becomes liquid refrigerant.
  • the refrigerant sent to the indoor unit 200 is decompressed by the indoor expansion valve 203 and enters the indoor heat exchanger 201.
  • the indoor heat exchanger 201 exchanges heat with indoor air sent by the indoor fan 202 and evaporates to become a gas refrigerant.
  • the gas refrigerant leaving the indoor unit 200 is sent to the outdoor unit 100 through the gas pipe 122.
  • the gas refrigerant that has entered the outdoor unit 100 enters the accumulator 105 through the four-way valve 106.
  • the accumulator 105 acts as a buffer tank for storing liquid refrigerant when the liquid refrigerant returns transiently, and prevents liquid compression due to the liquid refrigerant returning to the compressor 104. Under normal conditions, gas refrigerant enters the accumulator 104 from the accumulator 105 and is compressed.
  • the high temperature gas refrigerant discharged from the compressor 104 is sent to the gas pipe 122 through the four-way valve 106.
  • the high temperature gas refrigerant that has entered the gas piping 122 is sent to the indoor unit 200.
  • the high temperature gas refrigerant that has entered the indoor unit 200 exchanges heat with the indoor air sent by the indoor fan 202 in the indoor heat exchanger 201 and condenses to become liquid refrigerant, and passes through the indoor expansion valve 203 from the indoor unit 200 Get out. Heating is performed by heat exchange between the high temperature refrigerant and the indoor air in the indoor heat exchanger 200.
  • the liquid refrigerant that has left the indoor unit 200 then flows to the outdoor unit 100 via the liquid pipe 121.
  • the liquid refrigerant that has entered the outdoor unit 100 is decompressed when passing through the outdoor expansion valve 103 and enters the outdoor heat exchanger 101.
  • the outdoor heat exchanger 101 exchanges heat with the outdoor air sent by the outdoor fan 102 and evaporates to become a gas refrigerant.
  • Gas refrigerant enters accumulator 105 through four-way valve 106.
  • the accumulator 105 acts as a buffer tank when a large amount of liquid refrigerant passes through transiently, and prevents the compressor from being damaged by liquid compression. Under normal conditions, gas refrigerant enters the accumulator 104 from the accumulator 105 and is compressed.
  • the refrigerant liquid temperature sensor 204 of the indoor unit 200 detects the temperature of the refrigerant that has left the indoor heat exchanger 201. Further, the discharge pressure of the compressor 104 is detected by the discharge pressure sensor 108 of the outdoor unit 100. From the outlet side of the compressor 104 to the outlet side of the indoor heat exchanger 201, the pressure loss is relatively small because the refrigerant is in a high pressure state. Therefore, the degree of subcooling of the outlet side of the indoor heat exchanger 201 can be estimated by the following equation (1).
  • SC Tsat (Pd) -TL-C (1)
  • SC (K) is the degree of supercooling at the indoor heat exchanger outlet
  • Tsat () is the saturation temperature of pressure
  • Pd is the compressor discharge pressure (MPa)
  • TL is the indoor heat exchanger outlet temperature (° C)
  • C is It is a correction factor related to the refrigerant pressure loss.
  • FIG. 2 is an explanatory view of a state change on the outlet side of the condenser due to the discharge temperature suppression of the compressor 104 during the heating operation of the air conditioner using the R32 refrigerant.
  • the discharge temperature tends to be higher than when using the refrigerant R410A due to the influence of the refrigerant physical properties.
  • a condition in which the discharge temperature tends to be high includes a heating operation at a low temperature outside air where the pressure ratio of the compressor 104 tends to be large.
  • FIG. 2 is a Mollier diagram showing the operating condition at the low heating temperature, and the operating condition shown by the solid line is the degree of superheat SH (K) of a slight amount (2 to 3 K) as the refrigerant state on the suction side of the compressor 104. It shows the state of operation with the mark attached.
  • the discharge temperature Td1 of the compressor 104 may exceed the reliability upper limit allowable temperature (for example, 120 ° C.) of the compressor 104. Therefore, by increasing the opening degree of the outdoor expansion valve 103, the refrigerant on the suction side of the compressor 104 is made wet (suction dryness Xs), and the discharge temperature of the compressor 104 is set to Td2 (for example, 100 ° C.). It is desirable to lower it. As a result, deterioration of the compressor 104 such as deterioration of refrigeration oil and polymer material in the compressor 104 and demagnetization of a rare earth magnet can be prevented.
  • the suction dryness of the compressor 104 be Xs> 0.85.
  • the suction dryness is a value obtained by dividing the refrigerant gas mass flow by the refrigerant total mass flow, and suction dryness ⁇ refrigerant gas mass flow / refrigerant total mass flow, and refrigerator oil in the refrigerant is excluded. It shall be. Therefore, the compressor 104 is made to suck in the refrigerant whose suction dryness is Xs> 0.85.
  • the suction degree Xs of the compressor 104 when the suction degree Xs of the compressor 104 is decreased, the degree of the degree of abrasion also becomes low at the accumulator 105 located on the upstream side and the outlet side of the outdoor heat exchanger 101 acting as an evaporator. Therefore, the amount of refrigerant stored inside the accumulator 105 and the outdoor heat exchanger 101 is increased. Then, since the total amount of refrigerant in the cycle remains unchanged, the amount of refrigerant held in the indoor heat exchanger 201 acting as a condenser decreases, and as shown by Xco in FIG. 2, the outlet side of the indoor heat exchanger 201.
  • An indoor expansion valve 203 is installed at the outlet side of the indoor heat exchanger 201, and generates a refrigerant flow noise depending on the state of the refrigerant passing through, and generates noise to the occupant as abnormal noise from the indoor unit 200 of the air conditioner. It will cause discomfort.
  • FIG. 3 is a flow pattern determination diagram (Heiwitt-Roberts diagram) in the vertical upward flow (Source: Gas-Liquid Two-Phase Flow Handbook, page 10, Nippon Opportunity Society, 1989).
  • This FIG. 3 is used to estimate the refrigerant flow mode in the piping portion on the inlet side of the indoor expansion valve 203 during heating operation.
  • the horizontal axis of FIG. 3 shows the apparent momentum L L (j L ) 2 of the liquid refrigerant, where ⁇ L is the liquid refrigerant density (kg / m 3 ) and j L (m / s) It is the apparent flow rate of the liquid refrigerant that the liquid refrigerant flowed to satisfy the entire cross-sectional area.
  • ⁇ G is the gas refrigerant density (kg / m 3 ) and j G (m / s) It is an apparent flow rate of the gas refrigerant in which the gas refrigerant flowed so as to satisfy the entire cross-sectional area.
  • the divided regions in Fig. 3 are the types of flow modes such as slag flow, churn flow, and annular flow, and an approximate flow mode can be estimated by examining which region they are in. can do.
  • the state at the time of heating operation is put on a diagram, it can be shown by ⁇ for pipe diameter 10.7 mm, ⁇ for 7.93 mm, and ⁇ for 5.0 mm.
  • the refrigerant flow noise is particularly unpleasant in the region of slug flow or churn flow where gas clumps intermittently pass through the expansion valve, and it is desirable to always avoid this region, for example in the region of bubbly flow .
  • the area on the upper right side is considered to be the area of bubble flow.
  • the displacement control of the compressor 104 it is difficult to reduce the refrigerant flow noise by narrowing the inner diameter of the pipe in this manner because the refrigerant circulation amount is not constant.
  • the refrigerant R32 when the indoor unit is shared, the refrigerant R32 has a smaller refrigerant flow rate than the refrigerant R410A if the pipe inner diameter does not change. be able to.
  • the flow velocity of the refrigerant since the flow velocity of the refrigerant is reduced, the flow of the refrigerant may be more likely to occur in the region of the slag flow or the churn flow, and the refrigerant flow noise may occur due to the outlet side of the indoor heat exchanger 201 becoming the two phase region.
  • FIG. 4 is operation
  • suction suction degree Xs is controlled to, for example, about 0.9 for suppression of discharge temperature
  • the pressure reduction amount is small as ⁇ Pexpi, and it is provided in front of the outdoor heat exchanger 101 acting as an evaporator.
  • the pressure reduction amount ⁇ Pexpo at the outdoor expansion valve 103 which is located is largely controlled.
  • the degree of dryness of the liquid pipe 121 at this time is XLp.
  • the air conditioner of the present embodiment when the degree of subcooling is determined to be zero using the above-described arithmetic expression (1) of the degree of subcooling at the outlet of the indoor heat exchanger 201, indoor expansion is performed.
  • the valve 203 is controlled to squeeze.
  • the amount of pressure reduction by the indoor expansion valve 203 becomes large as ⁇ Pexpi ′, so the degree of dryness is increased up to the degree of dryness XLp ′ of the liquid pipe.
  • the amount of refrigerant held in the liquid pipe 121 can be reduced, and the amount of refrigerant held in the indoor heat exchanger 201, which has run short, can be increased.
  • the refrigerant state on the outlet side of the indoor heat exchanger 201 can be made into a liquid state by securing the subcooling degree SC of 2 to 3 K or more. Therefore, it is possible to prevent the generation of the unpleasant refrigerant flow noise generated in the indoor expansion valve 203.
  • the indoor unit is shared from the indoor unit using the refrigerant R410A in the air conditioner using the refrigerant R410A and the air conditioner using the refrigerant R32, that is, when the indoor unit is shared. Even if the inner diameter of the pipe does not change, the control method of this embodiment can reduce unpleasant refrigerant flow noise.

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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/JP2013/058900 2013-03-27 2013-03-27 空気調和機 WO2014155545A1 (ja)

Priority Applications (3)

Application Number Priority Date Filing Date Title
CN201380073435.2A CN105143786B (zh) 2013-03-27 2013-03-27 空调机
JP2015507754A JP6224079B2 (ja) 2013-03-27 2013-03-27 空気調和機
PCT/JP2013/058900 WO2014155545A1 (ja) 2013-03-27 2013-03-27 空気調和機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2013/058900 WO2014155545A1 (ja) 2013-03-27 2013-03-27 空気調和機

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CN (1) CN105143786B (zh)
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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019230436A1 (ja) * 2018-05-31 2019-12-05 株式会社デンソー 冷凍サイクル装置
EP3951285A4 (en) * 2019-03-26 2022-12-28 Fujitsu General Limited AIR CONDITIONING DEVICE
WO2023243022A1 (ja) * 2022-06-16 2023-12-21 三菱電機株式会社 ヒートポンプ装置

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018115831A (ja) * 2017-01-20 2018-07-26 ダイキン工業株式会社 室内ユニット
US20220290901A1 (en) * 2019-10-18 2022-09-15 Mitsubishi Electric Corporation Refrigeration Cycle Apparatus
CN112432341A (zh) * 2020-12-08 2021-03-02 合肥美的暖通设备有限公司 空调系统的控制方法、空调系统和可读存储介质

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JP2001194015A (ja) * 1999-10-18 2001-07-17 Daikin Ind Ltd 冷凍装置
JP2001227822A (ja) * 2000-02-17 2001-08-24 Mitsubishi Electric Corp 冷凍空調装置
JP2001295762A (ja) * 2000-04-13 2001-10-26 Daikin Ind Ltd 圧縮機および冷凍システム
JP2007225264A (ja) * 2006-02-27 2007-09-06 Mitsubishi Electric Corp 空気調和装置
JP2012032108A (ja) * 2010-08-02 2012-02-16 Daikin Industries Ltd 空気調和装置
JP2012159216A (ja) * 2011-01-31 2012-08-23 Mitsubishi Electric Corp 室外機、室内機及び空気調和装置

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JPH0571772A (ja) * 1991-09-11 1993-03-23 Matsushita Refrig Co Ltd 多室冷暖房装置
WO2001029489A1 (fr) * 1999-10-18 2001-04-26 Daikin Industries, Ltd. Dispositif de refrigeration
JP2012030603A (ja) * 2010-07-28 2012-02-16 Tgk Co Ltd 車両用冷暖房装置

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Publication number Priority date Publication date Assignee Title
JP2001194015A (ja) * 1999-10-18 2001-07-17 Daikin Ind Ltd 冷凍装置
JP2001227822A (ja) * 2000-02-17 2001-08-24 Mitsubishi Electric Corp 冷凍空調装置
JP2001295762A (ja) * 2000-04-13 2001-10-26 Daikin Ind Ltd 圧縮機および冷凍システム
JP2007225264A (ja) * 2006-02-27 2007-09-06 Mitsubishi Electric Corp 空気調和装置
JP2012032108A (ja) * 2010-08-02 2012-02-16 Daikin Industries Ltd 空気調和装置
JP2012159216A (ja) * 2011-01-31 2012-08-23 Mitsubishi Electric Corp 室外機、室内機及び空気調和装置

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019230436A1 (ja) * 2018-05-31 2019-12-05 株式会社デンソー 冷凍サイクル装置
JP2019211118A (ja) * 2018-05-31 2019-12-12 株式会社デンソー 冷凍サイクル装置
EP3951285A4 (en) * 2019-03-26 2022-12-28 Fujitsu General Limited AIR CONDITIONING DEVICE
WO2023243022A1 (ja) * 2022-06-16 2023-12-21 三菱電機株式会社 ヒートポンプ装置

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CN105143786B (zh) 2017-05-10
CN105143786A (zh) 2015-12-09
JP6224079B2 (ja) 2017-11-01
JPWO2014155545A1 (ja) 2017-02-16

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