WO2017081820A1 - Système de climatisation et procédé de commande d'un système de climatisation - Google Patents

Système de climatisation et procédé de commande d'un système de climatisation Download PDF

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Publication number
WO2017081820A1
WO2017081820A1 PCT/JP2015/082017 JP2015082017W WO2017081820A1 WO 2017081820 A1 WO2017081820 A1 WO 2017081820A1 JP 2015082017 W JP2015082017 W JP 2015082017W WO 2017081820 A1 WO2017081820 A1 WO 2017081820A1
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Prior art keywords
air
temperature
heat exchanger
dew point
evaporation temperature
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PCT/JP2015/082017
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English (en)
Japanese (ja)
Inventor
守 濱田
正樹 豊島
勇人 堀江
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2017549959A priority Critical patent/JP6479210B2/ja
Priority to PCT/JP2015/082017 priority patent/WO2017081820A1/fr
Publication of WO2017081820A1 publication Critical patent/WO2017081820A1/fr

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/89—Arrangement or mounting of control or safety devices

Definitions

  • the present invention relates to an air conditioning system including a ventilation device and a control method thereof.
  • An air conditioning system including an air conditioner having a refrigerant circuit (refrigeration cycle) and a ventilator is known.
  • the refrigerant circuit of the air conditioner includes a compressor, a four-way valve, an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.
  • the compressor, the four-way valve, the outdoor heat exchanger, the expansion valve, and the indoor heat exchanger are sequentially connected by piping.
  • the refrigerant circulates through the refrigerant circuit.
  • the high-temperature and high-pressure gas refrigerant compressed by the compressor is sent to the outdoor heat exchanger.
  • the refrigerant is liquefied by exchanging heat between the outdoor air and the refrigerant.
  • the liquefied refrigerant is decompressed by the decompression device, becomes a gas-liquid two-phase state, and flows into the indoor heat exchanger.
  • the refrigerant that has flowed into the indoor heat exchanger exchanges heat with room air and absorbs heat from the room air to gasify it.
  • indoor space is cooled.
  • the gasified refrigerant returns to the compressor.
  • the ventilation device replaces indoor air with fresh outdoor air. Specifically, the outdoor air is supplied to the room while the indoor air is discharged to the outside.
  • outdoor air becomes a cooling load (outside air load) when the enthalpy of air introduced from the outside (outdoor air) is high during cooling.
  • Other loads include a load generated indoors (indoor load) and a heat load that enters from the wall of the building.
  • the total heat load includes a latent heat load and a sensible heat load.
  • the latent heat load is processed by dehumidifying the indoor air while keeping the temperature of the indoor heat exchanger (refrigerant evaporation temperature) constant.
  • Patent Document 1 in order to process the total heat load of the outside air, the temperature and humidity of the air supplied from the ventilator to the room are controlled to target values. Maintains comfort.
  • This invention was made in order to solve the said subject, Comprising: It aims at providing the air conditioning system which can suppress the fall of energy saving property, suppressing the fall of comfort.
  • the air conditioning system includes a first heat exchanger, a refrigerant circuit, a ventilator, a detection unit that detects dew point temperature, and a control device that controls the evaporation temperature of the refrigerant circuit.
  • the first heat exchanger functions as an evaporator.
  • the refrigerant circuit is configured to circulate the refrigerant through the compressor, the condenser, the expansion valve, and the first heat exchanger.
  • the ventilator is configured to supply air, which is taken in from the outside and heat-exchanged with the refrigerant by the first heat exchanger, into the room.
  • the detection unit is provided at the outlet of the ventilator and is configured to detect the dew point temperature of the supply air.
  • the control device is configured to reduce the refrigerant pressure when the dew point temperature of the supply air detected by the detection unit exceeds a preset target dew point temperature of the indoor air.
  • the present invention it is possible to avoid a shortage of latent heat treatment and to reduce the amount of excess processing heat, and thus it is possible to suppress a decrease in energy saving while suppressing a decrease in comfort.
  • FIG. 1 is a schematic diagram illustrating a configuration of an air conditioning system according to Embodiment 1.
  • FIG. 2 is a schematic diagram of a refrigerant system of the air-conditioning system in Embodiment 1.
  • FIG. 1 is a schematic diagram illustrating a configuration of a ventilation device of an air conditioning system according to Embodiment 1.
  • FIG. 3 is a schematic diagram in which a configuration relating to control of the refrigerant system in the first embodiment is added. It is explanatory drawing of the determination method of target evaporation temperature Te according to humidity difference (DELTA) X. It is explanatory drawing of the determination method of target evaporation temperature Te according to dew point temperature difference (DELTA) Tdp.
  • DELTA humidity difference
  • DELTA dew point temperature difference
  • FIG. 3 is a flowchart showing the operation of the air conditioning system according to Embodiment 1. It is an air diagram which shows the change of the air state in the air supply ventilation path A of a ventilator.
  • FIG. 4 is a ph diagram of a second refrigerant system in the first embodiment.
  • 6 is a flowchart illustrating a first modification of the operation of the air-conditioning system according to Embodiment 1. It is an air diagram which shows the change of the air state in the air supply ventilation path A of the ventilation apparatus in the modification 1. It is a figure which shows the relationship between the temperature efficiency (eta) t of the cooler 26, and temperature difference (DELTA) T.
  • FIG. 4 is a diagram showing the relationship between the temperature efficiency ⁇ t of the cooler 26 and the air volume of the supply air passage A. It is a figure which shows the relationship between the temperature efficiency (eta) t of the cooler 26, and the superheat degree SH of the cooler 26 exit. It is a figure explaining operation
  • FIG. 4 is a diagram showing the relationship between the temperature efficiency ⁇ t of the cooler 26 and the air volume of the supply air passage A. It is a figure which shows the relationship between the temperature efficiency (eta) t of the cooler 26, and the superheat degree SH of the cooler 26 exit. It is a figure explaining operation
  • FIG. 1 is a schematic diagram showing a configuration of an air-conditioning system according to Embodiment 1 of the present invention.
  • the air conditioning system 100 corresponds to a plurality of indoor units 1A to 1C, an outdoor unit 2 provided corresponding to the indoor units 1A to 1C, a ventilator 3, and a ventilator 3.
  • the outdoor unit 4 provided and the centralized controller 102 is included.
  • there are a plurality of indoor units and a single ventilator but there may be a single indoor unit and a plurality of ventilators.
  • the plurality of indoor units 1A to 1C and the outdoor unit 2 are connected by a refrigerant pipe 104.
  • the indoor units 1A to 1C are arranged in the room 200, and the outdoor unit 2 is arranged outside the room.
  • the ventilation device 3 and the outdoor unit 4 are connected by a refrigerant pipe 105.
  • the ventilation device 3 is arranged in the room 200, and the outdoor unit 4 is arranged outside the room.
  • the centralized controller 102 is connected to each of the indoor units 1A to 1C, the outdoor unit 2, the ventilator 3, and the outdoor unit 4 through the transmission line 103.
  • the centralized controller 102 is provided with a setting input unit 44.
  • FIG. 2 is a schematic diagram of a refrigerant system of the air-conditioning system according to Embodiment 1.
  • the air conditioning system 100 includes two refrigerant systems: a refrigerant circuit 11 that is an indoor unit system and a refrigerant circuit 21 that is a ventilator system.
  • the refrigerant circuit 11 includes a compressor 12, a four-way valve 13, an outdoor heat exchanger 14, expansion valves 15A and 15B, indoor heat exchangers 16A and 16B, a blower 17 for the outdoor heat exchanger 14, And blowers 18A and 18B for the heat exchangers 16A and 16B.
  • the compressor 12, the four-way valve 13, the outdoor heat exchanger 14, the expansion valves 15A and 15B, and the indoor heat exchangers 16A and 16B are sequentially connected by pipes to constitute the refrigerant circuit 11 in which the refrigerant circulates.
  • the compressor 12, the four-way valve 13, the outdoor heat exchanger 14, and the blower 17 are installed in the outdoor unit 2.
  • the expansion valve 15A, the indoor heat exchanger 16A, and the blower 18A are installed in the indoor unit 1A.
  • the expansion valve 15B, the indoor heat exchanger 16B, and the blower 18B are installed in the indoor unit 1B.
  • FIG. 2 illustration of the indoor unit 1C is omitted in order to avoid complication, but the indoor unit 1C is arranged in parallel with the indoor unit 1A in the same manner as the indoor unit 1B. 14 and the four-way valve 13 are connected.
  • the configuration of the indoor unit 1C is the same as the configuration of the indoor unit 1B.
  • the refrigerant circuit 21 includes a compressor 22, a four-way valve 23, an outdoor heat exchanger 24, an expansion valve 25, a cooler 26, and a blower 27 for the outdoor heat exchanger 24.
  • the compressor 22, the four-way valve 23, the outdoor heat exchanger 24, the expansion valve 25, and the cooler 26 are sequentially connected by a pipe to constitute a refrigerant circuit 21 in which the refrigerant circulates.
  • the compressor 22, the four-way valve 23, the outdoor heat exchanger 24, and the blower 27 are installed in the outdoor unit 4.
  • the expansion valve 25 and the cooler 26 are installed in the ventilation device 3.
  • FIG. 2 shows a state where the four-way valves 13 and 23 are set to cooling, and the refrigerant flows in the direction indicated by the arrow.
  • an air conditioning system 100 including two refrigerant systems that is, a refrigerant circuit 11 that is an indoor unit system and a refrigerant circuit 21 that is a ventilator system, will be described.
  • a configuration without the refrigerant circuit 11 may be used. That is, the air conditioning system 100 may be configured to include the refrigerant circuit 21, the ventilation device 3, and the centralized controller 102 (control device).
  • FIG. 3 is a schematic diagram showing the configuration of the ventilation device of the air-conditioning system according to Embodiment 1 of the present invention.
  • the ventilation device 3 includes a cooler 26, a total heat exchanger 30, an air supply fan 28, and an exhaust fan 29 in the main body casing. Further, an air supply passage A and an exhaust passage B are formed independently of each other in the main body casing.
  • the air supply ventilation path A is a ventilation path that takes in the outdoor air OA by the supply air blower 28, passes it through the total heat exchanger 30 and the cooler 26, and supplies it to the room 200 as the supply air SA.
  • the exhaust ventilation path B is a ventilation path that takes in the indoor air RA by the exhaust blower 29 and passes it through the total heat exchanger 30 and exhausts it outside as the exhaust EA.
  • suction air IA the air that flows through the total heat exchanger 30 in the air supply ventilation path A and then flows into the cooler 26 is referred to as suction air IA.
  • the ventilation device 3 further includes a temperature / humidity detection unit 31 that detects the dry bulb temperature and absolute humidity of the outdoor air OA, a temperature / humidity detection unit 32 that detects the dry bulb temperature and absolute humidity of the indoor air RA, and a supply And a detector 33 for detecting the dew point temperature of the air SA.
  • the total heat exchanger 30 has a structure in which, for example, air passages orthogonal to each other are alternately stacked.
  • total heat exchange is performed between the indoor air RA and the outdoor air OA.
  • the outdoor air OA passes through the total heat exchanger 30, it becomes the intake air IA.
  • the indoor air RA becomes exhaust EA when passing through the total heat exchanger 30.
  • the cooler 26 is composed of the evaporator of the refrigerant circuit as described above, and dehumidifies the air passing through the cooler 26 by cooling it below the dew point temperature.
  • the ventilation device 3 has a role of processing the latent heat load of the room 200 as described above in addition to ventilation.
  • the ventilator 3 processes the latent heat load in the room 200 by the total heat exchanger 30 and the cooler 26. That is, the supply air SA dehumidified by the ventilator 3 is replaced with room air, so that the room air is dehumidified as a whole, and the latent heat load of the room 200 is processed.
  • the total heat exchanger 30 may be omitted, and the latent heat load in the room 200 may be processed only by the cooler 26.
  • FIG. 4 is a schematic diagram in which a configuration related to the control of the refrigerant system in the first embodiment is added.
  • the refrigerant circuit 11 and the refrigerant circuit 21 are provided with various detection devices and control devices as shown in FIG.
  • the air conditioning system 100 includes a cooler 26, a refrigerant circuit 21, a ventilation device 3, a detection unit 33 that detects a dew point temperature, and a control device 101 that controls the evaporation temperature of the refrigerant circuit 21.
  • the cooler 26 functions as an evaporator.
  • the refrigerant circuit 21 circulates the refrigerant through the compressor 22, the outdoor heat exchanger 24, the expansion valve 25, and the cooler 26.
  • the outdoor heat exchanger 24 functions as a condenser.
  • the ventilation device 3 exchanges heat between the outdoor air OA and the refrigerant by the cooler 26, and supplies the outdoor air OA to the room as supply air SA.
  • the detection part 33 is provided in the blower outlet of the ventilation apparatus 3, and detects the dew point temperature of supply air SA.
  • the control device 101 controls the evaporation temperature Te of the refrigerant circuit 21 so that the dew point temperature of the supply air SA detected by the detection unit 33 is lower than a preset target dew point temperature Tdp_in
  • the refrigerant circuit 11 includes a control unit 41 that controls the frequency of the compressor, a temperature detection unit 42 that detects the evaporation temperature, and temperature / humidity detection units 43A and 43B.
  • the temperature detection unit 42 detects the temperature of the refrigerant sucked into the compressor 12.
  • the temperature / humidity detection units 43A and 43B are provided in the plurality of indoor units 1A and 1B, respectively.
  • the temperature / humidity detection units 43A and 43B detect the temperature and humidity of the intake air (room air) of the indoor units 1A and 1B, respectively.
  • the control unit 41 changes the operation capacity of the compressor 22 by controlling the rotation speed (operation frequency) of the drive motor of the compressor 12.
  • the control unit 41 acquires information on the target value of the evaporation temperature of the refrigerant circuit 11 from the centralized controller 102.
  • the control part 41 controls the operating frequency of the compressor 12 so that the temperature which the temperature detection part 42 detected becomes the target value of evaporation temperature. Specifically, when the detected temperature is lower than the target value, the control unit 41 decreases the operating frequency of the compressor 12. Conversely, when the detected temperature is higher than the target value, the control unit 41 increases the operating frequency of the compressor 12.
  • control unit 41 transmits information on detection values of the temperature detection unit 42 and the temperature / humidity detection units 43A and 43B to the centralized controller 102.
  • the refrigerant circuit 21 includes a control unit 51 and a temperature detection unit 52.
  • the temperature detection unit 52 detects the temperature of the refrigerant sucked into the compressor 22.
  • the controller 51 changes the operating capacity of the compressor 22 by controlling the rotational speed (operating frequency) of the drive motor of the compressor 22.
  • control unit 51 acquires information on the target value of the evaporation temperature of the refrigerant circuit 21 from the centralized controller 102. And the control part 51 controls the operating frequency of the compressor 22 so that the temperature which the temperature detection part 52 detected becomes the target value of evaporation temperature. Specifically, when the detected temperature is lower than the target value, the control unit 41 decreases the operating frequency of the compressor 12. Conversely, when the detected temperature is higher than the target value, the control unit 41 increases the operating frequency of the compressor 12.
  • control unit 51 transmits information on the temperature / humidity detection unit 31, the temperature / humidity detection unit 32, the detection unit 33, and the temperature detection unit 52 to the centralized controller 102.
  • the centralized controller 102 sets the target temperature, which is the temperature of the target air in the room 200, and the target absolute humidity, which is the absolute humidity of the target air, by the setting input unit 44.
  • the centralized controller 102 determines a range of the evaporation temperature of the refrigerant circuit 21 (hereinafter referred to as an evaporation temperature range), and determines a target value of the evaporation temperature within this evaporation temperature range. Details of the determination of the target value will be described later with reference to FIGS.
  • a target temperature that is the temperature of the target air in the room 200 and a target dew point temperature that is the dew point temperature of the target air may be set.
  • the temperature / humidity detection unit 31, the temperature / humidity detection unit 32, the detection unit 33, the temperature detection unit 42, the temperature / humidity detection units 43A and 43B, and the temperature detection unit 52 are a temperature sensor, a humidity sensor, a dew point meter, or the like. It is comprised by the sensor apparatus of.
  • the control unit 51 calculates the dew point temperature of the supply air SA based on the detection result of the detection unit 33.
  • the dew point temperature may be calculated by the centralized controller 102.
  • the control unit 41, the control unit 51, and the centralized controller 102 can be realized by hardware such as a circuit device that realizes these functions, or can be realized as software executed on a computing device such as a microcomputer or CPU. You can also.
  • control unit 41 and the control unit 51 may be provided in the centralized controller 102. Further, the function of the centralized controller 102 may be provided in the control unit 41 or the control unit 51.
  • the centralized controller 102 and the control units 41 and 51 operate as the control device 101 in the present invention as a whole.
  • the cooler 26 corresponds to the “first heat exchanger” in the present invention.
  • the operation of the refrigerant circuit during the cooling operation and the heating operation will be described.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 12 passes through the four-way valve 13 and flows to the outdoor heat exchanger 14 to exchange heat with outdoor air to be condensed and liquefied.
  • the condensed and liquefied refrigerant is decompressed by the expansion valve 15 to become a low-pressure gas-liquid two-phase refrigerant, flows into the indoor heat exchangers 16A and 16B, and exchanges heat with air to be gasified.
  • the gasified refrigerant passes through the four-way valve 13 and is sucked into the compressor 12.
  • the indoor air sent by the blowers 18A and 18B for the indoor heat exchangers 16A and 16B is cooled and blown out into the room 200, thereby cooling the room 200.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 22 flows through the four-way valve 23 to the outdoor heat exchanger 24, and exchanges heat with the outdoor air OA that passes through the supply air passage A.
  • the condensed and liquefied refrigerant is depressurized by the expansion valve 25 to become a low-pressure gas-liquid two-phase refrigerant, flows to the cooler 26, and exchanges heat with the outdoor air OA to be gasified.
  • the gasified refrigerant passes through the four-way valve 23 and is sucked into the compressor 22.
  • the outdoor air OA passing through the air supply ventilation path A is cooled by the cooler 26, the latent heat load is processed, and supplied to the room 200 as the supply air SA.
  • the four-way valve 13 is set to a state rotated 90 ° from the state shown in FIG.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 12 passes through the four-way valve 13 and flows to the indoor heat exchangers 16 ⁇ / b> A and 16 ⁇ / b> B to exchange heat with room air to be condensed and liquefied.
  • the condensed and liquefied refrigerant is decompressed by the expansion valve 15 to become a low-pressure gas-liquid two-phase refrigerant, flows to the outdoor heat exchanger 14 and exchanges heat with air to be gasified.
  • the gasified refrigerant passes through the four-way valve 13 and is sucked into the compressor 12.
  • the indoor air sent by the blowers 18A and 18B for the indoor heat exchangers 16A and 16B is warmed and blown out into the room 200 to heat the room 200.
  • the four-way valve 23 is set to a state rotated 90 ° from the state of FIG.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 22 flows through the four-way valve 23 to the cooler 26 and exchanges heat with the outdoor air OA passing through the supply air passage A to be condensed and liquefied.
  • the cooler 26 operates as a condenser during heating operation.
  • the refrigerant condensed and liquefied in the cooler 26 is decompressed by the expansion valve 25 to become a low-pressure gas-liquid two-phase refrigerant, flows to the outdoor heat exchanger 24, exchanges heat with air, and is gasified.
  • the gasified refrigerant passes through the four-way valve 23 and is sucked into the compressor 22.
  • the outdoor air OA passing through the supply air passage A is warmed by the cooler 26 that operates as a condenser, and the warmed air is supplied to the room 200 as the supply air SA.
  • the air conditioning system 100 may perform at least a cooling operation, and the four-way valves 13 and 23 can be omitted. (Adjustment operation of the evaporation temperature of the refrigerant circuit 21) Next, the adjustment operation of the evaporation temperature in the refrigerant circuit 21 of the air conditioning system 100 will be described. As will be described in detail later with reference to the flowchart of FIG. 7, in the adjustment operation of the evaporation temperature of the refrigerant circuit 21, the maximum evaporation temperature Te_max and the minimum evaporation temperature Te_min are determined, and the target evaporation is performed based on the humidity difference ⁇ X in the range between these. The temperature Te is determined. Thus, two examples of the method for determining the target evaporation temperature Te will be described.
  • FIG. 5 is an explanatory diagram of a method for determining the target evaporation temperature Te according to the humidity difference ⁇ X.
  • the horizontal axis indicates the humidity difference ⁇ X
  • the vertical axis indicates the evaporation temperature.
  • the absolute humidity x_ra [kg / kg ′] of the indoor air RA detected by the temperature / humidity detection unit 32 of FIG. 3 and the setting input unit 44 of FIG.
  • a humidity difference ⁇ X (latent heat load) from the absolute humidity Xa_tgt [kg / kg ′] of the target air is calculated.
  • the target evaporation temperature Te [° C.] is determined according to the humidity difference ⁇ X.
  • the target evaporation temperature Te is determined within an evaporation temperature range between the maximum evaporation temperature Te_max [° C.] and the minimum evaporation temperature Te_min [° C.].
  • the target evaporation temperature Te is set to be smaller as the humidity difference ⁇ X is larger in the range of 0 to X1. For example, as shown in FIG. 5, when the humidity difference ⁇ X is zero, the target evaporation temperature Te is set to the maximum evaporation temperature Te_max. When the humidity difference ⁇ X is the allowable humidity difference X1, the target evaporation temperature Te is set to the minimum evaporation temperature Te_min.
  • the relationship between the humidity difference ⁇ X and the target evaporation temperature Te may be a linear relationship (straight line) as shown in FIG. 5, or may be determined by a function that decreases the inclination angle as the humidity difference ⁇ X decreases. Can be set.
  • FIG. 6 is an explanatory diagram of a method for determining the target evaporation temperature Te according to the dew point temperature difference ⁇ Tdp.
  • the horizontal axis represents the dew point temperature difference ⁇ Tdp
  • the vertical axis represents the evaporation temperature.
  • the target evaporation temperature Te is determined within an evaporation temperature range determined between the maximum evaporation temperature Te_max [° C.] and the minimum evaporation temperature Te_min [° C.].
  • the target evaporation temperature Te is set to be smaller as the dew point temperature difference ⁇ Tdp is larger in the range of 0 to Tdp1.
  • the target evaporation temperature Te is set to the maximum evaporation temperature Te_max.
  • the target evaporation temperature Te is set to the minimum evaporation temperature Te_min.
  • the relationship between the dew point temperature difference ⁇ Tdp and the target evaporation temperature Te may be a linear relationship (straightness) as shown in FIG. 6, or may be determined by a function that decreases the tilt angle as the dew point temperature difference ⁇ Tdp decreases. Well, it can be set arbitrarily.
  • the centralized controller 102 transmits information on the determined target evaporation temperature Te to the control unit 51, and the control unit 51 controls the refrigerant circuit (the frequency of the compressor 22) of the refrigerant circuit 21 so that the target evaporation temperature Te is reached. Control, rotation speed control of the blower 27, etc.).
  • the air conditioning system optimizes the heat treatment distribution between the internal air conditioner (air conditioner) and the external air conditioner (ventilator) by determining the evaporation temperature Te as described above.
  • the external air conditioner processes latent heat and the internal air conditioner operates to process sensible heat.
  • the centralized controller 102 sets the evaporating temperature Te of the external controller to the absolute humidity difference ⁇ X (FIG. 5) or the dew point temperature difference ⁇ Tdp (FIG. ).
  • FIG. 7 is a flowchart showing the operation of the air conditioning system according to Embodiment 1 of the present invention.
  • the process of the flowchart of FIG. 7 is called from the main routine and executed when a driving instruction is issued, or every predetermined time or every predetermined condition is satisfied.
  • the operation of the centralized controller 102 will be described with reference to FIG.
  • the centralized controller 102 starts the operation of the refrigerant circuit 21 and starts a timer.
  • the centralized controller 102 acquires the temperature and absolute humidity of the indoor air RA and the temperature and absolute humidity of the outdoor air OA from the detection values of the temperature / humidity detection unit 31 and the temperature / humidity detection unit 32 (step S1).
  • the centralized controller 102 determines whether or not the ventilation device 3 of the refrigerant circuit 21 is using the total heat exchanger 30 (step S2). Whether or not the ventilation device 3 uses the total heat exchanger 30 can be determined, for example, by whether or not the centralized controller 102 itself has switched to a bypass air path that bypasses the total heat exchanger 30.
  • the ventilator 3 uses the total heat exchanger 30 (YES in S2), the absolute humidity exchange efficiency ⁇ hx of the total heat exchanger 30, the absolute humidity x_ra of the indoor air RA, and the absolute humidity x_oa of the outdoor air OA Then, the absolute humidity x_0 of the intake air IA is calculated, and the absolute humidity x_0 is converted into a dew point temperature to determine the dew point temperature Tdp_0 of the intake air IA (step S3).
  • concentration is performed.
  • the controller 102 converts the absolute humidity of the outdoor air OA into a dew point temperature, obtains the dew point temperature of the outdoor air OA, and sets this as the dew point temperature Tdp_0 of the intake air IA (step S4).
  • the maximum evaporation temperature Te_max is determined based on the relationship among the dew point temperature Tdp_0 of the intake air IA, the dew point temperature Tdp_in of the indoor air RA at the target absolute humidity, and the temperature efficiency ⁇ t of the cooler 26 (step S5). Then, the centralized controller 102 determines the minimum evaporation temperature Te_min in step S6.
  • FIG. 8 is an air diagram showing changes in the air state in the supply air passage A of the ventilator of FIG.
  • the vertical axis of the air diagram of FIG. 8 is the absolute humidity [kg / kg ′] of air, and the horizontal axis is the dry bulb temperature [° C.] of air.
  • the air state is represented by one point on the air diagram from the dry bulb temperature and the absolute humidity, and FIG. 8 shows the air states of the outdoor air OA, the intake air IA, and the supply air SA. .
  • the outdoor air OA is hotter and humid than the indoor air RA will be described as an example.
  • outdoor air OA undergoes total heat exchange with indoor air RA from exhaust ventilation path B when passing through total heat exchanger 30 and is cooled and dehumidified to become intake air IA. 26 flows in.
  • the suction air IA that has flowed into the cooler 26 is cooled to a dew point temperature Tdp_0 or lower when passing through the cooler 26, cooled and dehumidified, and supplied to the room 200 as supply air SA.
  • the outdoor air OA is cooled and dehumidified by total heat exchange with the indoor air RA in the total heat exchanger 30, and further cooled and dehumidified by the cooler 26 before being supplied to the room 200.
  • the dew point temperature Tdp_sa of the supply air SA is equal to or lower than the dew point temperature Tdp_in of the target room air
  • the latent heat load of the room 200 is processed and the room 200 is moved to the target absolute humidity ( Or the target dew point temperature) or lower can be achieved.
  • the indoor humidity can be gradually lowered to the target value by ventilating the supply air SA with the room air.
  • the dew point temperature Tdp_sa of the supply air SA only needs to match the target dew point temperature Tdp_in.
  • the evaporation temperature of the cooler 26 may be adjusted. If the evaporation temperature of the cooler 26 increases, the absolute humidity (dew point temperature) of the supply air SA increases. Therefore, the latent heat treatment capability of the cooler 26 decreases, and if the evaporation temperature of the cooler 26 decreases, the absolute value of the supply air SA increases. Since the humidity decreases, the latent heat treatment capability of the cooler 26 increases.
  • the dew point temperature Tdp_sa of the supply air SA is determined as the dew point temperature of the room air RA at the target absolute humidity.
  • the evaporation temperature when it coincides with (or the target dew point temperature) Tdp_in may be set as the maximum value of the evaporation temperature of the cooler 26 (hereinafter referred to as the maximum evaporation temperature Te_max).
  • the target evaporation temperature Te is set in a predetermined range below the maximum evaporation temperature Te_max, the latent heat treatment of the cooler 26 does not become excessive, and energy consumption can be reduced while maintaining comfort.
  • the relationship between the dew point temperature Tdp_0 of the intake air IA flowing into the cooler 26, the dew point temperature (or target dew point temperature) Tdp_in of the indoor air RA at the target absolute humidity, and the temperature efficiency ⁇ t of the cooler 26 Based on this, the maximum evaporation temperature Te_max is determined.
  • the temperature efficiency ⁇ t is a fixed value set in advance according to the refrigeration capacity of the refrigerant circuit 21, the heat exchange capacity of the cooler 26, and the like.
  • the control device 101 determines the dew point temperature Tdp_0 of the intake air IA based on the absolute humidity x_0 of the intake air IA flowing into the cooler 26. Then, the control device 101 compares the difference between the dew point temperature Tdp_0 of the intake air IA and the target dew point temperature Tdp_in, and the difference between the dew point temperature Tdp_0 of the intake air IA and the maximum evaporation temperature Te_max that is the evaporation temperature that matches the target dew point temperature Tdp_in. The maximum evaporating temperature Te_max is determined so that the ratio to the temperature efficiency ⁇ t of the cooler 26 matches.
  • the control device 101 Since the target evaporation temperature Te is set lower than the maximum evaporation temperature Te_max as shown in FIGS. 5 and 6, the control device 101 sets the refrigerant pressure when the dew point temperature of the supply air SA exceeds the maximum evaporation temperature Te_max.
  • the compressor and the like are controlled so as to decrease.
  • the control device 101 controls the frequency of the compressor 22 so as to reduce the refrigerant pressure.
  • the rotational speed control of the blower 27, the opening degree change control of the expansion valve 25, and the like may be performed.
  • the dew point temperature Tdp_0 of the suction air IA flowing into the cooler 26 can be converted from the absolute humidity x_0 of the suction air IA flowing into the cooler 26.
  • the absolute humidity x_0 of the intake air IA can be obtained from the absolute humidity exchange efficiency ⁇ hx of the total heat exchanger 30, the absolute humidity x_ra of the indoor air RA, and the absolute humidity x_oa of the outdoor air OA.
  • the absolute humidity exchange efficiency ⁇ hx of the total heat exchanger 30 is a value inherent to the total heat exchanger 30 and is a preset value.
  • the absolute humidity x_ra of the indoor air RA is detected by the temperature / humidity detector 32.
  • the absolute humidity x_oa of the outdoor air OA is detected by the temperature / humidity detection unit 31.
  • the absolute humidity exchange efficiency ⁇ hx may vary depending on the air conditions for total heat exchange, and may be changed according to the indoor 200 and outdoor air conditions.
  • the absolute humidity x_0 and the dew point temperature Tdp_0 of the intake air IA flowing into the cooler 26 is calculated from the absolute humidity exchange efficiency ⁇ hx, the absolute humidity x_ra, the absolute humidity x_oa, and the like has been described.
  • the invention is not limited to this.
  • a sensor for detecting the dew point temperature Tdp_0 of the intake air IA flowing into the cooler 26 may be provided separately.
  • the centralized controller 102 determines the minimum evaporation temperature Te_min in step S6. Below, the detail of the determination method of minimum evaporation temperature Te_min is demonstrated.
  • the minimum evaporation temperature Te_min is set to a value obtained by subtracting the drop ⁇ from the maximum evaporation temperature Te_max.
  • the descending amount ⁇ may be a preset fixed value (for example, 5K) or may be determined according to the latent heat load in the room 200.
  • the drop ⁇ can be determined from the evaporation temperature at which the latent heat load can be processed when the number of seated persons in the room 200 is maximum.
  • the generated latent heat load Ltp from the room 200 is determined by the following equation (3) from the maximum number of seated persons Np_max [person] and a preset latent heat load Lp [kW / person] per person.
  • the control device 101 controls the frequency of the compressor 22 so as to increase the refrigerant pressure.
  • the rotational speed control of the blower 27, the opening degree change control of the expansion valve 25, and the like may be performed.
  • the target evaporation temperature Te increases. That is, the amount of latent heat treatment can be reduced and the energy consumption can be reduced by raising the target evaporation temperature Te within a range that does not impair the comfort of the room 200.
  • FIG. 6 may be used instead of FIG. 5, but in order to create a map for converting the humidity difference ⁇ Tdp of FIG. 6 into the target evaporation temperature Te, in addition to Te_max and Te_min, further allowance It is necessary to determine the humidity difference Tdp1.
  • a method for determining the allowable humidity difference Tdp1 will also be described.
  • the target evaporation temperature Te rises. That is, within the range that does not impair the comfort of the room 200, the target evaporation temperature Te can be raised to reduce the amount of latent heat treatment, thereby reducing energy consumption.
  • FIG. 5 or FIG. 6 can be created, so that the preparation for determining the target evaporation temperature Te is complete.
  • the centralized controller 102 determines the absolute humidity x_ra of the indoor air RA and the absolute humidity Xa_tgt of the target air within the evaporation temperature range determined between the maximum evaporation temperature Te_max and the minimum evaporation temperature Te_min.
  • the target evaporation temperature Te is determined according to the humidity difference ⁇ X.
  • the dew point temperature Tdpa of the indoor air RA and the target air are within the evaporation temperature range determined between the maximum evaporation temperature Te_max and the minimum evaporation temperature Te_min.
  • the target evaporation temperature Te may be determined according to the dew point temperature difference ⁇ Tdp from the dew point temperature Tdp_tgt.
  • the control device 101 sets the evaporation temperature range Te_max to Te_min, which is the evaporation temperature range, with the maximum evaporation temperature Te_max being the evaporation temperature matching the target dew point temperature Tdp_in as the upper limit. .
  • the control device 101 sets the target value Te of the evaporation temperature within the evaporation temperature range according to the difference ⁇ X between the absolute humidity x_ra of the room air RA and the target absolute humidity Xa_tgt of the room air RA. To decide. Further, for example, as shown in FIG.
  • the control device 101 sets the target value Te of the evaporation temperature within the evaporation temperature range according to the difference ⁇ Tdp between the dew point temperature of the room air RA and the target dew point temperature of the room air RA. To decide.
  • the control device 101 controls the evaporation temperature of the refrigerant circuit 21 so that the determined target value Te is obtained.
  • the centralized controller 102 determines whether or not the target room temperature or the target room humidity has been changed by the setting input unit 44, or whether or not the timer has reached a certain time T1 (step S8). If the condition at step S8 is not satisfied, the centralized controller 102 repeatedly executes the operation at step S7.
  • step S8 when the condition of step S8 is satisfied, the centralized controller 102 resets the timer (step S9), and returns the process to the main routine in step S10.
  • Te_max, Te_min, and target evaporation temperature Te are periodically determined in order to cope with changes in the outside air and changes in the room air.
  • the target evaporation temperature Te is reset after looking at the situation (humidity) after operating for a certain time (here, T1). It is said.
  • the evaporation temperature at which the dew point temperature Tdp_sa of the supply air SA matches the dew point temperature Tdp_in of the indoor air RA at the target absolute humidity is obtained as the maximum evaporation temperature Te_max, and the maximum evaporation temperature Te_max is determined.
  • the evaporation temperature of the refrigerant circuit is controlled to be lower.
  • the control device 101 controls the frequency of the compressor 22 so as to reduce the refrigerant pressure.
  • the opening degree change control of the expansion valve 25, and the like may be performed.
  • the target evaporation temperature Te is determined according to the humidity difference ⁇ X (latent heat load) or the dew point temperature difference ⁇ Tdp (latent heat load). For this reason, evaporation temperature can be made high in the range which does not impair comfort. This effect will be described with reference to FIG.
  • FIG. 9 is a ph diagram of the second refrigerant system in the first embodiment of the present invention.
  • the refrigerant state at the inlet of the compressor 22 changes to the point XA as shown in FIG. 9 by increasing the target evaporation temperature Te as the humidity difference ⁇ X or dew point temperature difference ⁇ Tdp decreases.
  • point XB To point XB.
  • FIG. 10 is a flowchart showing Modification 1 of the operation of the air-conditioning system according to Embodiment 1 of the present invention.
  • the flowchart of FIG. 10 includes processes of steps S13, S14, and S15 instead of steps S3, S4, and S5 in the flowchart of FIG.
  • steps S3, S4, and S5 instead of steps S3, S4, and S5 in the flowchart of FIG.
  • step S2 When the condition of step S2 is satisfied, the centralized controller 102 changes the temperature T0 of the intake air IA to the temperature t_ra of the indoor air RA, the temperature t_oa of the outdoor air OA, and the temperature exchange efficiency ⁇ t2 of the total heat exchanger 30. Based on the determination (step S13). On the other hand, when the condition of step S2 is not satisfied, the centralized controller 102 sets the temperature t_oa of the outdoor air OA as the temperature T0 of the intake air IA (step S14).
  • the maximum evaporation temperature Te_max is determined using the temperature T0 of the intake air IA obtained in step S13 or step S14 (step S15). Other operations are the same as those in FIG.
  • step S13 and step S15 will be described in more detail.
  • FIG. 11 is an air line diagram showing a change in the air state in the supply air passage A of the ventilator of FIG.
  • the dew point temperature Tdp_sa of the supply air SA matches the dew point temperature Tdp_in of the indoor air RA at the target absolute humidity.
  • the temperature T0 of the intake air IA can be determined based on the temperature t_ra of the indoor air RA, the temperature t_oa of the outdoor air OA, and the temperature exchange efficiency ⁇ t2 of the total heat exchanger 30 (step S13).
  • the temperature exchange efficiency ⁇ t2 of the total heat exchanger 30 is a value unique to the total heat exchanger 30, and is set in advance.
  • the temperature t_ra of the indoor air RA is obtained from the temperature / humidity detection unit 32.
  • the temperature t_oa of the outdoor air OA is obtained from the temperature / humidity detection unit 31.
  • temperature exchange efficiency ⁇ t2 may vary depending on the air conditions for total heat exchange, and therefore may be changed according to the indoor 200 and outdoor air conditions.
  • the determination method of the minimum evaporation temperature Te_min, the determination method of the allowable humidity difference X1, and the determination method of the allowable dew point temperature difference Tdp1 are the same as the processing after the determination of Te_max in the first embodiment.
  • FIG. 12 is a diagram showing the relationship between the temperature efficiency ⁇ t of the cooler 26 and the temperature difference ⁇ T. As shown in FIG. 12, there is a relationship that the temperature efficiency ⁇ t of the cooler 26 increases as the temperature difference ⁇ T between the temperature of the intake air IA and the evaporation temperature of the cooler 26 increases.
  • the centralized controller 102 stores information (table) on the relationship between the temperature difference ⁇ T and the temperature efficiency ⁇ t, and calculates the temperature difference ⁇ T between the temperature of the intake air IA and the evaporation temperature of the cooler 26.
  • the temperature efficiency ⁇ t may be determined by detection.
  • FIG. 13 is a diagram illustrating the relationship between the temperature efficiency ⁇ t of the cooler 26 and the air volume of the supply air passage A. As shown in FIG. 13, there is a relationship that the temperature efficiency ⁇ t of the cooler 26 decreases as the air volume in the air supply ventilation path A (the air volume of the exhaust fan 29) increases.
  • the centralized controller 102 stores information (table) on the relationship between the air volume of the air supply path A and the temperature efficiency ⁇ t, and the air volume of the air supply path A (the flow of the exhaust fan 29). The air efficiency) may be detected to determine the temperature efficiency ⁇ t.
  • FIG. 14 is a diagram showing the relationship between the temperature efficiency ⁇ t of the cooler 26 and the degree of superheat SH at the outlet of the cooler 26.
  • the centralized controller 102 stores information (table) on the relationship between the superheat degree SH at the outlet of the cooler 26 and the temperature efficiency ⁇ t, detects the superheat degree SH at the outlet of the cooler 26, The temperature efficiency ⁇ t may be determined.
  • the maximum evaporating temperature Te_max can be determined with higher accuracy by determining the temperature efficiency ⁇ t of the cooler 26 according to the operating conditions and the like.
  • Mode 3 the operation of adjusting the evaporation temperature of the refrigerant circuit 21 has been described. However, the operation of adjusting the evaporation temperature of the refrigerant circuit 11 that mainly processes the sensible heat load may be performed simultaneously. Specific examples will be described below.
  • FIG. 15 is a diagram for explaining the operation of Modification 3 of the air-conditioning system according to Embodiment 1 of the present invention.
  • the horizontal axis indicates the temperature difference ⁇ T
  • the vertical axis indicates the evaporation temperature of the refrigerant circuit 11.
  • the target evaporation temperature Te1 [° C.] is determined in accordance with the temperature difference ⁇ T (sensible heat load) from the temperature Ta_tgt [° C.].
  • the refrigerant circuit 11 corresponds to the “second refrigerant circuit” in the present invention.
  • the target evaporation temperature Te1 is determined within an evaporation temperature range determined between the maximum evaporation temperature Te_max1 [° C.] and the minimum evaporation temperature Te_min1 [° C.].
  • the target evaporation temperature Te1 is set to be smaller as the temperature difference ⁇ T is larger. For example, as shown in FIG. 15, when the temperature difference ⁇ T is zero, the target evaporation temperature Te1 is set to the maximum evaporation temperature Te_max1, and when the temperature difference ⁇ T is the allowable temperature T1, the target evaporation temperature Te1 is set to the minimum evaporation temperature Te_min1. To do.
  • the relationship between the temperature difference ⁇ T and the target evaporation temperature Te1 may be a proportional relationship (straight line) as shown in FIG. 15, or may be determined by a function that decreases the inclination angle as the temperature difference ⁇ T decreases. Can be set.
  • the air conditioning system further includes an air conditioning apparatus for processing a sensible heat load in the room in addition to ventilation apparatus 3 that performs ventilation.
  • the air conditioner includes indoor heat exchangers 16A and 16B, a compressor 12, an outdoor heat exchanger 14 that operates as a condenser, and a refrigerant circuit 21 that circulates refrigerant through expansion valves 15A and 15B.
  • the control device 101 controls the evaporation temperature of the refrigerant circuit 21 according to the difference ⁇ T between the temperature of the room air RA and the target temperature of the room air RA.
  • the centralized controller 102 transmits information of the determined target evaporation temperature Te1 to the control unit 41, and the control unit 41 controls the refrigerant circuit of the refrigerant circuit 11 (the frequency of the compressor 12) so that the target evaporation temperature Te1 is reached. Control, rotation speed control of the fans 17, 18A, 18B, etc.).
  • the maximum evaporation temperature Te_max1 and the minimum evaporation temperature Te_min1 may be fixed values set in advance or may be changed according to the load of the air conditioning harmony system.
  • the maximum evaporation temperature Te_max1 and the minimum evaporation temperature Te_min1 are set low.
  • the maximum evaporation temperature Te_max1 and the minimum evaporation temperature Te_min1 are set high.
  • the temperature of the outdoor air OA may be used, or other load detection means may be used.
  • the sensible heat treatment is controlled by the refrigerant circuit 11 that is the indoor unit system
  • the latent heat treatment is independently controlled by the refrigerant circuit 21 that is the ventilator system. It becomes easy to set both the target humidity and the target value.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air Conditioning Control Device (AREA)
  • Central Air Conditioning (AREA)

Abstract

L'invention concerne un système de climatisation (100) comprenant un échangeur thermique à ventilation (26), un circuit de refroidissement (21), un dispositif de ventilation (3), une unité de détection (33) permettant la détection de la température de point de rosée, et un dispositif de commande (101) permettant la commande de la température d'évaporation dans le circuit de refroidissement (21). Le circuit de refroidissement (21) fait circuler un fluide frigorigène à travers un compresseur (22), un condenseur (24), un détendeur (25) et l'échangeur thermique à ventilation (26). Le dispositif de ventilation (3) fournit de l'air à l'intérieur, l'air ayant été aspiré depuis l'extérieur et soumis à un échange thermique au moyen d'un fluide frigorigène à l'aide de l'échangeur thermique à ventilation (26). L'unité de détection (33) est placée à la sortie du dispositif de ventilation (3) et détecte la température de point de rosée de l'air fourni. Le dispositif de commande (101) réduit la pression du fluide frigorigène lorsque la température de point de rosée de l'air fourni, détectée par l'unité de détection (33), est supérieure à une température de point de rosée souhaitée prédéfinie pour l'air fourni. Selon la présente invention, il est possible d'éviter un traitement de chaleur latente insuffisant et de réduire la quantité d'excédent de chaleur de procédé ; par conséquent, il est possible de réduire au minimum toute diminution du confort et de réduire au minimum toute diminution en termes d'économies d'énergie.
PCT/JP2015/082017 2015-11-13 2015-11-13 Système de climatisation et procédé de commande d'un système de climatisation WO2017081820A1 (fr)

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Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20190089434A (ko) * 2018-01-22 2019-07-31 엘지전자 주식회사 공기조화기 및 그 제어방법
WO2019193639A1 (fr) * 2018-04-02 2019-10-10 三菱電機株式会社 Système de climatisation
JP2020016419A (ja) * 2018-07-27 2020-01-30 三菱電機株式会社 空気調和システム
JPWO2021084568A1 (fr) * 2019-10-28 2021-05-06
EP3961113A4 (fr) * 2019-05-31 2023-01-11 Daikin Industries, Ltd. Système de climatisation
EP4184070A4 (fr) * 2020-12-08 2024-01-24 Samsung Electronics Co Ltd Système de ventilation, système de climatisation intégré et procédé de commande associé

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2022124684A1 (fr) * 2020-12-08 2022-06-16 삼성전자주식회사 Dispositif de ventilation et système de climatisation intégré le comprenant
KR20230105434A (ko) * 2022-01-04 2023-07-11 삼성전자주식회사 환기 시스템 및 그 제어 방법

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001041541A (ja) * 1999-08-03 2001-02-16 Hitachi Ltd 空気調和機
WO2009116160A1 (fr) * 2008-03-21 2009-09-24 三菱電機株式会社 Section intérieure et appareil de climatisation la comprenant
JP2010133612A (ja) * 2008-12-03 2010-06-17 Daikin Ind Ltd 空調システム
JP4975187B2 (ja) * 2009-02-20 2012-07-11 三菱電機株式会社 利用側ユニット及び空気調和装置
JP2013204899A (ja) * 2012-03-28 2013-10-07 Mitsubishi Electric Corp 空気調和システム

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010127522A (ja) * 2008-11-27 2010-06-10 Daikin Ind Ltd 空調システム

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001041541A (ja) * 1999-08-03 2001-02-16 Hitachi Ltd 空気調和機
WO2009116160A1 (fr) * 2008-03-21 2009-09-24 三菱電機株式会社 Section intérieure et appareil de climatisation la comprenant
JP2010133612A (ja) * 2008-12-03 2010-06-17 Daikin Ind Ltd 空調システム
JP4975187B2 (ja) * 2009-02-20 2012-07-11 三菱電機株式会社 利用側ユニット及び空気調和装置
JP2013204899A (ja) * 2012-03-28 2013-10-07 Mitsubishi Electric Corp 空気調和システム

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102104448B1 (ko) 2018-01-22 2020-04-24 엘지전자 주식회사 공기조화기 및 그 제어방법
KR20190089434A (ko) * 2018-01-22 2019-07-31 엘지전자 주식회사 공기조화기 및 그 제어방법
JP7142682B2 (ja) 2018-04-02 2022-09-27 三菱電機株式会社 空気調和システム
WO2019193639A1 (fr) * 2018-04-02 2019-10-10 三菱電機株式会社 Système de climatisation
JPWO2019193639A1 (ja) * 2018-04-02 2020-12-17 三菱電機株式会社 空気調和システム
JP2020016419A (ja) * 2018-07-27 2020-01-30 三菱電機株式会社 空気調和システム
JP7209485B2 (ja) 2018-07-27 2023-01-20 三菱電機株式会社 空気調和システム
EP3961113A4 (fr) * 2019-05-31 2023-01-11 Daikin Industries, Ltd. Système de climatisation
EP4053467A4 (fr) * 2019-10-28 2022-10-26 Mitsubishi Electric Corporation Dispositif de commande, système de climatisation, et procédé de commande pour système de climatisation
WO2021084568A1 (fr) * 2019-10-28 2021-05-06 三菱電機株式会社 Dispositif de commande, système de climatisation, et procédé de commande pour système de climatisation
JPWO2021084568A1 (fr) * 2019-10-28 2021-05-06
JP7329613B2 (ja) 2019-10-28 2023-08-18 三菱電機株式会社 制御装置、空気調和システム及び空気調和システムの制御方法
EP4184070A4 (fr) * 2020-12-08 2024-01-24 Samsung Electronics Co Ltd Système de ventilation, système de climatisation intégré et procédé de commande associé

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