WO2019021464A1 - Dispositif de conditionnement d'air - Google Patents

Dispositif de conditionnement d'air Download PDF

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Publication number
WO2019021464A1
WO2019021464A1 PCT/JP2017/027465 JP2017027465W WO2019021464A1 WO 2019021464 A1 WO2019021464 A1 WO 2019021464A1 JP 2017027465 W JP2017027465 W JP 2017027465W WO 2019021464 A1 WO2019021464 A1 WO 2019021464A1
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WO
WIPO (PCT)
Prior art keywords
refrigerant
expansion valve
electronic expansion
load
temperature
Prior art date
Application number
PCT/JP2017/027465
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English (en)
Japanese (ja)
Inventor
周平 水谷
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2017/027465 priority Critical patent/WO2019021464A1/fr
Priority to JP2019532326A priority patent/JP6758506B2/ja
Publication of WO2019021464A1 publication Critical patent/WO2019021464A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/20—Electric components for separate outdoor units
    • F24F1/24—Cooling of electric components
    • 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

Definitions

  • the present invention relates to an air conditioner provided with a refrigerant cooler of a control device.
  • the present invention has been made to solve the problems as described above, and an air conditioner provided with a refrigerant cooler capable of suppressing condensation due to cooling of a control device using a refrigerant in each operation mode. Intended to provide.
  • the compressor, the heat source side heat exchanger, the intermediate pressure adjusting electronic expansion valve, the load side electronic expansion valve, and the load side heat exchanger constitute a refrigerant circuit connected by refrigerant piping, and compressed Between the electronic expansion valve for intermediate pressure adjustment and the load-side electronic expansion valve, which is provided on the discharge side of the compressor and that switches the circulation direction of the refrigerant, the controller that controls each device that constitutes the refrigerant circuit And a refrigerant cooler for cooling the control device using a refrigerant, and in the cooling operation mode, the opening degree of the intermediate pressure adjusting electronic expansion valve is maximized.
  • dew condensation due to cooling of the control device using the refrigerant can be suppressed in each operation mode.
  • FIG. 1 is a refrigerant circuit diagram of an air conditioner according to Embodiment 1 of the present invention.
  • the air conditioning apparatus 100 is installed in, for example, a building or an apartment and can perform a cooling operation, a heating operation, and a defrosting operation by using a refrigeration cycle (a heat pump cycle) that circulates a refrigerant.
  • the air conditioning apparatus 100 includes a heat source side unit 80 and a load side unit 90, and forms a refrigeration cycle by connecting the heat source side unit 80 and the load side unit 90 with a refrigerant pipe 70.
  • fluorocarbon refrigerants for example, R32 refrigerant of HFC refrigerant, R125, R134a, R410A, R407c, R404A of these mixed refrigerants, etc.
  • HFO refrigerant for example, HFO-1234yf, HFO-1234ze (E), HFO-1234ze (Z)
  • CO2 refrigerant for example, propane, isobutane refrigerant
  • ammonia refrigerant mixed refrigerant of R32 and HFO-1234yf such as mixed refrigerant of the above refrigerants, etc. used in vapor compression type heat pump Refrigerant is used.
  • the air conditioner 100 includes a compressor 1, a four-way valve 2, a heat source side heat exchanger 3, an intermediate pressure adjusting electronic expansion valve 4, a refrigerant cooler 5, a load side electronic expansion valve 6, a load side heat exchanger 7 and an accumulator.
  • a refrigerant circuit 8 is connected by a refrigerant pipe 70, and the refrigerant circulates inside.
  • the heat source side unit 80 has a function of supplying cold or heat to the load side unit 90.
  • the heat source side unit 80 is mounted with a compressor 1, a four-way valve 2, a heat source side heat exchanger 3, an intermediate pressure adjusting electronic expansion valve 4, a refrigerant cooler 5 and an accumulator 8. These devices are connected in series to form a part of the main refrigerant circuit.
  • the compressor 1 is a fluid machine that compresses low-pressure refrigerant that has been taken in and discharges it as high-pressure refrigerant.
  • the compressor 1 is configured as, for example, a rotary compressor or a scroll compressor.
  • the compressor 1 may be configured as, for example, a compressor having a constant rotational frequency, or may be configured as a compressor capable of controlling a rotational frequency on which an inverter is mounted.
  • the four-way valve 2 is provided on the discharge side of the compressor 1 and is a flow path switching device for switching the circulation direction of the refrigerant in the cooling operation mode and the circulation direction of the refrigerant in the heating operation mode.
  • the flow of the refrigerant in the cooling operation mode and the heating operation mode will be described later.
  • the heat source side heat exchanger 3 is an air cooling type heat exchanger capable of performing heat exchange between the refrigerant flowing inside and the air.
  • the heat source side heat exchanger 3 functions as a condenser in the cooling operation mode and functions as an evaporator in the heating operation mode.
  • the load-side heat exchanger 3 is configured, for example, as a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a plurality of fins, or a plate fin type heat exchanger.
  • the heat source side unit 80 takes in the air which exchanges heat with the heat source side heat exchanger 3 into the heat source side unit 80
  • the heat source side blower 18 is provided for this purpose.
  • the rotation number of the heat source side fan 18 is controlled by the control device 10 described later, and controls the condensing capacity or the evaporation capacity of the heat source side heat exchanger 3.
  • the heat source side blower 18 is configured as, for example, a centrifugal fan such as a sirocco fan or a turbo fan, a cross flow fan, a diagonal flow fan, or a propeller fan.
  • the intermediate pressure adjusting electronic expansion valve 4 has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant.
  • the intermediate pressure adjusting electronic expansion valve 4 is configured, for example, as a pressure reducing device such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously.
  • the refrigerant cooler 5 includes a cooling pipe 51 and a cooling plate 52 which are a part of refrigerant piping between the intermediate pressure adjusting electronic expansion valve 4 and a load-side electronic expansion valve 6 described later.
  • the refrigerant cooler 5 absorbs heat of the control device 10 described later using a refrigerant to cool the control device 10.
  • the cooling plate 52 is fixed in contact with the surface of the control device 10
  • the cooling pipe 51 is fixed to the surface of the cooling plate 52 opposite to the surface in contact with the control device 10.
  • a refrigerant is flowed into the inside of the cooling pipe 51, and the heat generation of the control device 10 is absorbed via the cooling plate 52 to cool the control device 10.
  • the cooling pipe 51 and the cooling plate 52 are preferably made of the same material, and for example, aluminum is used.
  • the cooling pipe 51 has a temperature lower than the outside air temperature depending on the operating condition, and there is a possibility that dew condensation water may occur on the surface.
  • the cooling pipe 51 and the cooling plate 52 are made of different materials, the electrolytic corrosion will easily occur, so that the electrolytic corrosion can be prevented by using the same material.
  • the cooling pipe 51 and the cooling plate 52 may be closely fixed via silicon, or may be fixed by welding by brazing.
  • the accumulator 8 is provided on the suction side of the compressor 1 and has a function of separating a liquid refrigerant and a gas refrigerant and a function of storing an excess refrigerant.
  • the heat source side unit 80 also has a high pressure sensor 11 that detects the pressure (high pressure) of the refrigerant discharged from the compressor 1.
  • the heat source side unit 80 also has a low pressure sensor 12 that detects the pressure (low pressure) of the refrigerant drawn into the compressor 1.
  • the heat source side unit 100 further includes a cooling pipe temperature sensor 13 that detects the pipe temperature of the refrigerant pipe upstream of the refrigerant cooler 5 in the heating operation mode.
  • the heat source side unit 100 further includes an outside air temperature sensor 14 for detecting the outside air temperature. Each of these sensors sends a signal related to the detected pressure and a signal related to the detected temperature to the control device 10 that controls the operation of the air conditioner 100.
  • the load side unit 90 supplies the cold heat or the heat from the heat source side unit 80 to the cooling load or the heating load.
  • the load-side electronic expansion valve 6 and the load-side heat exchanger 7 are connected in series and mounted on the load-side unit 90, and constitute a refrigerant circuit together with the heat-source-side unit 80.
  • the load-side electronic expansion valve 6 has a function as a pressure reducing valve or an expansion valve, and decompresses and expands the refrigerant.
  • the load-side electronic expansion valve 6 is configured, for example, as a pressure reducing device such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously.
  • the load-side heat exchanger 7 is an air-cooled heat exchanger capable of performing heat exchange between the refrigerant flowing inside and the air.
  • the load side heat exchanger 7 functions as an evaporator in the cooling operation mode, and functions as a condenser in the heating operation mode.
  • the load-side heat exchanger 3 is configured, for example, as a cross fin type fin-and-tube heat exchanger composed of a heat transfer tube and a plurality of fins, or a plate fin type heat exchanger.
  • the load-side heat exchanger 7 is an air-cooled heat exchanger as in the first embodiment, the load-side unit 90 takes in air, which exchanges heat with the load-side heat exchanger 7, into the heat source-side unit 90.
  • the load side blower 19 is provided.
  • the rotation speed of the load-side fan 19 is controlled by the control device 10 described later, and controls the condensing capacity or the evaporation capacity of the load-side heat exchanger 7.
  • the load-side blower 19 is configured as, for example, a centrifugal fan such as a sirocco fan or a turbo fan, a cross flow fan, a diagonal flow fan, or a propeller fan.
  • the load side unit 90 also has a load side piping temperature sensor 15 that detects the temperature of the refrigerant pipe between the load side electronic expansion valve 6 and the load side heat exchanger 7.
  • the load-side pipe temperature sensor 15 sends a signal related to the detected temperature to the control device 10 that controls the operation of the air conditioner 100.
  • the control device 10 operates the air conditioning device 100 using a control program loaded in advance based on information and operation information from other various sensors mounted on the air conditioning device 100 and setting information of the user. It is to control.
  • the control device 10 controls, for example, drive frequency control of the compressor 1, switching control of the four-way valve 2, opening degree control of each electronic expansion valve, rotation speed control of each blower, and the like. Further, the control device 10 calculates the temperature of the refrigerant flowing into the refrigerant cooler 5 in the heating operation mode based on the pipe temperature information from the cooling pipe temperature sensor 13.
  • the control device 10 is configured by, for example, hardware such as a circuit device that realizes such a function, or software executed on an arithmetic device such as a microcomputer or a CPU.
  • control unit 10 may be provided on the load side unit 90.
  • control device 10 may be provided outside the heat source side unit 80 and the load side unit 90.
  • control device 10 may be divided into a plurality of units according to the function, and provided in each of the heat source side unit 80 and the load side unit 90. In this case, each control device may be connected wirelessly or in a wired manner to enable communication.
  • FIG. 2 is a refrigerant circuit diagram showing a refrigeration cycle in the cooling operation mode of the air conditioning apparatus according to the embodiment of the present invention.
  • FIG. 3 is a refrigerant circuit diagram showing a refrigeration cycle in the heating operation mode of the air conditioning apparatus according to the embodiment of the present invention.
  • the circulation direction of the refrigerant in the cooling operation mode and in the heating operation mode can be switched by the four-way valve 2.
  • the operation in the cooling operation mode will be described with reference to FIG.
  • a high temperature and high pressure gas refrigerant is discharged from the compressor 1 and flows into the heat source side heat exchanger 3 via the four-way valve 2.
  • the refrigerant flowing into the heat source side heat exchanger 3 exchanges heat with air and is condensed to be a low temperature and high pressure refrigerant.
  • the condensed refrigerant passes through the intermediate pressure adjustment electronic expansion valve 4 and then flows into the refrigerant cooler 5 to cool the control device 10. Thereafter, it flows out from the heat source side unit 80, flows into the load side unit 90, is decompressed by the load side electronic expansion valve 6, and becomes a gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant exchanges heat with air in the load side heat exchanger 7 and is evaporated.
  • the evaporated refrigerant flows out of the load side unit 90, flows into the heat source side unit 80, is sucked into the compressor 1 through the four-way valve 2, and is compressed again.
  • the load-side heat exchanger 7 functions as an evaporator to cool the room.
  • the opening degree of the intermediate pressure adjusting electronic expansion valve 4 is controlled to the maximum in order to minimize the pressure loss.
  • the refrigerant condensed in the heat source side heat exchanger 3 is not decompressed, and can be made to flow into the refrigerant cooler 5 while maintaining the temperature higher than the outside air temperature. It can be suppressed.
  • the load-side electronic expansion valve 6 can reduce the pressure to the target evaporation temperature. Note that the maximum described here also includes the vicinity of the maximum.
  • the operation in the heating operation mode will be described with reference to FIG.
  • a high temperature and high pressure gas refrigerant is discharged from the compressor 1, flows out from the heat source side unit 80 through the four-way valve 2, flows into the load side unit 90, It flows into the side heat exchanger 7.
  • the refrigerant flowing into the load-side heat exchanger 7 exchanges heat with air and is condensed to be a low-temperature high-pressure refrigerant.
  • the condensed refrigerant is decompressed by the load-side electronic expansion valve 6 to be a gas-liquid two-phase refrigerant, and flows out from the load-side unit 90 and flows into the heat-source-side unit 80.
  • the refrigerant flowing into the heat source side unit 80 flows into the refrigerant cooler 5 and cools the control device 10. Thereafter, the pressure is reduced by the intermediate pressure adjusting electronic expansion valve 4 and flows into the heat source side heat exchanger 3.
  • the refrigerant flowing into the heat source side heat exchanger 3 exchanges heat with air and is evaporated.
  • the evaporated refrigerant is drawn into the compressor 1 through the four-way valve 2 and compressed again.
  • the load-side heat exchanger 7 functions as a condenser to heat the room.
  • the refrigerant flowing into the refrigerant cooler 5 is after passing through the load side electronic expansion valve 6, if the opening degree of the load side electronic expansion valve 6 is small, it becomes a low pressure low temperature refrigerant Condensation may occur in the device 10.
  • the temperature of the refrigerant flowing into the refrigerant cooler 5 needs to be equal to or higher than the dew point temperature. Therefore, when the temperature of the refrigerant detected by the cooling pipe temperature sensor 13 is equal to or lower than the dew point temperature, the opening degree of the intermediate pressure adjusting electronic expansion valve 4 is reduced, whereby the gas-liquid flowing into the refrigerant cooler 5 The pressure of the phase refrigerant can be raised to raise the temperature.
  • the refrigerant cooling can be performed by further increasing the opening degree of the load side electronic expansion valve 6.
  • the pressure of the refrigerant flowing into the vessel 5 can be further raised, and the temperature of the refrigerant can be further raised.
  • the refrigerant condensed by the heat source side heat exchanger 3 by controlling the opening degree of the intermediate pressure adjusting electronic expansion valve 4 to the maximum in the cooling operation mode. Since the refrigerant can be made to flow into the refrigerant cooler 5 while maintaining the temperature higher than the outside air temperature, dew condensation in the control device 10 can be suppressed. Further, by reducing the opening degree of the intermediate pressure adjusting electronic expansion valve 4 in the heating operation mode, the temperature of the refrigerant flowing into the refrigerant cooler 5 can be raised, and condensation can be suppressed.
  • the temperature of the refrigerant can be further raised, so the temperature of the refrigerant flowing into the refrigerant cooler 5 can be made higher than the dew point temperature more reliably. it can.
  • FIG. 4 is a refrigerant circuit diagram of an air conditioner according to Embodiment 2 of the present invention.
  • the same reference numerals as in FIG. 1 denote the same or corresponding components, and the description thereof will be omitted.
  • the air conditioner 101 according to the second embodiment of the present invention branches from the refrigerant pipe on the discharge side of the compressor 1 and is connected to the refrigerant pipe between the refrigerant cooler 5 and the load-side electronic expansion valve 6. And, it differs from the air conditioning apparatus 100 of the first embodiment in that the bypass valve 20 provided in the bypass circuit 21 is provided.
  • the opening degree of the intermediate pressure adjusting electronic expansion valve 4 can not be reduced. There is a case. If the opening degree of the intermediate pressure adjustment electronic expansion valve 4 is reduced, the suction density of the compressor 1 is reduced, the circulation flow rate is reduced, and the heating air conditioning capacity is reduced, or it takes time to start the heating operation. is there. Such a phenomenon is likely to occur when the state of pressure or temperature of the refrigerant is unstable, and is particularly likely to occur during transient operation such as heating operation start and defrost operation end.
  • the refrigerant piping between the refrigerant cooler 5 and the load-side electronic expansion valve 6 is branched off from the refrigerant piping on the discharge side of the compressor 1.
  • a bypass circuit 21 to be connected is provided.
  • a bypass valve 20 is provided on the bypass circuit 21.
  • the bypass valve 20 is configured, for example, as a pressure reducing device such as a linear electronic expansion valve whose opening degree can be adjusted in multiple stages or continuously. Moreover, you may comprise as a capillary tube.
  • the bypass circuit 21 can merge the high temperature and high pressure gas refrigerant discharged from the compressor 1 with the refrigerant flowing into the refrigerant cooler 5. Therefore, the temperature of the refrigerant flowing into the refrigerant cooler 5 can be raised.
  • FIG. 5 is a flowchart showing control of the bypass valve of the air conditioning apparatus according to Embodiment 2 of the present invention.
  • the control device 10 determines whether the temperature of the refrigerant detected by the cooling pipe temperature sensor 13 is higher than the dew point temperature (ST1). If the temperature of the refrigerant is higher than the dew point temperature, nothing is performed because the possibility of condensation within the control device 10 is low.
  • the temperature of the refrigerant is equal to or lower than the dew point temperature, it is determined whether the low pressure detected by the low pressure sensor 12 is higher than a predetermined value (ST2).
  • the suction density of the compressor 1 is large to some extent, so the opening degree of the intermediate pressure adjusting electronic expansion valve 4 can be reduced (ST6).
  • the suction density of the compressor 1 is reduced and the circulation flow rate is reduced. Therefore, the opening degree of the intermediate pressure adjusting electronic expansion valve 4 can not be reduced. Therefore, the bypass valve 20 is opened to flow the refrigerant to the bypass circuit 21 (ST3). By so doing, the temperature of the refrigerant flowing into the refrigerant cooler 5 can be raised.
  • the control device 10 determines whether the temperature of the refrigerant detected by the cooling pipe temperature sensor 13 is higher than the dew point temperature, and the degree of subcooling of the indoor unit outlet is larger than a predetermined value determined in advance ST4). If one of the conditions is not met, the pie bus valve 20 is kept open. If either condition is satisfied, the bypass valve 20 is closed (ST5).
  • the reason why the degree of supercooling at the outlet of the load unit 90 is set as a condition for closing the bypass valve 20 is to confirm that the dryness of the refrigerant flowing into the refrigerant cooler 5 is reduced. is there.
  • the degree of subcooling at the outlet of the load unit 90 is calculated by subtracting the temperature at the outlet of the condenser measured by the temperature sensor 15 on the load side from the condensation temperature determined by the high pressure sensor 11.
  • the bypass circuit branched from the refrigerant pipe on the discharge side of the compressor 1 and connected to the refrigerant pipe between the refrigerant cooler 5 and the load-side electronic expansion valve 6
  • the refrigerant valve can be opened by opening the bypass valve 20. A decrease in the temperature of the refrigerant flowing to 5 can be prevented, and condensation in the control device 10 can be suppressed.
  • the temperature of the refrigerant detected by the cooling pipe temperature sensor 13 becomes higher than the dew point temperature, and the degree of supercooling of the outlet of the load side unit 90 becomes larger than a predetermined value determined in advance. By closing, it is possible to prevent the decrease of the refrigerant temperature more reliably.
  • the temperature of the refrigerant flowing into the refrigerant cooler 5 is controlled to be equal to or higher than the dew point temperature.
  • the temperature of the refrigerant flowing into the refrigerant cooler 5 may be controlled to be equal to or more than a value obtained by subtracting the ⁇ degree from the outside air temperature detected by the outside air temperature sensor 14.
  • the temperature in the control device 10, which is a heat generating member, is cooled by the refrigerant flowing into the refrigerant cooler 5.
  • the temperature needs to be equal to or higher than the dew point temperature.
  • the degree to which the inside of the control device 10 is cooled is calculated in advance from the heat capacity of the cooling plate 52 and the like, and the temperature ⁇ which causes no problem even if the temperature of the refrigerant flowing into the refrigerant cooler 5 is lower than the outside air temperature is calculated.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

L'invention concerne un dispositif de conditionnement d'air 100 comprenant : un dispositif 2 de commutation de canal d'écoulement, qui constitue un circuit de fluide frigorigène comprenant un compresseur 1, un échangeur de chaleur 3 côté source de chaleur, une soupape de détente électronique 4 de réglage de pression intermédiaire, une soupape de détente électronique 6 côté charge et un échangeur de chaleur 7 côté charge raccordés au moyen d'une conduite de fluide frigorigène et qui est disposée du côté décharge du compresseur 1, ledit dispositif de commutation de canal d'écoulement commutant le sens de circulation de fluide frigorigène ; un dispositif de commande 10 qui commande les appareils constituant le circuit de fluide frigorigène ; et un refroidisseur 5 de fluide frigorigène, disposé entre la soupape de détente électronique 4 de réglage de pression intermédiaire et la soupape de détente électronique 6 côté charge, et qui refroidit le dispositif de commande 10 à l'aide d'un fluide frigorigène. Dans le mode de fonctionnement de refroidissement, le degré d'ouverture de la soupape de détente électronique 4 de réglage de pression intermédiaire est fixé à la valeur maximale.
PCT/JP2017/027465 2017-07-28 2017-07-28 Dispositif de conditionnement d'air WO2019021464A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/JP2017/027465 WO2019021464A1 (fr) 2017-07-28 2017-07-28 Dispositif de conditionnement d'air
JP2019532326A JP6758506B2 (ja) 2017-07-28 2017-07-28 空気調和装置

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Application Number Priority Date Filing Date Title
PCT/JP2017/027465 WO2019021464A1 (fr) 2017-07-28 2017-07-28 Dispositif de conditionnement d'air

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110044027A (zh) * 2019-04-15 2019-07-23 广东美的制冷设备有限公司 空调系统的控制方法
CN113383201A (zh) * 2019-02-06 2021-09-10 三菱电机株式会社 制冷循环装置
CN115264654A (zh) * 2022-07-28 2022-11-01 海信家电集团股份有限公司 一种空调器及其过负荷控制方法

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005133976A (ja) * 2003-10-28 2005-05-26 Hitachi Ltd 空気調和装置
WO2008059803A1 (fr) * 2006-11-13 2008-05-22 Daikin Industries, Ltd. Système d'échange de chaleur
WO2013161323A1 (fr) * 2012-04-27 2013-10-31 ダイキン工業株式会社 Dispositif de réfrigération

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2005133976A (ja) * 2003-10-28 2005-05-26 Hitachi Ltd 空気調和装置
WO2008059803A1 (fr) * 2006-11-13 2008-05-22 Daikin Industries, Ltd. Système d'échange de chaleur
WO2013161323A1 (fr) * 2012-04-27 2013-10-31 ダイキン工業株式会社 Dispositif de réfrigération

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113383201A (zh) * 2019-02-06 2021-09-10 三菱电机株式会社 制冷循环装置
CN113383201B (zh) * 2019-02-06 2022-10-21 三菱电机株式会社 制冷循环装置
CN110044027A (zh) * 2019-04-15 2019-07-23 广东美的制冷设备有限公司 空调系统的控制方法
CN115264654A (zh) * 2022-07-28 2022-11-01 海信家电集团股份有限公司 一种空调器及其过负荷控制方法

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