WO2019193680A1 - Système de climatisation - Google Patents

Système de climatisation Download PDF

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Publication number
WO2019193680A1
WO2019193680A1 PCT/JP2018/014415 JP2018014415W WO2019193680A1 WO 2019193680 A1 WO2019193680 A1 WO 2019193680A1 JP 2018014415 W JP2018014415 W JP 2018014415W WO 2019193680 A1 WO2019193680 A1 WO 2019193680A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
indoor heat
air
outside air
temperature
Prior art date
Application number
PCT/JP2018/014415
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English (en)
Japanese (ja)
Inventor
貴大 橋川
守 濱田
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 JP2020512156A priority Critical patent/JP7026781B2/ja
Priority to PCT/JP2018/014415 priority patent/WO2019193680A1/fr
Publication of WO2019193680A1 publication Critical patent/WO2019193680A1/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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • 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
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F3/00—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems
    • F24F3/12—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling
    • F24F3/14—Air-conditioning systems in which conditioned primary air is supplied from one or more central stations to distributing units in the rooms or spaces where it may receive secondary treatment; Apparatus specially designed for such systems characterised by the treatment of the air otherwise than by heating and cooling by humidification; by dehumidification

Definitions

  • the present invention relates to an air conditioning system including an outside air supply unit that supplies outside air to a space to be air-conditioned.
  • an air conditioning system that includes an outside air supply unit that supplies outside air to an air-conditioning target space and enables ventilation of the air-conditioning target space.
  • a conventional air conditioning system including an outside air supply unit includes an indoor unit that cools or heats air in a space to be air-conditioned by an indoor heat exchanger housed inside.
  • an air conditioning system that dehumidifies outside air taken into the outside air supply unit and supplies it to the air-conditioning target space has also been proposed.
  • the air conditioning system described in Patent Document 1 includes a refrigerant circuit having an evaporator and a condenser.
  • the evaporator and the condenser of the refrigerant circuit are accommodated in the outside air supply unit.
  • the air conditioning system of patent document 1 cools and dehumidifies the external air taken into the external air supply unit with the evaporator, and heats the external air dehumidified with the condenser. That is, the air conditioning system described in Patent Document 1 performs dehumidification and heating of outside air by using an evaporator and a condenser of one refrigerant circuit.
  • the degree of dehumidification of the outside air depends on how much the outside air is cooled. That is, in order to bring the outside air to a desired humidity, it is necessary to adjust the evaporation temperature of the refrigerant flowing through the evaporator. Further, in order to heat the dehumidified outside air to a desired temperature, it is necessary to adjust the condensation temperature of the refrigerant flowing through the condenser. However, in one refrigerant circuit, it is very difficult to independently adjust the evaporation temperature of the refrigerant flowing through the evaporator and the condensation temperature of the refrigerant flowing through the condenser.
  • the air conditioning system described in Patent Literature 1 cannot heat the dehumidified outside air to a desired temperature when the outside air supply unit performs the reheat dehumidifying operation. For this reason, when the outside air supply unit performs the reheat dehumidifying operation, the air conditioning system described in Patent Document 1 cannot control the temperature of the air blown from the outside air supply unit, and maintains the comfort of the air-conditioning target space. There was a problem that there was a case that could not be.
  • the conventional air conditioning system in which the outdoor air supply unit performs the reheat dehumidification operation includes a refrigerant circuit having an indoor heat exchanger housed in an indoor unit that heats or cools air in an air-conditioning target space, and an outdoor air supply unit. And a refrigerant circuit having an indoor heat exchanger housed in the housing.
  • the present invention has been made to solve the above-described problems, and can control the temperature of the air blown from the outside air supply unit during the reheat dehumidification operation, thereby suppressing an increase in cost.
  • the purpose is to propose a possible air conditioning system.
  • the air conditioning system includes a first indoor heat exchanger, a first refrigerant circuit having a second indoor heat exchanger that functions as an evaporator, and a third indoor heat exchanger that functions as a condenser.
  • An indoor unit having a first housing having a first refrigerant housing, a first air inlet and a first air outlet, in which the first indoor heat exchanger is housed, and a second air inlet and a second air outlet.
  • an outside air supply unit having a second housing in which the second indoor heat exchanger and the third indoor heat exchanger are housed, and in the indoor unit, the first housing is connected to the first housing.
  • Heat exchange is performed between the air in the air-conditioned space sucked into the body and the refrigerant flowing through the first indoor heat exchanger, and the air after the heat exchange is blown out from the first air outlet, and the outside air supply unit Then, the outside air sucked into the second housing from the second suction port is
  • the second indoor heat exchanger is disposed on the upstream side of the third indoor heat exchanger in the flow direction of the outside air that is blown out from the second air outlet and extends from the second suction port to the second air outlet.
  • the dehumidified external air is a 2nd refrigerant circuit different from the 1st refrigerant circuit which has a 2nd indoor heat exchanger. Heated by the third indoor heat exchanger.
  • movement can be controlled.
  • the outdoor air supply unit of the air conditioning system which concerns on this invention has the 1st refrigerant circuit which has the 1st indoor heat exchanger accommodated in the indoor unit, and the 3rd indoor heat exchanger accommodated in the outdoor air supply unit.
  • the reheat dehumidifying operation can be performed using the second refrigerant circuit.
  • the air conditioning system when the outside air supply unit performs the reheat dehumidifying operation, a new heat source such as a heater is not required other than the first refrigerant circuit and the second refrigerant circuit. For this reason, the air conditioning system which concerns on this invention can also suppress a raise of cost.
  • FIG. 1 is a diagram showing a schematic configuration of an air-conditioning system according to Embodiment 1 of the present invention.
  • FIG. 2 is a refrigerant circuit diagram illustrating a first refrigerant circuit of the air-conditioning system according to Embodiment 1 of the present invention.
  • FIG. 3 is a refrigerant circuit diagram illustrating a second refrigerant circuit of the air-conditioning system according to Embodiment 1 of the present invention.
  • FIG. 4 is a diagram illustrating a schematic configuration of an outside air supply unit of the air-conditioning system according to Embodiment 1 of the present invention.
  • the air conditioning system 100 includes a first outdoor unit 3, an indoor unit 4, a second outdoor unit 8, and an outdoor air supply unit 30.
  • the first outdoor unit 3 and the second outdoor unit 8 are disposed outdoors.
  • the indoor unit 4 is provided in the ceiling 102 of the room 101 whose inside is an air-conditioning target space.
  • the indoor unit 4 sucks air in the room 101 and cools or heats it, and blows out the cooled or heated air into the room 101.
  • the air conditioning system 100 which concerns on this Embodiment 1 is provided with the three indoor units 4, the number of the indoor units 4 is arbitrary.
  • the outside air supply unit 30 takes in outside air and supplies the outside air into the room 101.
  • the outside air supply unit 30 is provided on the ceiling 102 of the room 101.
  • the air conditioning system 100 includes a first refrigerant circuit 1 and a second refrigerant circuit 2.
  • Each configuration of the first refrigerant circuit 1 and the second refrigerant circuit 2 is accommodated in any of the first outdoor unit 3, the indoor unit 4, the second outdoor unit 8, and the outdoor air supply unit 30.
  • the first refrigerant circuit 1 includes a compressor 10, an outdoor heat exchanger 11, an expansion valve 12, an expansion valve 13, a first indoor heat exchanger 14, and a second indoor heat exchanger. 15 is provided.
  • the compressor 10 compresses the refrigerant.
  • the outdoor heat exchanger 11 is a heat exchanger that functions as a condenser.
  • the outdoor heat exchanger 11 is connected to the discharge port of the compressor 10.
  • the outdoor heat exchanger 11 is also connected to the first indoor heat exchanger 14 via the expansion valve 12.
  • the compressor 10 and the outdoor heat exchanger 11 are accommodated in the first outdoor unit 3.
  • the first outdoor unit 3 also stores an outdoor unit fan 17.
  • the outdoor unit fan 17 supplies the outdoor heat exchanger 11 with outside air that is a heat exchange target of the refrigerant flowing through the outdoor heat exchanger 11.
  • the expansion valve 12 expands the refrigerant and depressurizes it.
  • the first indoor heat exchanger 14 is a heat exchanger that functions as an evaporator.
  • the first indoor heat exchanger 14 is connected to the outdoor heat exchanger 11 via the expansion valve 12 as described above.
  • the first indoor heat exchanger 14 is connected to the suction port of the compressor 10.
  • the expansion valve 12 and the first indoor heat exchanger 14 are accommodated in the first housing 5 of the indoor unit 4.
  • An indoor unit fan 18 is also housed in the first housing 5 of the indoor unit 4.
  • the air conditioning system 100 includes the three indoor units 4.
  • the first refrigerant circuit 1 is provided with three sets of the expansion valve 12 and the first indoor heat exchanger 14.
  • Each set of the expansion valve 12 and the first indoor heat exchanger 14 is connected in parallel between the outdoor heat exchanger 11 and the suction port of the compressor 10.
  • the indoor unit 4 will be further described with reference to FIG. 1.
  • the first housing 5 includes a first inlet 6 and a first outlet 7 that communicate with the interior of the room 101.
  • the indoor unit fan 18 rotates in the first housing 5
  • the air in the room 101 is sucked into the first housing 5 from the first suction port 6.
  • the air sucked into the first housing 5 exchanges heat with the refrigerant flowing through the first indoor heat exchanger 14.
  • the air after the heat exchange is blown into the room 101 from the first blower outlet 7.
  • the first indoor heat exchanger 14 functions as an evaporator.
  • the indoor unit 4 performs a cooling operation. That is, the air sucked into the first housing 5 is cooled by the refrigerant flowing through the first indoor heat exchanger 14.
  • the first refrigerant circuit 1 includes a four-way valve 16 that switches the connection destination of the discharge port of the compressor 10.
  • the first indoor heat exchanger 14 functions as a condenser.
  • the indoor unit 4 performs a heating operation. That is, the air sucked into the first housing 5 is heated by the refrigerant flowing through the first indoor heat exchanger 14.
  • the expansion valve 13 expands and depressurizes the refrigerant.
  • the second indoor heat exchanger 15 is a heat exchanger that functions as an evaporator.
  • the second indoor heat exchanger 15 is connected to the outdoor heat exchanger 11 via the expansion valve 13.
  • the second indoor heat exchanger 15 is connected to the suction port of the compressor 10. That is, the expansion valve 13 and the second indoor heat exchanger 15 are connected in parallel with the expansion valve 12 and the first indoor heat exchanger 14 between the outdoor heat exchanger 11 and the suction port of the compressor 10. .
  • the expansion valve 13 and the second indoor heat exchanger 15 are accommodated in the second housing 31 of the outside air supply unit 30. Details of the outside air supply unit 30 will be described later.
  • the first refrigerant circuit 1 according to Embodiment 1 is provided on the discharge side of the compressor 10 in order to enable both the cooling operation and the heating operation in the indoor unit 4.
  • a four-way valve 16 is provided.
  • the four-way valve 16 switches the connection destination of the discharge port of the compressor 10. Specifically, when the flow path of the four-way valve 16 is in a state where the discharge port of the compressor 10 is connected to the outdoor heat exchanger 11, the suction port of the compressor 10 is connected to the first indoor heat exchanger 14 and the first heat exchanger 14. Two indoor heat exchangers 15 are connected.
  • the outdoor heat exchanger 11 functions as a condenser
  • the first indoor heat exchanger 14 and the second indoor heat exchanger 15 function as an evaporator.
  • the suction port of the compressor 10 is It is connected to the outdoor heat exchanger 11.
  • the outdoor heat exchanger 11 functions as an evaporator
  • the first indoor heat exchanger 14 and the second indoor heat exchanger 15 function as a condenser.
  • the four-way valve 16 is accommodated in the first outdoor unit 3.
  • it is not necessary to make the 1st indoor heat exchanger 14 function as a condenser it is not necessary to provide the four-way valve 16.
  • the second refrigerant circuit 2 includes a compressor 20, a third indoor heat exchanger 21, an expansion valve 22, and an outdoor heat exchanger 23.
  • the compressor 20 compresses the refrigerant.
  • the third indoor heat exchanger 21 is a heat exchanger that functions as a condenser.
  • the third indoor heat exchanger 21 is connected to the discharge port of the compressor 20.
  • the third indoor heat exchanger 21 is also connected to the outdoor heat exchanger 23 via the expansion valve 22.
  • the expansion valve 22 expands and depressurizes the refrigerant.
  • the expansion valve 22 adjusts the amount of refrigerant flowing to the third indoor heat exchanger 21.
  • the outdoor heat exchanger 23 is a heat exchanger that functions as an evaporator.
  • the outdoor heat exchanger 23 is connected to the third indoor heat exchanger 21 via the expansion valve 22 as described above.
  • the outdoor heat exchanger 23 is connected to the suction port of the compressor 20.
  • the second refrigerant circuit 2 includes a four-way valve 24 provided on the discharge side of the compressor 20.
  • the four-way valve 24 switches the connection destination of the discharge port of the compressor 20. Specifically, when the flow path of the four-way valve 24 is in a state where the discharge port of the compressor 20 is connected to the third indoor heat exchanger 21, the suction port of the compressor 10 is connected to the outdoor heat exchanger 23.
  • the third indoor heat exchanger 21 functions as a condenser
  • the outdoor heat exchanger 23 functions as an evaporator.
  • the suction port of the compressor 20 is connected to the third indoor heat exchanger 21.
  • the third indoor heat exchanger 21 functions as an evaporator
  • the outdoor heat exchanger 23 functions as a condenser.
  • it is not necessary to make the 3rd indoor heat exchanger 21 function as an evaporator it is not necessary to provide the four-way valve 24.
  • the compressor 20, the outdoor heat exchanger 23, and the four-way valve 24 are accommodated in the second outdoor unit 8.
  • the second outdoor unit 8 also stores an outdoor unit fan 25.
  • the outdoor unit fan 25 supplies the outdoor heat exchanger 23 with outside air that is a heat exchange target of the refrigerant flowing through the outdoor heat exchanger 23.
  • the third indoor heat exchanger 21 and the expansion valve 22 are accommodated in the second casing 31 of the outside air supply unit 30.
  • the second housing 31 of the outside air supply unit 30 includes a second suction port 32 and a second air outlet 33.
  • the second suction port 32 is a suction port for taking outside air into the second housing 31.
  • the second suction port 32 communicates with the outdoors via, for example, a duct.
  • the second air outlet 33 is an air outlet for blowing outside air taken into the second housing 31 out of the second housing 31.
  • the 2nd blower outlet 33 is connected with the inside of the room 101 via a duct etc., for example.
  • the second casing 31 houses an air supply fan 36. As the air supply fan 36 rotates, outside air is sucked into the second housing 31 from the second suction port 32, and the outside air sucked into the second housing 31 blows out into the room 101 from the second air outlet 33. Is done.
  • the second casing 31 houses the second indoor heat exchanger 15 of the first refrigerant circuit 1 and the third indoor heat exchanger 21 of the second refrigerant circuit 2.
  • the second indoor heat exchanger 15 is disposed upstream of the third indoor heat exchanger 21 in the flow direction of the outside air from the second suction port 32 to the second blower outlet 33. That is, when the outside air supply unit 30 performs the reheat dehumidifying operation described later, the outside air sucked into the second casing 31 is cooled and dehumidified by the refrigerant flowing through the second indoor heat exchanger 15 functioning as an evaporator.
  • the dehumidified outside air is heated by the refrigerant flowing through the third indoor heat exchanger 21 functioning as a condenser and blown out into the room 101.
  • the second casing 31 also includes a third suction port 34 and a third outlet 35.
  • the third suction port 34 is a suction port for taking air in the room 101 into the second housing 31.
  • the third suction port 34 communicates with the inside of the room 101 through, for example, a duct.
  • the third outlet 35 is an outlet for blowing out the air in the room 101 taken into the second casing 31 to the outside of the second casing 31.
  • the 3rd blower outlet 35 is connected with the outdoors through the duct etc., for example.
  • the second housing 31 houses an exhaust fan 37.
  • the exhaust fan 37 rotates, the air in the room 101 is sucked into the second housing 31 from the third suction port 34, and the air in the room 101 sucked into the second housing 31 becomes the third air outlet. 35 is blown out outdoors. Further, in the second casing 31 according to the first embodiment, total heat exchange in which heat is exchanged between outside air sucked from the second suction port 32 and air in the room 101 sucked from the third suction port 34. A vessel 38 is also provided.
  • the air conditioning system 100 includes a plurality of sensors and a control device 50 that controls each component of the air conditioning system 100 based on detection values of these sensors.
  • the air conditioning system 100 includes a temperature sensor 41 that detects the dry bulb temperature of the air in the room 101, that is, the dry bulb temperature of the air in the air-conditioning target space.
  • the temperature sensor 41 is provided around the first suction port 6 of the indoor unit 4. Note that the position of the temperature sensor 41 is arbitrary as long as the dry bulb temperature of the air in the air-conditioning target space can be detected.
  • the air conditioning system 100 also includes a humidity sensor 42 that detects the absolute humidity of the air in the room 101, that is, the absolute humidity of the air in the air-conditioning target space.
  • the humidity sensor 42 is provided around the third suction port 34 of the outside air supply unit 30.
  • the position of the humidity sensor 42 is arbitrary as long as the absolute humidity of the air in the air-conditioning target space can be detected.
  • the air conditioning system 100 includes a temperature sensor 43 that detects the dry bulb temperature of the air blown from the second outlet 33 of the outside air supply unit 30.
  • the temperature sensor 43 is provided around the second outlet 33 of the outside air supply unit 30.
  • the position of the temperature sensor 43 is arbitrary as long as the dry bulb temperature of the air blown from the second outlet 33 of the outside air supply unit 30 can be detected.
  • the dry bulb temperature is indicated.
  • absolute humidity is indicated when simply expressed as humidity.
  • FIG. 5 is a block diagram showing the control device of the air-conditioning system according to Embodiment 1 of the present invention.
  • the control device 50 is configured with dedicated hardware or a CPU (Central Processing Unit) that executes a program stored in a memory.
  • the CPU is also referred to as a central processing unit, a processing unit, an arithmetic unit, a microprocessor, a microcomputer, or a processor.
  • control device 50 When the control device 50 is dedicated hardware, the control device 50 may be, for example, a single circuit, a composite circuit, an ASIC (Application Specific Integrated Circuit), an FPGA (Field-Programmable Gate Array), or a combination of these. Applicable. Each functional unit realized by the control device 50 may be realized by individual hardware, or each functional unit may be realized by one piece of hardware.
  • ASIC Application Specific Integrated Circuit
  • FPGA Field-Programmable Gate Array
  • each function executed by the control device 50 is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are described as programs and stored in a memory.
  • the CPU implements each function of the control device 50 by reading and executing a program stored in the memory.
  • the memory is, for example, a nonvolatile or volatile semiconductor memory such as a RAM, a ROM, a flash memory, an EPROM, or an EEPROM.
  • a part of the function of the control device 50 may be realized by dedicated hardware, and a part may be realized by software or firmware.
  • the control device 50 includes an input unit 51, a calculation unit 52, a control unit 53, and a storage unit 54 as functional units.
  • the input unit 51 is a functional unit to which detection values of the temperature sensor 41, the humidity sensor 42, and the temperature sensor 43 are input. Operation modes of the indoor unit 4 and the outside air supply unit 30 are also input to the input unit 51 from a remote controller (not shown).
  • the calculation unit 52 is a functional unit that calculates control target values and the like of each component of the air conditioning system 100 based on information input to the input unit 51 and information stored in the storage unit 54.
  • the control unit 53 is a functional unit that controls each component of the air conditioning system 100 based on the control target value and the like calculated by the calculation unit 52.
  • the storage unit 54 is a functional unit that stores information input to the input unit 51, setting values used by the control unit 53, control target values, and the like.
  • the reheat dehumidifying operation is an operation of the outside air supply unit 30 that heats the dehumidified outside air and supplies the heated outside air into the room 101 that is the air-conditioning target space.
  • the outside air supply unit 30 performs the reheat dehumidification operation.
  • the sensible heat load and the latent heat load in the room 101 are determined as follows, for example. Note that the user may instruct the control device 50 of the air conditioning system 100 to cause the outside air supply unit 30 to perform the reheat dehumidification operation using a remote controller (not shown).
  • the calculation unit 52 of the control device 50 calculates ⁇ T, which is a difference obtained by subtracting the indoor target temperature from the temperature detected by the temperature sensor 41.
  • the indoor target temperature is stored in the storage unit 54 in advance.
  • (DELTA) T is in the prescription
  • ⁇ T is calculated not only when the first refrigerant circuit 1 is operating, but also when the first refrigerant circuit 1 is stopped.
  • the calculation unit 52 of the control device 50 calculates ⁇ X, which is a difference obtained by subtracting the indoor target humidity from the detected humidity of the humidity sensor 42.
  • the indoor target humidity is stored in advance in the storage unit 54.
  • (DELTA) X is larger than the threshold value previously memorize
  • control unit 53 of the control device 50 reheats the outside air supply unit 30. Start dehumidifying operation.
  • the calculation unit 52 uses the detected temperatures of all the temperature sensors 41. , ⁇ T is calculated. And in this Embodiment 1, when all (DELTA) T is in the prescription
  • the control unit 53 switches the flow path of the four-way valve 16 of the first refrigerant circuit 1 so that the second indoor heat exchanger 15 functions as an evaporator. Then, the control unit 53 activates the first refrigerant circuit 1. In addition, when the 2nd indoor heat exchanger 15 functions as an evaporator, the 1st indoor heat exchanger 14 of the 1st refrigerant circuit 1 also functions as an evaporator. For this reason, when there is an indoor unit 4 that is not performing the cooling operation, the control unit 53 performs the cooling operation so that the refrigerant does not flow to the first indoor heat exchanger 14 of the indoor unit 4 that is not performing the cooling operation.
  • the expansion valve 12 of the indoor unit 4 that is not performing is closed. Moreover, the control part 53 switches the flow path of the four-way valve 24 of the 2nd refrigerant circuit 2 so that the 3rd indoor heat exchanger 21 may function as a condenser. Then, the control unit 53 activates the second refrigerant circuit 2. Thereby, the outside air sucked into the second casing 31 of the outside air supply unit 30 is cooled and dehumidified by the refrigerant flowing through the second indoor heat exchanger 15 functioning as an evaporator. The dehumidified outside air is heated by the refrigerant flowing through the third indoor heat exchanger 21 functioning as a condenser and blown out into the room 101.
  • FIG. 6 is an air diagram showing a change in the state of the outside air passing through the outside air supply unit when the outside air supply unit is performing the reheat dehumidification operation in the air conditioning system according to Embodiment 1 of the present invention.
  • shaft of FIG. 6 has shown absolute temperature
  • shaft of FIG. 6 has shown dry-bulb temperature.
  • the state of the outside air sucked into the second housing 31 from the second suction port 32 is defined as a point OA.
  • the outside air in the state of the point OA sucked into the second housing 31 exchanges heat with the air in the room 101 sucked into the second housing 31 from the third suction port 34 when passing through the total heat exchanger 38. And it will cool and will be in the state of point T1.
  • the outside air that has passed through the total heat exchanger 38 and has reached the point T1 is cooled by the refrigerant flowing through the second indoor heat exchanger 15 when passing through the second indoor heat exchanger 15 that functions as an evaporator. It is dehumidified and enters the state of point T2.
  • the outside air in the state of point T2 flowing out from the second indoor heat exchanger 15 is heated by the refrigerant flowing through the third indoor heat exchanger 21 when passing through the third indoor heat exchanger 21 functioning as a condenser. It will be in the state of point SA. Then, the outside air in the state of the point SA flowing out from the third indoor heat exchanger 21 is blown out from the second air outlet 33 of the second housing 31 and supplied into the room 101.
  • the outdoor air supply unit 30 includes the first refrigerant circuit 1 having the first indoor heat exchanger 14 housed in the indoor unit 4 and the third indoor heat housed in the outdoor air supply unit 30.
  • the reheat dehumidification operation can be performed using the second refrigerant circuit 2 having the exchanger 21. That is, in the air conditioning system 100 according to Embodiment 1, when the outside air supply unit 30 performs the reheat dehumidifying operation, a new heat source such as a heater is provided in addition to the first refrigerant circuit 1 and the second refrigerant circuit 2. do not need. For this reason, the air conditioning system 100 which concerns on this Embodiment 1 can also suppress a raise of cost.
  • the second indoor heat exchange is increased as the humidity of the air in the room 101, that is, the air-conditioning target space is larger.
  • the evaporation temperature of the refrigerant flowing through the vessel 15 is lowered.
  • a state where the humidity of the air in the room 101 is the first absolute humidity is defined as a first humidity state.
  • the state where the humidity of the air in the room 101 is the second absolute humidity lower than the first absolute humidity be the second humidity state.
  • the air conditioning system 100 when the outside air supply unit 30 performs the reheat dehumidifying operation, the refrigerant flowing through the second indoor heat exchanger 15 in the first humidity state The evaporation temperature is lower than the evaporation temperature of the refrigerant flowing through the second indoor heat exchanger 15 in the second humidity state.
  • the calculation unit 52 of the control device 50 determines the target evaporation temperature TEI that is the control target value of the evaporation temperature of the refrigerant flowing through the second indoor heat exchanger 15 as follows. is doing. And the control part 53 is the rotation speed and expansion
  • the calculation unit 52 decreases the target evaporation temperature TEI when ⁇ X is large, and increases the target evaporation temperature TEI when ⁇ X is small. For example, the calculation unit 52 determines the target evaporation temperature TEI as shown in FIG.
  • FIG. 7 is a diagram for explaining an example of a method for determining the target evaporation temperature of the second indoor heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention.
  • the storage unit 54 stores in advance an upper limit value TEImax and a lower limit value TEImin of the target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15.
  • the calculation unit 52 sets the target evaporation temperature TEI as the upper limit value TEImax when ⁇ X ⁇ 0. Further, the calculation unit 52 sets the target evaporation temperature TEI as the lower limit value TEImin when ⁇ X> ⁇ X1.
  • the calculation unit 52 assumes that ⁇ X and the target evaporation temperature TEI are in a proportional relationship, and based on a calculation formula or a map stored in the storage unit 54, the upper limit value TEImax and the lower limit value A target evaporation temperature TEI is determined between the value TEImin.
  • ⁇ X1 is an allowable increase in indoor space humidity from the indoor target humidity, and is stored in the storage unit 54. ⁇ X1 may be set in advance or may be arbitrarily changed by the user or the like.
  • the control unit 53 In addition, in the state where the evaporation temperature of the second indoor heat exchanger 15 is the upper limit value TEImax, ⁇ X decreases, and when ⁇ X falls below the threshold value ⁇ Xmin stored in the storage unit 54 in advance, the control unit 53 Then, the compressor 10 is stopped. Further, after the compressor 10 is stopped, when ⁇ X exceeds the threshold value ⁇ Xmin stored in the storage unit 54 in advance, the control unit 53 starts the compressor 10 again.
  • the outside air supply unit 30 when the outside air supply unit 30 performs the reheat dehumidifying operation, based on the temperature of the air blown from the second outlet 33 of the outside air supply unit 30, The condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21 is changed.
  • the state where the temperature of the air blown from the second blower outlet 33 of the outside air supply unit 30 is the first temperature is defined as a first blown state.
  • a state where the temperature of the air blown from the second blower outlet 33 of the outside air supply unit 30 is the second temperature lower than the first temperature is defined as a second blowout state.
  • the refrigerant flowing through the third indoor heat exchanger 21 in the first blowing state The condensation temperature is lower than the condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21 in the second blowing state.
  • the condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21 based on the temperature of the air blown from the second blower outlet 33 of the outside air supply unit 30, the blower is blown from the second blower outlet 33. It is possible to prevent the temperature of the air to rise excessively.
  • the calculation unit 52 of the control device 50 calculates ⁇ TSA, which is a difference obtained by subtracting the detected temperature of the temperature sensor 43 from the target blowing temperature stored in advance in the storage unit 54. . Then, when ⁇ TSA is large, the calculation unit 52 decreases the target condensation temperature TCO that is the control target value of the condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21. Further, the calculation unit 52 increases the target condensation temperature TCO when ⁇ TSA is small. Then, the controller 53 adjusts the rotational speed of the compressor 20 of the second refrigerant circuit 2 so that the condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21 becomes the target condensation temperature TCO during the reheat dehumidification operation. Control. In the first embodiment, the opening degree of the expansion valve 22 is fixed to the specified opening degree during the reheat dehumidifying operation. For example, the calculation unit 52 determines the target condensation temperature TCO as shown in FIG.
  • FIG. 8 is a diagram for explaining an example of a method for determining the target condensation temperature of the third indoor heat exchanger in the air-conditioning system according to Embodiment 1 of the present invention.
  • the storage unit 54 stores in advance an upper limit value TCOmax and a lower limit value TCOmin of the target condensation temperature TCO of the refrigerant flowing through the third indoor heat exchanger 21.
  • the calculation unit 52 sets the target condensation temperature TCO as the lower limit value TCOmin when ⁇ TSA ⁇ 0. Further, the calculation unit 52 sets the target condensation temperature TCO as the upper limit value TCOmax when ⁇ TSA> ⁇ TSA1.
  • the calculation unit 52 assumes that ⁇ TSA and the target condensation temperature TCO are in a proportional relationship, and based on a calculation formula or a map stored in the storage unit 54, the upper limit value TCOmax and the lower limit value The target condensation temperature TCO is determined between the value TCOmin.
  • ⁇ TSA1 is a permissible decrease width from the target blowing temperature of the temperature of the air blown from the second blower outlet 33 of the outside air supply unit 30, and is stored in the storage unit 54.
  • ⁇ TSA1 may be set in advance or may be arbitrarily changed by the user or the like.
  • the control unit 53 In the state where the condensation temperature of the third indoor heat exchanger 21 is at the lower limit value TCOmin, ⁇ TSA decreases, and when ⁇ TSA is lower than the threshold value ⁇ TSAmin stored in the storage unit 54 in advance, the control unit 53 Then, the compressor 20 is stopped. When ⁇ TSA exceeds the threshold value ⁇ TSAmin stored in the storage unit 54 in advance, the control unit 53 starts the compressor 20 again. Alternatively, when ⁇ TSA decreases while the condensation temperature of the third indoor heat exchanger 21 is the lower limit value TCOmin, and ⁇ TSA falls below the threshold value ⁇ TSAmin, the controller 53 determines the opening of the expansion valve 22 as a predetermined value. It may be smaller than the value.
  • the amount of refrigerant flowing through the third indoor heat exchanger 21 may be reduced.
  • the expansion valve 22 In other words, in the state where the condensation temperature of the refrigerant flowing through the third indoor heat exchanger 21 is constant, when the temperature of the air blown out from the second outlet 33 of the outside air supply unit 30 decreases, the expansion valve 22 The opening of becomes smaller. Thereby, it can further prevent that the temperature of the air blown out from the second outlet 33 of the outside air supply unit 30 rises excessively.
  • FIG. 9 is a diagram illustrating an example of a control flow when the outside air supply unit performs the reheat dehumidifying operation in the air-conditioning system according to Embodiment 1 of the present invention.
  • the calculation unit 52 calculates ⁇ X, which is a difference obtained by subtracting the indoor target humidity from the detected humidity of the humidity sensor 42, and the temperature sensor 43 from the target blowing temperature.
  • ⁇ TSA which is a difference obtained by subtracting the detected temperature is calculated.
  • the calculation unit 52 calculates a target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15, for example, as described with reference to FIG.
  • the calculation unit 52 calculates the target condensation temperature TCO of the refrigerant flowing through the third indoor heat exchanger 21, for example, as described with reference to FIG.
  • step S3 the calculation unit 52 compares whether ⁇ X is smaller than the threshold value ⁇ Xmin.
  • the control unit 53 stops the compressor 10 of the first refrigerant circuit 1 in step S4.
  • the control unit 53 drives the compressor 10 in step S5.
  • step S6 the calculation unit 52 compares whether ⁇ TSA is smaller than the threshold value ⁇ TSAmin.
  • the control unit 53 stops the compressor 20 of the second refrigerant circuit 2 in step S7.
  • the control unit 53 makes the opening degree of the expansion valve 22 of the second refrigerant circuit 2 smaller than a specified value in step S7.
  • the control unit 53 drives the compressor 10 and sets the opening of the expansion valve 22 to a specified value.
  • Step S9 after step S7 or step S8 is a step of determining whether or not the reheat dehumidifying operation is complete.
  • ⁇ X or ⁇ T is a start condition for the reheat dehumidifying operation. When it deviates from, it will be in the state where a reheat dehumidification operation is complete
  • the reheat dehumidification operation ends.
  • step S9 If the reheat dehumidification operation is in a state to end in step S9, the reheat dehumidification operation ends. On the other hand, when the reheat dehumidifying operation is not completed in step S9, the process returns to step S1 described above.
  • the air conditioning system 100 includes the first refrigerant circuit 1, the second refrigerant circuit 2, the indoor unit 4, and the outside air supply unit 30.
  • the first refrigerant circuit 1 includes a first indoor heat exchanger 14 and a second indoor heat exchanger 15 that functions as an evaporator.
  • the second refrigerant circuit 2 has a third indoor heat exchanger 21 that functions as a condenser.
  • the indoor unit 4 includes a first suction port 6 and a first air outlet 7 and includes a first housing 5 in which the first indoor heat exchanger 14 is accommodated.
  • the outside air supply unit 30 includes a second suction port 32 and a second outlet 33, and includes a second casing 31 in which the second indoor heat exchanger 15 and the third indoor heat exchanger 21 are accommodated. .
  • the indoor unit 4 heat exchange is performed between the air in the air-conditioning target space sucked into the first housing 5 from the first suction port 6 and the refrigerant flowing through the first indoor heat exchanger 14. Air is blown out from the first air outlet 7.
  • outside air sucked into the second housing 31 from the second suction port 32 is blown out from the second air outlet 33.
  • the second indoor heat exchanger 15 is arranged upstream of the third indoor heat exchanger 21 in the flow direction of the outside air from the second suction port 32 to the second blower outlet 33.
  • the air conditioning system 100 can control the temperature of the air blown from the outside air supply unit 30 during the reheat dehumidification operation. Further, in the outside air supply unit 30 of the air conditioning system 100 according to Embodiment 1, it is not necessary to provide a new heat source such as a heater in the outside air supply unit 30. For this reason, the air conditioning system 100 which concerns on this Embodiment 1 can also suppress a raise of cost.
  • FIG. The target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15 may be determined as in the second embodiment.
  • items that are not particularly described are the same as those in Embodiment 1, and the same functions and configurations as those in Embodiment 1 are described using the same reference numerals.
  • the calculation unit 52 of the control device 50 of the air-conditioning system 100 according to Embodiment 2 determines the target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15 according to the estimated value of the latent heat load.
  • the estimation method of the estimated value of a latent heat load is not specifically limited, It can obtain
  • the estimated value of the latent heat load can be estimated based on the humidity of the outside air temperature, the number of people present in the room 101, and the like. That is, the air conditioning system according to the second embodiment is added to the air conditioning system 100 shown in the first embodiment by adding a detection device that detects information necessary for estimating the estimated value of the latent heat load. System 100 is obtained.
  • the estimated latent heat load is determined for a specified time. It is possible to calculate the evaporation temperature of the refrigerant flowing through the second indoor heat exchanger 15 necessary for processing inside. This calculation is performed by the calculation unit 52. At this time, when the calculated evaporation temperature is equal to or lower than the upper limit value TEImax of the target evaporation temperature TEI and equal to or higher than the lower limit value TEImin, the calculation unit 52 uses the calculated evaporation temperature of the refrigerant flowing through the second indoor heat exchanger 15.
  • a target evaporation temperature TEI is set. Further, when the calculated evaporation temperature exceeds the upper limit value TEImax, the calculation unit 52 sets the target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15 as the upper limit value TEImax. Further, when the calculated evaporation temperature is lower than the lower limit value TEImin, the calculation unit 52 sets the target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15 as the lower limit value TEImin.
  • the air conditioning system 100 can determine the target evaporation temperature TEI of the refrigerant flowing through the second indoor heat exchanger 15 according to the air conditioning load, so that the comfort in the room 101 is maintained. The power consumption can be suppressed by improving the efficiency of the air conditioning system 100.

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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)

Abstract

L'invention concerne un système de climatisation pourvu d'un premier circuit de fluide frigorigène comprenant un premier échangeur de chaleur intérieur et un deuxième échangeur de chaleur intérieur fonctionnant en tant qu'évaporateur, un deuxième circuit de fluide frigorigène comprenant un troisième échangeur de chaleur intérieur fonctionnant en tant que condenseur, une machine intérieure comprenant une première enceinte recevant le premier échangeur de chaleur intérieur et une unité d'alimentation en air extérieur qui comprend une seconde enceinte recevant le deuxième échangeur de chaleur intérieur et le troisième échangeur de chaleur intérieur : dans la machine intérieure, de la chaleur est échangée entre l'air dans un espace à climatiser, aspiré dans la première enceinte, et un fluide frigorigène s'écoulant à travers le premier échangeur de chaleur intérieur et l'air après échange de chaleur est soufflé vers l'espace à climatiser ; dans l'unité d'alimentation en air extérieur, de l'air extérieur aspiré dans la seconde enceinte est soufflé vers l'espace à climatiser ; et le deuxième échangeur de chaleur intérieur est disposé en amont du troisième échangeur de chaleur intérieur dans la direction d'écoulement de l'air extérieur dans la seconde enceinte.
PCT/JP2018/014415 2018-04-04 2018-04-04 Système de climatisation WO2019193680A1 (fr)

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JP2020512156A JP7026781B2 (ja) 2018-04-04 2018-04-04 空気調和システム
PCT/JP2018/014415 WO2019193680A1 (fr) 2018-04-04 2018-04-04 Système de climatisation

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CN113375270A (zh) * 2021-06-21 2021-09-10 海信（广东）空调有限公司 空调器及其控制方法
CN113375271A (zh) * 2021-06-21 2021-09-10 海信（广东）空调有限公司 空调器及其控制方法
WO2023079709A1 (fr) * 2021-11-05 2023-05-11 三菱電機株式会社 Système de traitement d'air
JP7277839B1 (ja) 2022-01-31 2023-05-19 ダイキン工業株式会社 換気装置
WO2023206849A1 (fr) * 2022-04-29 2023-11-02 邯郸美的制冷设备有限公司 Procédé et appareil de commande, et dispositif de climatisation et support de stockage

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JP2005049059A (ja) * 2003-07-31 2005-02-24 Daikin Ind Ltd 空気調和システム
JP2005226922A (ja) * 2004-02-13 2005-08-25 Kimura Kohki Co Ltd ヒートポンプ式空調機
JP2006145070A (ja) * 2004-11-17 2006-06-08 Hitachi Ltd 空調システム及び空調システム制御方法

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Publication number Priority date Publication date Assignee Title
JP2005049059A (ja) * 2003-07-31 2005-02-24 Daikin Ind Ltd 空気調和システム
JP2005226922A (ja) * 2004-02-13 2005-08-25 Kimura Kohki Co Ltd ヒートポンプ式空調機
JP2006145070A (ja) * 2004-11-17 2006-06-08 Hitachi Ltd 空調システム及び空調システム制御方法

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113375270A (zh) * 2021-06-21 2021-09-10 海信（广东）空调有限公司 空调器及其控制方法
CN113375271A (zh) * 2021-06-21 2021-09-10 海信（广东）空调有限公司 空调器及其控制方法
WO2023079709A1 (fr) * 2021-11-05 2023-05-11 三菱電機株式会社 Système de traitement d'air
JP7277839B1 (ja) 2022-01-31 2023-05-19 ダイキン工業株式会社 換気装置
WO2023145162A1 (fr) * 2022-01-31 2023-08-03 ダイキン工業株式会社 Dispositif de ventilation
JP2023111129A (ja) * 2022-01-31 2023-08-10 ダイキン工業株式会社 換気装置
WO2023206849A1 (fr) * 2022-04-29 2023-11-02 邯郸美的制冷设备有限公司 Procédé et appareil de commande, et dispositif de climatisation et support de stockage

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