WO2018167866A1 - Dispositif de climatisation - Google Patents

Dispositif de climatisation Download PDF

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Publication number
WO2018167866A1
WO2018167866A1 PCT/JP2017/010348 JP2017010348W WO2018167866A1 WO 2018167866 A1 WO2018167866 A1 WO 2018167866A1 JP 2017010348 W JP2017010348 W JP 2017010348W WO 2018167866 A1 WO2018167866 A1 WO 2018167866A1
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WO
WIPO (PCT)
Prior art keywords
pressure
compressor
refrigerant
expansion valve
bypass
Prior art date
Application number
PCT/JP2017/010348
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English (en)
Japanese (ja)
Inventor
靖人 熊城
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/JP2017/010348 priority Critical patent/WO2018167866A1/fr
Priority to JP2019505580A priority patent/JPWO2018167866A1/ja
Publication of WO2018167866A1 publication Critical patent/WO2018167866A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle

Definitions

  • This invention relates to an air conditioner. In particular, it relates to ensuring the reliability of the compressor.
  • the load in the target space related to the air condition may be installed in an environment where the capacity of the apparatus is excessive.
  • the liquid bypass valve is opened, and the liquid refrigerant is compressed from the accumulator through the liquid bypass throttling device.
  • an object of the present invention is to obtain an air conditioner that can drive a compressor in a pressure usage range and ensure reliability.
  • An air conditioner according to the present invention is a refrigeration cycle apparatus having a main refrigerant circuit configured to connect a compressor, a flow path switching device, a condenser, an expansion valve, and an evaporator with refrigerant piping to circulate the refrigerant.
  • the bypass pipe connecting the refrigerant pipe between the condenser and the expansion valve, the refrigerant pipe on the suction side of the compressor, the bypass expansion valve for adjusting the flow rate of the refrigerant flowing through the bypass pipe, and the condenser
  • a condensing temperature detecting device for detecting the condensing temperature, an evaporating temperature detecting device for detecting the evaporating temperature in the evaporator, a discharge pressure and an intake pressure in the compressor are obtained from the detected condensing temperature and evaporating temperature, and the discharge pressure and the intake pressure are obtained. It is determined whether or not at least one of the pressures is outside the pressure usage range of the compressor. If it is determined that the pressure is outside the pressure usage range, the bypass expansion valve is set to the first predetermined value. Time is increased, in which a control device for passing the refrigerant flowing out from the condenser.
  • the control device compresses at least one of the discharge pressure and the suction pressure of the compressor obtained from the condensation temperature and the evaporation temperature according to the detection of the condensation temperature detection device and the evaporation temperature detection device. If it is determined that the pressure is out of the range of the compressor, the bypass throttle device is opened, the suction pressure of the compressor is increased during heating operation, and the refrigerant passing through the evaporator is reduced during cooling operation. Thus, the evaporating temperature is lowered, and the discharge pressure and the suction pressure of the compressor are returned to the pressure use range, so that the reliability of the compressor and thus the air conditioner can be ensured.
  • FIG. 1 is a diagram showing a configuration of an air-conditioning apparatus according to Embodiment 1 of the present invention.
  • an air conditioner will be described as an example of the refrigeration cycle apparatus.
  • the air conditioner in FIG. 1 has an outdoor unit 10 and an indoor unit 20.
  • the outdoor unit 10 and the indoor unit 20 are connected by a refrigerant pipe to constitute a refrigerant circuit in which the refrigerant circulates.
  • the indoor unit 20 has an indoor heat exchanger 21.
  • the indoor heat exchanger 21 performs heat exchange between air to be air-conditioned and a refrigerant.
  • it functions as a condenser and condenses and liquefies the refrigerant.
  • it functions as an evaporator during cooling operation, evaporating and evaporating the refrigerant.
  • the outdoor unit 10 includes a compressor 11, a four-way valve 12, an outdoor heat exchanger 13, a first expansion valve 14, and an accumulator 15.
  • the compressor 11, the four-way valve 12, the outdoor heat exchanger 13, the first expansion valve 14, and the accumulator 15 are installed on a main refrigerant circuit together with the indoor heat exchanger 21 of the indoor unit 20.
  • Compressor 11 compresses and discharges the sucked refrigerant.
  • the compressor 11 changes the capacity of the compressor 11 (the amount of refrigerant sent out per unit time) by arbitrarily changing the operating frequency by, for example, an inverter circuit. It may be possible to make it.
  • the four-way valve 12 serves as a flow path switching device that switches the flow of the refrigerant between the cooling operation and the heating operation.
  • the outdoor heat exchanger 13 in Embodiment 1 performs heat exchange between the refrigerant and air (outdoor air). For example, it functions as an evaporator during heating operation, evaporating and evaporating the refrigerant. Moreover, it functions as a condenser during the cooling operation, and condenses and liquefies the refrigerant.
  • the first expansion valve 14 is a throttling device (flow control device) that decompresses and expands the refrigerant.
  • the first expansion valve 14 is configured by, for example, an electronic expansion valve that can change the opening degree based on an instruction from the control device 30 and perform pressure, flow rate adjustment, and the like.
  • the accumulator 15 is provided on the suction side of the compressor 11. The accumulator 15 stores, for example, surplus refrigerant generated in the transition period when the difference in the amount of refrigerant used between the heating operation and the cooling operation, or when the operation changes.
  • the air conditioner of Embodiment 1 has a bypass pipe 16 serving as a bypass flow path for the main refrigerant circuit.
  • the bypass pipe 16 connects the refrigerant pipe between the indoor heat exchanger 21 and the first expansion valve 14 and the inlet side pipe of the accumulator 15. Further, the refrigerant pipe between the outdoor heat exchanger 13 and the first expansion valve 14 and the inlet side pipe of the accumulator 15 are connected.
  • a bypass expansion valve 17, a first check valve 18 and a second check valve 19 are installed on the bypass flow path.
  • the bypass expansion valve 17 adjusts the flow rate and pressure of the refrigerant passing through the bypass pipe 16.
  • the bypass expansion valve 17 is configured by, for example, an electronic expansion valve that can change the opening degree based on an instruction from the control device 30 and perform pressure adjustment or the like.
  • the first check valve 18 allows the refrigerant flowing into the bypass pipe 16 from the outdoor heat exchanger 13 side to pass therethrough, and blocks the refrigerant that is about to flow from the indoor heat exchanger 21 side to the outdoor heat exchanger 13 side.
  • the second check valve 19 allows the refrigerant flowing into the bypass pipe 16 from the indoor heat exchanger 21 side to pass therethrough, and blocks the refrigerant that flows from the outdoor heat exchanger 13 side to the indoor heat exchanger 21 side.
  • the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32 are provided.
  • the outdoor heat exchanger side temperature sensor 31 is installed in the outdoor heat exchanger 13.
  • the outdoor heat exchanger side temperature sensor 31 is a condensing temperature detecting device that detects the condensing temperature when the outdoor heat exchanger 13 functions as a condenser, and detects the evaporating temperature when the outdoor heat exchanger 13 functions as an evaporator. Evaporation temperature detection device.
  • the indoor heat exchanger side temperature sensor 32 is installed in the indoor heat exchanger 21.
  • the indoor heat exchanger side temperature sensor 32 becomes a condensation temperature detection device that detects the condensation temperature when the indoor heat exchanger 21 functions as a condenser, and detects the evaporation temperature when the indoor heat exchanger 21 functions as an evaporator. Evaporation temperature detection device.
  • the control device 30 controls equipment in the refrigerant circuit such as the compressor 11, the first expansion valve 14, the four-way valve 12, and the bypass expansion valve 17 to air-condition the target space.
  • the control device 30 controls the opening degree of the bypass expansion valve 17 based on temperatures detected by the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32. To do.
  • the control device 30 includes a data processing unit 30A, a determination processing unit 30B, a device control processing unit 30C, and a storage unit 30D.
  • the data processing unit 30A processes data included in the signal, the storage unit 30D, and the like.
  • the determination processing unit 30B makes a determination based on the processing of the data processing unit 30A. Here, in particular, the determination relating to the pressure usage range of the compressor 11 described later is performed.
  • the device control processing unit 30C controls devices in the refrigerant circuit.
  • the storage unit 30D stores data necessary for the processing of the control device 30 temporarily or for a long time.
  • control device 30 is composed of, for example, a microcomputer having a control arithmetic processing device such as a CPU (Central Processing Unit). Further, it has a storage device (not shown), and has data in which the processing procedure performed by the data processing unit 30A, the determination processing unit 30B, and the device control processing unit 30C is a program. And a control arithmetic processing apparatus performs a process based on the data of a program, and implement
  • the present invention is not limited to this, and each device may be configured by a dedicated device (hardware).
  • the control apparatus 30 is installed in the outdoor unit 10, it does not limit about an installation location.
  • FIG. 2 is a diagram for explaining the pressure use range of the compressor 11 according to Embodiment 1 of the present invention.
  • the vertical axis of the graph represents the discharge pressure Pd (MpaG) of the compressor 11.
  • the horizontal axis of the graph represents the suction pressure Ps (MpaG) of the compressor 11.
  • the inside of the polygon in the graph indicates an allowable range in which the compressor 11 can be normally driven as a specification. If the driving in the range outside the polygon is continued, the compressor 11 may be broken.
  • the heating load when the heating load is excessive, the room temperature remains low without increasing the room temperature even when the air conditioner is operated.
  • the upper side and the right side from the sides (1) to (4) of the polygon that is the pressure usage range of the compressor 11 are the upper limits of the discharge pressure Pd and the suction pressure Ps.
  • the lower side and the left side of the sides of (5) and (6) are the lower limits of the discharge pressure Pd and the suction pressure Ps.
  • the condensation pressure Pc in the heat exchanger used as a condenser can be approximated with the discharge pressure Pd.
  • the evaporation pressure Pe in the heat exchanger serving as an evaporator can be approximated to the suction pressure Ps.
  • FIG. 3 is a diagram showing the processing contents of the control device 30 corresponding to the heating load according to Embodiment 1 of the present invention.
  • the processing of the control device 30 when the heating load is excessive will be described.
  • the description is based on a summary of the processing of each unit of the control device 30 described above (hereinafter the same).
  • the control device 30 Based on the evaporation temperature and condensation temperature data included in the signals sent from the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32, the control device 30 converts the condensation pressure Pc and the evaporation pressure by saturation temperature conversion. Pe is obtained (step S1). It is determined whether at least one of the condensation pressure Pc and the evaporation pressure Pe exceeds the upper limit of the pressure usage range of the compressor 11 (step S2). If it is determined that the upper limit of the pressure use range of the compressor 11 is not exceeded, it is determined whether or not a predetermined time has elapsed (step S3), and processing is performed at predetermined time intervals. Heating operation continues.
  • the opening of the bypass expansion valve 17 is opened by the first predetermined opening.
  • the refrigerant is allowed to pass through the bypass pipe 16 (step S4).
  • the pressure of the refrigerant that has passed through the bypass pipe 16 is higher than the pressure of the refrigerant in the outdoor heat exchanger 13.
  • the refrigerant flowing in the outdoor heat exchanger 13 serving as an evaporator is reduced to lower the evaporation pressure Pe, and the discharge pressure Pd and the suction pressure Ps of the compressor 11 are used as pressure. Try to bring it back in range. Thereafter, the process proceeds to an upper limit opening process performed by opening the bypass expansion valve 17 (step S5).
  • FIG. 4 is a diagram showing the contents of the upper limit opening process of the control device 30 according to the first embodiment of the present invention.
  • the control device 30 converts the evaporation temperature and condensation temperature data included in the signals sent from the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32 to each other. Based on this, the condensation pressure Pc and the evaporation pressure Pe are obtained (step S12). Then, it is determined whether at least one of the condensation pressure Pc and the evaporation pressure Pe exceeds the upper limit of the pressure use range of the compressor 11 (step S13). If it is determined that at least one of the condensation pressure Pc and the evaporation pressure Pe exceeds the upper limit of the pressure usage range of the compressor 11, the bypass expansion valve 17 is further opened to a first predetermined opening (step S14).
  • discharge superheat refrigerant discharge temperature from compressor 11 ⁇ condensation temperature.
  • the threshold temperature of the discharge superheat degree SHd is 10 ° C.
  • the method for obtaining the refrigerant discharge temperature is not particularly limited.
  • a discharge temperature detection device may be disposed on the discharge side of the compressor 11 to detect the refrigerant discharge temperature. Further, the estimation calculation may be performed from the condensation pressure or the like.
  • Step S16 If it is determined that the discharge superheat degree SHd is lower than the threshold temperature (not higher than the threshold temperature), the opening degree of the bypass expansion valve 17 is closed by the second predetermined opening degree to restrict passage of the refrigerant through the bypass pipe 16 ( Step S16). By restricting the passage of the refrigerant through the bypass pipe 16, the amount of liquid refrigerant flowing to the suction side of the compressor 11 is suppressed, thereby preventing liquid back.
  • At least one of the condensation pressure Pc and the evaporation pressure Pe is a predetermined pressure difference from the upper limit of the pressure usage range of the compressor 11. It is determined whether or not it has fallen by ⁇ P or more (away from the lower side) (step S17). For example, if the compressor 11 is driven efficiently with respect to a heating load, for example, the compressor 11 is set so that the discharge pressure and the suction pressure are close to the upper limit of the pressure use range even within the pressure use range. It is better to drive.
  • the opening of the bypass expansion valve 17 is closed to the third predetermined opening (step S18).
  • the control device 30 repeats the above processing, and performs drive control such that the discharge pressure Pd and the suction pressure Ps of the compressor 11 are located near the upper limit of the pressure use range even when the heating load is excessive.
  • FIG. 5 is a diagram showing the processing contents of the control device 30 corresponding to the cooling load according to the first embodiment of the present invention.
  • the processing of the control device 30 when the cooling load is excessive will be described.
  • the cooling load increases, the heat exchange with the refrigerant is frequently performed, so that the evaporation pressure Pe and the condensation pressure Pc tend to increase.
  • the control device 30 obtains the condensation pressure Pc and the evaporation pressure Pe based on the condensation temperature and evaporation temperature data included in the signals sent from the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32 ( Step S21). It is determined whether at least one of the condensation pressure Pc and the evaporation pressure Pe is below the lower limit of the pressure usage range of the compressor 11 (step S22). If it is determined that the lower limit of the pressure usage range of the compressor 11 is not exceeded, it is determined whether or not a predetermined time has elapsed (step S23), and processing is performed at predetermined time intervals. The cooling operation is continued as it is.
  • the opening of the bypass expansion valve 17 is opened by the first predetermined opening. And let the refrigerant pass through the bypass pipe 16 (step S24).
  • the first predetermined opening is set as in the case where it is determined that the upper limit of the pressure use range is exceeded, but it may be opened at a different opening.
  • the bypass expansion valve 17 is opened and the refrigerant is allowed to pass through the bypass pipe 16, thereby reducing the refrigerant passing through the indoor heat exchanger 21 serving as an evaporator, and the refrigerant in the indoor heat exchanger 21. Reduce the pressure.
  • the suction pressure Ps is increased, and the discharge pressure Pd and the suction pressure Ps of the compressor 11 are returned to within the pressure use range. Thereafter, the process proceeds to a lower limit opening process performed by opening the bypass expansion valve 17 and the process ends (step S25).
  • FIG. 6 is a diagram showing the contents of the lower limit opening process of the control device 30 according to the first embodiment of the present invention.
  • the control device 30 converts the condensation temperature and evaporation temperature data included in the signals sent from the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32 to each other. Based on this, the condensation pressure Pc and the evaporation pressure Pe are obtained (step S32). Then, it is determined whether at least one of the condensation pressure Pc and the evaporation pressure Pe exceeds the upper limit of the pressure use range of the compressor 11 (step S33).
  • the bypass expansion valve 17 is further opened to the first predetermined opening (step S34).
  • the opening may be made at an opening different from the first predetermined opening.
  • discharge superheat refrigerant discharge temperature from compressor 11 ⁇ condensation temperature.
  • the threshold temperature of the discharge superheat degree SHd is 10 ° C.
  • the method for obtaining the refrigerant discharge temperature is not particularly limited.
  • a discharge temperature detection device may be disposed on the discharge side of the compressor 11 to detect the refrigerant discharge temperature. Further, the estimation calculation may be performed from the condensation pressure or the like.
  • Step S36 the opening degree of the bypass expansion valve 17 is closed by the second predetermined opening degree to restrict passage of the refrigerant through the bypass pipe 16.
  • the opening degree of the bypass expansion valve 17 is closed by the second predetermined opening degree to restrict passage of the refrigerant through the bypass pipe 16 (Ste S36).
  • the control device 30 is obtained from the condensation temperature and the evaporation temperature related to the detection by the outdoor heat exchanger side temperature sensor 31 and the indoor heat exchanger side temperature sensor 32.
  • the bypass expansion valve 17 is opened, and the suction of the compressor 11 is performed during the heating operation. Since the pressure is increased and the cooling temperature is lowered by reducing the refrigerant passing through the evaporator during the cooling operation, the discharge pressure and the suction pressure of the compressor 11 are returned to the pressure use range. The reliability of the compressor 11 and the air conditioner can be ensured.
  • the valve of the bypass expansion valve 17 is opened.
  • the control device 30 determines whether or not it is more than ⁇ P away from the upper limit of the pressure use range, and if it is judged that it is more than ⁇ P away from the upper limit of the pressure use range, the opening degree of the bypass expansion valve 17 is set to the third predetermined opening degree. Since it is made to close, the compressor 11 can be driven efficiently so that the discharge pressure and the suction pressure are close to the upper limit of the pressure use range.
  • the opening degree of the valve in the bypass expansion valve 17 is set to a second predetermined value. Since the opening is closed, liquid back due to opening of the bypass expansion valve 17 can be prevented. For this reason, the reliability of the compressor 11 is securable.
  • FIG. FIG. 7 is a diagram showing a configuration of an air-conditioning apparatus according to Embodiment 2 of the present invention.
  • FIG. 7 for devices having the same reference numerals as those in FIG. 1, operations similar to those described in Embodiment 1 are performed.
  • the accumulator 15, the first check valve 18 and the second check valve 19 are not installed.
  • the second expansion valve 41, the receiver tank 42, and the inter-refrigerant heat exchanger 43 are installed.
  • the second expansion valve 41 decompresses and expands the refrigerant in the main refrigerant circuit.
  • the second expansion valve 41 is also composed of an electronic expansion valve or the like.
  • the receiver tank 42 is a tank serving as a liquid receiver that is disposed at a position where a liquid refrigerant (liquid refrigerant) flowing out from a heat exchanger functioning as a condenser flows and stores the liquid refrigerant.
  • the inter-refrigerant heat exchanger 43 performs heat exchange between the refrigerants. For example, during cooling operation, the liquid refrigerant flowing through the main refrigerant circuit is supercooled.
  • control device 30 performs control to fully open the first expansion valve 14 and adjust the opening degree of the second expansion valve 41 in the cooling operation.
  • the second expansion valve 41 is fully opened and the opening degree of the first expansion valve 14 is adjusted.
  • the refrigerant flowing into the bypass pipe 16 becomes a liquid refrigerant, and the same control as that of the air conditioner of Embodiment 1 can be performed for an excessive load.
  • Embodiment 3 FIG.
  • the control apparatus 30 performed the process in the procedure divided into the upper limit side and the lower limit side about the pressure usage range of the compressor 11, you may make it perform a process collectively.

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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)

Abstract

Ce dispositif de climatisation est un dispositif à cycle de réfrigération ayant un circuit de fluide frigorigène principal qui fait circuler un fluide frigorigène et comprend un compresseur, un condenseur, un détendeur et un évaporateur relié à une tuyauterie de fluide frigorigène. Le dispositif de climatisation comprend: une tuyauterie de dérivation qui relie une tuyauterie de fluide frigorigène entre le condenseur et le détendeur et une tuyauterie de fluide frigorigène sur le côté d'admission du compresseur; un détendeur de dérivation qui ajuste le débit de fluide frigorigène s'écoulant dans la tuyauterie de dérivation; un dispositif de détection de température de condensation qui détecte la température de condensation dans le condenseur; un dispositif de détection de température d'évaporation qui détecte la température d'évaporation dans l'évaporateur; et un dispositif de commande qui acquiert la pression de refoulement et la pression d'admission du compresseur à partir de la température de condensation détectée et de la température d'évaporation détectée, qui détermine si au moins l'une de la pression de refoulement et de la pression d'admission est en dehors de la plage de pression du compresseur, qui ouvre le détendeur de dérivation vers une première ouverture prescrite lorsque la pression est déterminée comme étant à l'extérieur de la plage de pression, et qui amène le fluide frigorigène à traverser par réduction de la pression du fluide frigorigène s'écoulant à partir le condenseur.
PCT/JP2017/010348 2017-03-15 2017-03-15 Dispositif de climatisation WO2018167866A1 (fr)

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Application Number Priority Date Filing Date Title
PCT/JP2017/010348 WO2018167866A1 (fr) 2017-03-15 2017-03-15 Dispositif de climatisation
JP2019505580A JPWO2018167866A1 (ja) 2017-03-15 2017-03-15 空気調和装置

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Application Number Priority Date Filing Date Title
PCT/JP2017/010348 WO2018167866A1 (fr) 2017-03-15 2017-03-15 Dispositif de climatisation

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WO2018167866A1 true WO2018167866A1 (fr) 2018-09-20

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102087249B1 (ko) * 2020-01-29 2020-03-10 (주)수성이엔지 효율성이 개선된 공냉식 냉방기시스템

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06265232A (ja) * 1993-03-11 1994-09-20 Mitsubishi Electric Corp 空気調和装置
JPH10176869A (ja) * 1996-12-13 1998-06-30 Mitsubishi Electric Corp 冷凍サイクル装置
JP2008039332A (ja) * 2006-08-09 2008-02-21 Mitsubishi Heavy Ind Ltd マルチ型ヒートポンプ式空気調和機
JP2010054118A (ja) * 2008-08-28 2010-03-11 Daikin Ind Ltd 空気調和装置
JP5759017B2 (ja) * 2011-12-22 2015-08-05 三菱電機株式会社 空気調和装置
WO2016139736A1 (fr) * 2015-03-02 2016-09-09 三菱電機株式会社 Dispositif de commande et procédé de réfrigération de dispositif de cycle

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06265232A (ja) * 1993-03-11 1994-09-20 Mitsubishi Electric Corp 空気調和装置
JPH10176869A (ja) * 1996-12-13 1998-06-30 Mitsubishi Electric Corp 冷凍サイクル装置
JP2008039332A (ja) * 2006-08-09 2008-02-21 Mitsubishi Heavy Ind Ltd マルチ型ヒートポンプ式空気調和機
JP2010054118A (ja) * 2008-08-28 2010-03-11 Daikin Ind Ltd 空気調和装置
JP5759017B2 (ja) * 2011-12-22 2015-08-05 三菱電機株式会社 空気調和装置
WO2016139736A1 (fr) * 2015-03-02 2016-09-09 三菱電機株式会社 Dispositif de commande et procédé de réfrigération de dispositif de cycle

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102087249B1 (ko) * 2020-01-29 2020-03-10 (주)수성이엔지 효율성이 개선된 공냉식 냉방기시스템

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