WO2019155614A1 - Dispositif de climatisation, système de climatisation et unité d'échange de chaleur - Google Patents

Dispositif de climatisation, système de climatisation et unité d'échange de chaleur Download PDF

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Publication number
WO2019155614A1
WO2019155614A1 PCT/JP2018/004650 JP2018004650W WO2019155614A1 WO 2019155614 A1 WO2019155614 A1 WO 2019155614A1 JP 2018004650 W JP2018004650 W JP 2018004650W WO 2019155614 A1 WO2019155614 A1 WO 2019155614A1
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Prior art keywords
air
heat
heat medium
refrigerant
temperature
Prior art date
Application number
PCT/JP2018/004650
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English (en)
Japanese (ja)
Inventor
麻里夫 佐藤
Original Assignee
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 JP2019570248A priority Critical patent/JP6903173B2/ja
Priority to PCT/JP2018/004650 priority patent/WO2019155614A1/fr
Publication of WO2019155614A1 publication Critical patent/WO2019155614A1/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
    • 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
    • F24F3/153—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 with subsequent heating, i.e. with the air, given the required humidity in the central station, passing a heating element to achieve the required temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F7/00—Ventilation
    • F24F7/04—Ventilation with ducting systems, e.g. by double walls; with natural circulation
    • F24F7/06—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit
    • F24F7/08—Ventilation with ducting systems, e.g. by double walls; with natural circulation with forced air circulation, e.g. by fan positioning of a ventilator in or against a conduit with separate ducts for supplied and exhausted air with provisions for reversal of the input and output systems
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B27/00—Machines, plants or systems, using particular sources of energy
    • F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
    • Y02A30/00—Adapting or protecting infrastructure or their operation
    • Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
    • Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine

Definitions

  • the present invention relates to an air conditioner, an air conditioning system, and a heat exchange unit that adjust air in an air-conditioned space.
  • Patent Document 1 discloses an air conditioner provided with a refrigerant circuit through which refrigerant flows, a brine circuit through which brine flows, and a ventilation device.
  • heat is exchanged between the return air discharged from the air-conditioned space and exhausted to the non-air-conditioned space, and the refrigerant is recovered.
  • Patent Document 1 includes a heat exchanger that exchanges heat between the brine flowing in the brine circuit and the outside air supplied to the air-conditioned space and the return air.
  • the air conditioner and the ventilator are separate devices and perform separate controls.
  • the air conditioner disclosed in Patent Document 1 includes a heat exchanger that exchanges heat between the brine flowing in the brine circuit and the outside air supplied to the air-conditioned space and the return air.
  • a heat exchanger that exchanges heat between the brine flowing in the brine circuit and the outside air supplied to the air-conditioned space and the return air.
  • the present invention has been made to solve the above-described problems, and provides an air conditioner, an air conditioning system, and a heat exchange unit that recover exhaust heat of a heat medium flowing in a heat medium circuit.
  • the air conditioner according to the present invention includes a pump, a cascade heat exchanger, and a heat medium circuit in which a heat exchanger pipe is connected to a use side heat exchanger that exchanges heat between the air flowing in the air-conditioned space and the heat medium.
  • the heat medium after the heat medium bypass heat exchanger is heat-exchanged by the use side heat exchanger, and the conditioned space Heat exchange with the outside air supplied to the.
  • the exhaust heat of the heat medium after heat exchange is performed by the use side heat exchanger can be recovered, and the recovered exhaust heat can be used for supplying air to the air-conditioned space.
  • FIG. 1 is a schematic diagram showing an air conditioning system 1 according to Embodiment 1 of the present invention.
  • the air conditioning system 1 includes an air conditioner 2 that adjusts air in an air conditioned space 8, a ventilator 6 that ventilates the air conditioned space 8, and a control unit that controls the air conditioner 2 and the ventilator 6. 50.
  • the air conditioner 2 includes, for example, a heat source unit 4 provided in a non-air-conditioned space 9 that is outdoor, a heat exchange unit 3 provided in a ceiling space 10, and a use-side unit 5 that cools or heats the air-conditioned space 8. And.
  • FIG. 2 is a circuit diagram showing the air conditioning system 1 according to Embodiment 1 of the present invention.
  • the heat source unit 4 includes a compressor 21, a flow path switching device 20, a heat source heat exchanger 22, a heat source blower 22 a, and an outside air temperature detection unit 55, and the heat exchange unit 3 Supply the refrigerant.
  • the compressor 21 sucks the refrigerant in a low temperature and low pressure state, compresses the sucked refrigerant, and discharges it as a refrigerant in a high temperature and high pressure state.
  • the flow path switching device 20 switches whether the refrigerant discharged from the compressor 21 flows into the heat source heat exchanger 22 (solid line in FIG.
  • the heat source heat exchanger 22 exchanges heat, for example, between the outside air and the refrigerant.
  • the heat source heat exchanger 22 acts as a condenser during the cooling operation, and acts as an evaporator during the heating operation.
  • the heat source blower 22 a sends outdoor air to the heat source heat exchanger 22.
  • the outside air temperature detection unit 55 detects the temperature of outside air.
  • the use side unit 5 includes a use side heat exchanger 26 and a use side blower 26a, and adjusts the air in the air-conditioned space 8 by the heat medium supplied from the heat exchange unit 3.
  • the use side heat exchanger 26 exchanges heat between, for example, room air and a heat medium.
  • the use side heat exchanger 26 acts as an evaporator during the cooling operation, and acts as a condenser during the heating operation.
  • the use side blower 26 a sends room air to the use side heat exchanger 26.
  • the heat exchange unit 3 is connected to the heat source unit 4 at the refrigerant piping port 11a, and is connected to the use side unit 5 at the heat medium piping port 12a.
  • the heat exchange unit 3 includes a pump 25, a cascade heat exchanger 24, an expansion unit 23, a heat medium bypass circuit 13, and a heat medium flow rate adjustment valve 32.
  • the expansion unit 23 may be provided in the heat source unit 4.
  • the pump 25 may be provided in a pump unit different from the heat exchange unit 3.
  • the heat exchange unit 3 includes a refrigerant bypass circuit 14, a refrigerant flow rate adjustment valve 34, a heat medium temperature detection unit 51, and a refrigerant temperature detection unit 52.
  • the pump 25 conveys the heat medium.
  • the cascade heat exchanger 24 exchanges heat between the refrigerant and the heat medium.
  • the expansion part 23 is a pressure reducing valve or an expansion valve that expands by depressurizing the refrigerant, and is composed of, for example, an electronic expansion valve whose opening degree is adjusted.
  • the heat medium bypass circuit 13 bypasses the heat medium pipe between the cascade heat exchanger 24 and the pump 25, and a part of the heat medium conveyed from the pump 25 flows.
  • the heat medium flow control valve 32 is provided in the heat medium circuit 12 and adjusts the flow rate of the heat medium flowing into the cascade heat exchanger 24.
  • the heat medium temperature detection unit 51 is provided in the heat medium circuit 12 and detects the temperature of the heat medium conveyed from the pump 25.
  • the refrigerant bypass circuit 14 bypasses the refrigerant pipe between the cascade heat exchanger 24 and the compressor 21, and a part of the refrigerant flowing out of the cascade heat exchanger 24 flows.
  • the refrigerant flow rate adjustment valve 34 is provided in the refrigerant circuit 11 and adjusts the flow rate of the refrigerant flowing out of the cascade heat exchanger 24.
  • the refrigerant temperature detector 52 is provided in the refrigerant circuit 11 and detects the temperature of the refrigerant flowing out of the cascade heat exchanger 24.
  • the refrigerant temperature detection unit 52 includes a cooling sensor 52a and a heating sensor 52b.
  • the cooling sensor 52a is provided between the heat source heat exchanger 22 and the refrigerant flow rate adjustment valve 34, and is used for control during cooling operation.
  • the heating sensor 52b is provided between the expansion portion 23 and the refrigerant flow rate adjustment valve 34, and is used for control during heating operation.
  • the refrigerant temperature detector 52 is provided upstream of the refrigerant bypass circuit 14 in each of the cooling operation and the heating operation.
  • the refrigerant temperature detection part 52 is good also as one.
  • the compressor 21, the heat source heat exchanger 22, the expansion unit 23, and the cascade heat exchanger 24 are connected by a refrigerant pipe to constitute the refrigerant circuit 11.
  • the heat medium circuit 12 is configured by connecting the pump 25, the cascade heat exchanger 24, and the use side heat exchanger 26 through a heat medium pipe.
  • the ventilation device 6 ventilates the air-conditioned space 8, and includes a casing 41, a total heat exchanger 42, an air supply fan 43, an exhaust fan 44, an air supply temperature detection unit 53, and an exhaust temperature detection unit. 54, a heat medium bypass heat exchanger 31, and a refrigerant bypass heat exchanger 33.
  • the casing 41 includes an outside air port 45 for taking in outside air, an air supply port 46 for taking outside air taken in from the outside air port 45 into the air-conditioned space 8, a return air port 47 for discharging air from the air-conditioned space 8, and a return air port An exhaust port 48 for exhausting the air discharged from 47 to the air-conditioned space 8 is formed.
  • the total heat exchanger 42 is provided in the casing 41 and exchanges heat between the return air and the outside air.
  • the air supply fan 43 takes in outside air from the outside air port 45 and sends outside air from the air supply port 46 to the air-conditioned space 8.
  • the exhaust fan 44 takes in air in the air-conditioned space 8 from the return air port 47 and discharges air from the exhaust port 48 to the non-air-conditioned space 9.
  • the supply air temperature detector 53 detects the supply air temperature to the air-conditioned space 8.
  • the exhaust temperature detector 54 detects the exhaust temperature from the air-conditioned space 8.
  • the heat medium bypass heat exchanger 31 is provided in the heat medium bypass circuit 13 and exchanges heat between the outside air supplied to the conditioned space 8 and the heat medium.
  • the refrigerant bypass heat exchanger 33 is provided in the refrigerant bypass circuit 14 and exchanges heat between the return air discharged from the air-conditioned space 8 and exhausted into the non-air-conditioned space 9 and the refrigerant.
  • the heat medium flow control valve 32 When the heat medium flow control valve 32 is opened, the heat medium conveyed from the pump 25 passes through the heat medium circuit 12 and flows into the cascade heat exchanger 24, and the heat medium passes through the heat medium bypass circuit 13. Branches to the heat medium flowing into the bypass heat exchanger 31.
  • the heat medium flow control valve 32 when the heat medium flow control valve 32 is closed, the heat medium conveyed from the pump 25 does not pass through the portion of the heat medium circuit 12 where the heat medium flow control valve 32 is provided, and passes through the heat medium bypass circuit 13. And flows into the heat medium bypass heat exchanger 31.
  • the heat medium is configured to flow into the heat medium bypass circuit 13 regardless of whether the heat medium flow control valve 32 is opened or closed.
  • the present invention is not limited to this.
  • the heat medium may be water or brine.
  • the refrigerant that has flowed out of the expansion unit 23 passes through the refrigerant circuit 11 and flows into the heat source heat exchanger 22, and passes through the refrigerant bypass circuit 14 to the refrigerant bypass heat exchanger 33. Branches to incoming refrigerant.
  • the refrigerant flow rate adjustment valve 34 is closed, the refrigerant that has flowed out of the expansion portion 23 does not pass through the portion of the refrigerant circuit 11 where the refrigerant flow rate adjustment valve 34 is provided, but passes through the refrigerant bypass circuit 14 and passes through the refrigerant bypass heat. It flows into the exchanger 33.
  • the refrigerant is configured to flow into the refrigerant bypass circuit 14 regardless of whether the refrigerant flow rate adjustment valve 34 is opened or closed.
  • the present invention is not limited to this.
  • the refrigerant flow rate adjustment valve 34 may be provided in either the refrigerant circuit 11 or the refrigerant bypass circuit 14, so that whether the refrigerant flows only in the refrigerant circuit 11 or only in the refrigerant bypass circuit 14 may be selected.
  • FIG. 3 is a circuit diagram showing an air conditioning system 1 according to a modification.
  • the heat medium flow control valve 32 includes a three-way valve 32a and a three-way valve 32b.
  • the three-way valve 32 a is provided at a connection location between the outlet side of the pump 25 and the heat medium bypass circuit 13 and switches whether the heat medium flows into the heat medium bypass circuit 13.
  • the three-way valve 32 b is provided at a connection location between the heat medium bypass circuit 13 and the inlet side of the cascade heat exchanger 24.
  • the refrigerant flow rate adjustment valve 34 includes a three-way valve 34a and a three-way valve 34b.
  • the three-way valve 34 a is provided at a connection location between the expansion portion 23 and the refrigerant bypass circuit 14 and switches whether the refrigerant flows to the refrigerant bypass circuit 14.
  • the three-way valve 34b is provided at a connection point between the refrigerant bypass circuit 14 and the outlet side of the heat source heat exchanger 22 during cooling.
  • the air conditioner 2 performs a cooling operation.
  • the flow of the refrigerant in the refrigerant circuit 11 will be described.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 21 passes through the flow path switching device 20 and flows into the heat source heat exchanger 22 acting as a condenser, and in the heat source heat exchanger 22, the heat source blower 22a. Heat is exchanged with the outside air sent by the air to condense and liquefy.
  • the condensed refrigerant in the liquid state flows into the expansion section 23 and is expanded and decompressed in the expansion section 23 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the cascade heat exchanger 24 acting as an evaporator, and in the cascade heat exchanger 24, heat is exchanged with the heat medium to evaporate and gasify. At this time, the heat medium is cooled.
  • the evaporated low-temperature and low-pressure gaseous refrigerant passes through the flow path switching device 20 and is sucked into the compressor 21.
  • a part of the refrigerant flowing out of the heat source heat exchanger 22 flows into the refrigerant bypass circuit 14 and reaches the refrigerant bypass heat exchanger 33.
  • the refrigerant exchanges heat with the exhaust gas in the refrigerant bypass heat exchanger 33 and returns to the refrigerant circuit 11 again.
  • the refrigerant flow rate adjustment valve 34 includes a three-way valve 34 a and a three-way valve 34 b, the refrigerant can be controlled so as not to flow into the refrigerant bypass circuit 14.
  • the heat medium transported to the pump 25 flows into the cascade heat exchanger 24, and is cooled by heat exchange with the refrigerant in the cascade heat exchanger 24.
  • the heat medium flowing out from the cascade heat exchanger 24 flows into the use side heat exchanger 26, and heat is exchanged with the air in the air-conditioned space 8 sent by the use side blower 26a in the use side heat exchanger 26 and heated. .
  • the air in the conditioned space 8 is cooled to perform cooling.
  • the heat medium flowing out from the use side heat exchanger 26 is sucked into the pump 25.
  • the heat medium flow control valve 32 includes a three-way valve 32 a and a three-way valve 32 b, the heat medium can be controlled so as not to flow into the heat medium bypass circuit 13.
  • FIG. 4 is a block diagram showing the control unit 50 according to Embodiment 1 of the present invention.
  • the control part 50 controls operation
  • the control unit 50 performs control for interlocking the air conditioner 2 and the ventilator 6.
  • the control unit 50 includes a determination unit 61 and a valve adjustment unit 62.
  • FIG. 5 is a table showing control of the heat medium flow rate adjustment valve 32 and the refrigerant flow rate adjustment valve 34 of the air conditioning system 1 according to Embodiment 1 of the present invention.
  • the determination unit 61 determines whether the heat medium temperature detected by the heat medium temperature detection unit 51 is lower than the supply air temperature detected by the supply air temperature detection unit 53 during the cooling operation. .
  • the valve adjustment unit 62 closes the heat medium flow rate adjustment valve 32.
  • the valve adjustment unit 62 is the heat medium flow rate adjustment valve 32. open. Thereby, a part of the heat medium flowing in the heat medium circuit 12 flows to the heat medium bypass circuit 13, and the remaining part does not flow to the heat medium bypass circuit 13. Accordingly, since the amount of heat transferred from the heat medium to the supply air is reduced, it is possible to prevent the temperature of the air supplied from the supply port 46 to the air-conditioned space 8 in the ventilation device 6 from increasing.
  • the heat medium can be controlled so as not to flow into the heat medium bypass circuit 13, so that the heat medium moves from the supply air to the supply air.
  • the amount of heat to be generated can be further reduced.
  • the determination unit 61 determines whether the refrigerant temperature detected by the cooling sensor 52 a is higher than the exhaust temperature detected by the exhaust temperature detection unit 54 during the cooling operation.
  • the valve adjustment unit 62 closes the refrigerant flow rate adjustment valve 34.
  • all of the refrigerant flowing through the refrigerant circuit 11 flows through the refrigerant bypass circuit 14. Accordingly, the amount of warm heat that moves from the refrigerant to the exhaust increases, so that it can be supercooled.
  • valve adjusting means 62 opens the refrigerant flow rate adjusting valve 34 when the refrigerant temperature detected by the cooling sensor 52a is equal to or lower than the exhaust temperature detected by the exhaust temperature detecting unit 54 during the cooling operation. Thereby, a part of the refrigerant flowing in the refrigerant circuit 11 flows into the refrigerant bypass circuit 14, and the remaining part does not flow into the refrigerant bypass circuit 14. Accordingly, since the amount of heat transferred from the exhaust to the refrigerant is reduced, the degree of supercooling can be maintained.
  • control can be performed so that the refrigerant does not flow to the refrigerant bypass circuit 14, and thus the amount of heat transferred from the exhaust to the refrigerant can be reduced. Further reduction can be achieved.
  • the heat medium bypass heat exchanger 31 after the heat medium bypass heat exchanger 31 is heat-exchanged by the use-side heat exchanger 26 in the heat medium bypass circuit 13 provided on the downstream side of the use-side heat exchanger 26.
  • the heat medium is exchanged with the outside air supplied to the air-conditioned space 8.
  • this Embodiment 1 collect
  • the heat medium bypass heat exchanger 31 exchanges heat between the heat medium flowing into the cascade heat exchanger 24 and the outside air supplied to the air-conditioned space 8, so that cool air is supplied to the supply air during the cooling operation.
  • the cooling operation of the refrigerant circuit 11 can be assisted.
  • the comfort of the air-conditioned space 8 after the supply of air can be improved by exhaust heat recovery.
  • the refrigerant bypass circuit 14 and the refrigerant bypass heat exchanger 33 are provided as in the first embodiment, the refrigerant bypass heat exchanger 33 is exhausted to the non-air-conditioned space 9. Heat exchange is performed between the return air and the refrigerant that has been heat-exchanged by the heat source heat exchanger 22.
  • Embodiment 1 can recover the exhaust heat of the air exhausted into the non-air-conditioned space 9 and use the exhaust heat in the refrigeration cycle of the refrigerant circuit 11.
  • the valve adjusting means 62 closes the heat medium flow rate adjusting valve 32 when it is determined that the heat medium temperature is lower than the supply air temperature during the cooling operation. Thereby, all of the heat medium flowing through the heat medium circuit 12 flows through the heat medium bypass circuit 13. Accordingly, since the amount of heat that moves from the supply air to the heat medium increases, the temperature of the air supplied from the supply port 46 to the air-conditioned space 8 in the ventilation device 6 can be lowered. Further, the valve adjustment means 62 closes the refrigerant flow rate adjustment valve 34 when it is determined that the refrigerant temperature is higher than the exhaust temperature during the cooling operation. As a result, all of the refrigerant flowing through the refrigerant circuit 11 flows through the refrigerant bypass circuit 14. Accordingly, the amount of warm heat that moves from the refrigerant to the exhaust increases, so that it can be supercooled.
  • the exhaust heat of the exhaust after heat-exchange in the total heat exchanger 42 is utilized for an air conditioning.
  • the space that is conditioned by the air conditioner 2 and the space that is supplied and exhausted by the ventilation device 6 are the same space, but may be different spaces. In the case of another space, the same effect as in the first embodiment is obtained when each of the spaces is warmed or cooled.
  • FIG. FIG. 6 is a circuit diagram showing an air conditioning system 1 according to Embodiment 2 of the present invention.
  • the second embodiment exemplifies the case where the heating operation is performed, and the circuit diagram of the second embodiment is the same as the circuit diagram of the first embodiment.
  • the air conditioner 2 performs a heating operation.
  • the flow of the refrigerant in the refrigerant circuit 11 will be described.
  • the refrigerant sucked into the compressor 21 is compressed by the compressor 21 and discharged in a high-temperature and high-pressure gas state.
  • the high-temperature and high-pressure gas refrigerant discharged from the compressor 21 passes through the flow path switching device 20 and flows into the cascade heat exchanger 24 that acts as a condenser. Heat exchanges to condense and liquefy.
  • the condensed liquid refrigerant flows into the expansion section 23 and is expanded and decompressed in the expansion section 23 to become a low-temperature and low-pressure gas-liquid two-phase refrigerant.
  • the gas-liquid two-phase refrigerant flows into the heat source heat exchanger 22 acting as an evaporator, and in the heat source heat exchanger 22, heat is exchanged with the outside air sent by the heat source blower 22a to evaporate and gasify. .
  • the evaporated low-temperature and low-pressure gaseous refrigerant passes through the flow path switching device 20 and is sucked into the compressor 21.
  • a part of the refrigerant discharged from the compressor 21 flows into the refrigerant bypass circuit 14 and reaches the refrigerant bypass heat exchanger 33.
  • the refrigerant exchanges heat with the exhaust gas in the refrigerant bypass heat exchanger 33 and returns to the refrigerant circuit 11 again.
  • the refrigerant flow rate adjustment valve 34 includes a three-way valve 34 a and a three-way valve 34 b, the refrigerant can be controlled so as not to flow into the refrigerant bypass circuit 14.
  • the heat medium conveyed to the pump 25 flows into the cascade heat exchanger 24, and heat is exchanged with the refrigerant in the cascade heat exchanger 24 to be heated.
  • the heat medium that has flowed out of the cascade heat exchanger 24 flows into the use side heat exchanger 26, and in the use side heat exchanger 26, heat is exchanged with the air in the air-conditioned space 8 sent by the use side blower 26a to be cooled. .
  • the air in the air-conditioned space 8 is heated to perform heating.
  • the heat medium flowing out from the use side heat exchanger 26 is sucked into the pump 25.
  • the heat medium flow control valve 32 includes a three-way valve 32 a and a three-way valve 32 b, the heat medium can be controlled so as not to flow into the heat medium bypass circuit 13.
  • FIG. 7 is a table showing control of the heat medium flow rate adjustment valve 32 and the refrigerant flow rate adjustment valve 34 of the air conditioning system 1 according to Embodiment 2 of the present invention.
  • the determination unit 61 determines whether the heat medium temperature detected by the heat medium temperature detection unit 51 is higher than the supply air temperature detected by the supply air temperature detection unit 53 during the heating operation. .
  • the valve adjustment unit 62 closes the heat medium flow rate adjustment valve 32. Thereby, all of the heat medium flowing through the heat medium circuit 12 flows through the heat medium bypass circuit 13. Therefore, since the amount of heat that moves from the heat medium to the supply air increases, the temperature of the air supplied from the supply port 46 to the conditioned space 8 can be increased.
  • the valve adjustment unit 62 heats the heat medium flow rate adjustment valve 32. open. Thereby, a part of the heat medium flowing in the heat medium circuit 12 flows to the heat medium bypass circuit 13, and the remaining part does not flow to the heat medium bypass circuit 13. Accordingly, since the amount of heat transferred from the supply air to the heat medium is reduced, the temperature of the air supplied from the supply port 46 to the air-conditioned space 8 in the ventilation device 6 can be suppressed.
  • the determination unit 61 determines whether the refrigerant temperature detected by the heating sensor 52b is lower than the exhaust temperature detected by the exhaust temperature detection unit 54 during the heating operation. When the determination unit 61 determines that the refrigerant temperature is lower than the exhaust gas temperature, the valve adjustment unit 62 closes the refrigerant flow rate adjustment valve 34. As a result, all of the refrigerant flowing through the refrigerant circuit 11 flows through the refrigerant bypass circuit 14. Accordingly, since the amount of warm heat that moves from the exhaust to the refrigerant increases, evaporation can be assisted.
  • the rotation speed of the heat source blower 22a can also be reduced.
  • the valve adjusting means 62 opens the refrigerant flow rate adjusting valve 34 when the refrigerant temperature detected by the heating sensor 52b is equal to or higher than the exhaust temperature detected by the exhaust temperature detecting unit 54 during the heating operation. Thereby, a part of the refrigerant flowing in the refrigerant circuit 11 flows into the refrigerant bypass circuit 14, and the remaining part does not flow into the refrigerant bypass circuit 14. Therefore, the amount of warm heat moving from the refrigerant to the exhaust is reduced, so that the degree of superheat can be maintained.
  • the heat medium bypass heat exchanger 31 exchanges heat between the heat medium flowing into the cascade heat exchanger 24 and the outside air supplied to the air-conditioned space 8, so that hot air is supplied to the supply air during the heating operation.
  • the heating operation of the circuit 11 can be assisted.
  • the comfort of the air-conditioned space 8 after the supply of air can be improved by exhaust heat recovery.
  • the valve adjustment unit 62 closes the heating medium flow rate adjustment valve 32. Thereby, all of the heat medium flowing through the heat medium circuit 12 flows through the heat medium bypass circuit 13. Therefore, since the amount of heat that moves from the heat medium to the supply air increases, the temperature of the air supplied from the supply port 46 to the conditioned space 8 can be increased. Further, the valve adjustment means 62 closes the refrigerant flow rate adjustment valve 34 when it is determined that the refrigerant temperature is lower than the exhaust temperature during the heating operation. As a result, all of the refrigerant flowing through the refrigerant circuit 11 flows through the refrigerant bypass circuit 14. Accordingly, since the amount of warm heat that moves from the exhaust to the refrigerant increases, evaporation can be assisted.
  • FIG. FIG. 8 is a table showing control of the air conditioning system 1 according to Embodiment 3 of the present invention.
  • the third embodiment is control in the case of performing cooling mainly under low outside air, such as cooling of a computer room in winter, and is different from the first embodiment in that control is performed based on the outside air temperature.
  • the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first embodiment.
  • the control unit 50 stops the heat source unit 4 including the compressor 21 when the temperature of the outside air detected by the outside air temperature detection unit 55 is lower than the outside air temperature threshold. At that time, the control unit 50 continues the operation of the pump 25.
  • the heat medium conveyed by the pump 25 is cooled by the heat medium bypass heat exchanger 31 because it is heat-exchanged with the low-temperature outside air. Therefore, the air-conditioned space 8 can be cooled without operating the heat source unit 4.
  • the control unit 50 continues the operation of the heat source unit 4 including the compressor 21 when the temperature of the outside air detected by the outside air temperature detection unit 55 is equal to or higher than the outside air temperature threshold.
  • FIG. 9 is a table showing control of the heat medium flow control valve 32 of the air conditioning system 1 according to Embodiment 3 of the present invention.
  • the determination unit 61 determines whether the heat medium temperature detected by the heat medium temperature detection unit 51 is higher than the supply air temperature detected by the supply air temperature detection unit 53 during the cooling operation. .
  • the valve adjustment unit 62 closes the heat medium flow rate adjustment valve 32. Thereby, all of the heat medium flowing through the heat medium circuit 12 flows through the heat medium bypass circuit 13.
  • the heat medium can be cooled. Therefore, even if the compressor 21 is stopped and the cooling amount in the cascade heat exchanger 24 is reduced, the heat medium is cooled and the cooling operation can be performed. Thereby, an energy-saving driving
  • FIG. 10 is a circuit diagram showing an air conditioning system 100 according to Embodiment 4 of the present invention.
  • the fourth embodiment is different from the first embodiment in that an air supply side drain pan 161, an exhaust side drain pan 162, a hose 163, and a vaporization filter 164 are provided.
  • the same parts as those in the first embodiment are denoted by the same reference numerals, and the description thereof will be omitted. The description will focus on differences from the first embodiment.
  • the supply-side drain pan 161 is installed below the heat medium bypass heat exchanger 31 and receives condensed water adhering to the heat medium bypass heat exchanger 31.
  • the exhaust side drain pan 162 is installed below the refrigerant bypass heat exchanger 33 and receives condensed water adhering to the refrigerant bypass heat exchanger 33.
  • the hose 163 connects the exhaust side drain pan 162 and the vaporization filter 164.
  • the vaporization filter 164 is provided between the total heat exchanger 42 and the intake fan, and vaporizes moisture.
  • the refrigerant is cooled by exchanging heat with the refrigerant in the refrigerant bypass heat exchanger 33, and moisture contained in the exhaust is condensed.
  • the condensed water flows down from the refrigerant bypass heat exchanger 33 to the exhaust side drain pan 162.
  • the condensed water received by the exhaust side drain pan 162 reaches the vaporization filter 164 through the hose 163.
  • Water is vaporized by the vaporization filter 164 and taken into the supply air that has passed through the vaporization filter 164.
  • the air-conditioned space 8 can be humidified without requiring water supply during heating operation. For example, in a greenhouse where tropical plants and the like are cultivated, heating is performed even in summer. In such a heating application in summer, when the heat medium temperature is lower than the supply air temperature, the valve adjustment means 62 closes the heat medium flow rate adjustment valve 32 to stop the compressor 21 as in the third embodiment.
  • the air-conditioned space 8 can be heated.
  • FIG. 11 is a table showing control of the heat medium flow rate adjustment valve 32 and the refrigerant flow rate adjustment valve 34 of the air conditioning system 100 according to Embodiment 4 of the present invention.
  • the determination unit 61 determines whether the refrigerant temperature detected by the heating sensor 52 b is lower than the exhaust temperature detected by the exhaust temperature detection unit 54 during the heating operation.
  • the valve adjustment unit 62 closes the refrigerant flow rate adjustment valve 34.
  • the amount of warm heat moving from the exhaust to the refrigerant increases, so that evaporation can be assisted.
  • condensed water accumulates in the exhaust side drain pan 162, and the condensed water flows to the vaporization filter 164 through the hose 163. That is, moisture can be supplied to the vaporization filter 164.
  • the determination unit 61 determines whether the heat medium temperature detected by the heat medium temperature detection unit 51 is higher than the supply air temperature detected by the supply air temperature detection unit 53 during the heating operation.
  • the valve adjustment unit 62 closes the heat medium flow rate adjustment valve 32.
  • the amount of heat transferred from the heat medium to the supply air increases, so that the temperature of the air supplied from the supply port 46 to the conditioned space 8 can be increased.
  • the air supplied to the air-conditioned space 8 from the air supply port 46 receives water from the vaporization filter 164 supplied with the moisture condensed in the refrigerant bypass heat exchanger 33. Thereby, humidified warm air can be supplied to the air-conditioned space 8.
  • the dew condensation accumulated in the exhaust side drain pan 162 increases, and the moisture content of the vaporization filter 164 increases, so that the humidification effect is further enhanced.
  • the heat medium temperature is considerably higher than the supply air temperature
  • the amount of water that the supply air receives from the vaporization filter 164 increases, so that the humidification effect is enhanced.
  • the moisture contained in the outside air is transferred to the return air by the total heat exchanger 42 and the relative humidity of the exhaust gas is increased, the humidification effect is further enhanced.
  • the outside air is warmed to return air by the total heat exchanger 42 and the relative humidity of the supply air is lowered, the humidification effect is further enhanced.
  • the supply air is cooled by heat exchange with the heat medium in the heat medium bypass heat exchanger 31, and moisture contained in the supply air is condensed.
  • the condensed water flows down from the heat medium bypass heat exchanger 31 to the supply side drain pan 161. Thereby, it can suppress that the humidity of the air-conditioning space 8 by supply air rises at the time of air_conditionaing
  • FIG. 12 is a table showing control of the heat medium flow control valve 32 of the air conditioning system 100 according to Embodiment 4 of the present invention.
  • the determination unit 61 determines whether the heat medium temperature detected by the heat medium temperature detection unit 51 is lower than the supply air temperature detected by the supply air temperature detection unit 53 during the cooling operation. .
  • the valve adjustment unit 62 closes the heat medium flow rate adjustment valve 32. Thereby, all of the heat medium flowing through the heat medium circuit 12 flows through the heat medium bypass circuit 13.
  • the temperature of the air supplied from the supply port 46 to the air-conditioned space 8 in the ventilation device 6 can be lowered.
  • dehumidified cold air is sent to the air-conditioned space 8.
  • the dehumidifying effect is enhanced.
  • the supply air temperature is considerably higher than the heat medium temperature, the dehumidifying effect is enhanced.

Landscapes

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

Abstract

L'invention concerne un dispositif de climatisation comprenant : un circuit de milieu caloporteur (12) dans lequel circule un milieu caloporteur, et dans lequel une pompe (25), un échangeur de chaleur en cascade (24), et un échangeur de chaleur côté utilisation (26) pour échanger de la chaleur entre un milieu caloporteur et de l'air s'écoulant dans un espace climatisé sont reliés au moyen d'une tuyauterie de milieu caloporteur; un circuit de dérivation de milieu caloporteur (13) dans lequel le milieu caloporteur s'écoulant à partir de l'échangeur de chaleur côté utilisation s'écoule; et un échangeur de chaleur de dérivation de milieu caloporteur (31) qui est disposé dans le circuit de dérivation de milieu caloporteur, et qui échange de la chaleur entre le milieu caloporteur et l'air extérieur fourni à l'espace climatisé.
PCT/JP2018/004650 2018-02-09 2018-02-09 Dispositif de climatisation, système de climatisation et unité d'échange de chaleur WO2019155614A1 (fr)

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JP2019570248A JP6903173B2 (ja) 2018-02-09 2018-02-09 空気調和装置及び空調システム
PCT/JP2018/004650 WO2019155614A1 (fr) 2018-02-09 2018-02-09 Dispositif de climatisation, système de climatisation et unité d'échange de chaleur

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WO2023042268A1 (fr) * 2021-09-14 2023-03-23 三菱電機株式会社 Climatiseur
WO2023126992A1 (fr) * 2021-12-27 2023-07-06 三菱電機株式会社 Dispositif de climatisation extérieur

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JPH08152226A (ja) * 1994-11-30 1996-06-11 Kajima Corp 空気調和装置
JPH09243110A (ja) * 1996-03-13 1997-09-16 Takasago Thermal Eng Co Ltd 空気調和機
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CN106705334A (zh) * 2016-11-18 2017-05-24 仲恺农业工程学院 能量回收型双冷源大焓差蓄能新风机组及其控制方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2023042268A1 (fr) * 2021-09-14 2023-03-23 三菱電機株式会社 Climatiseur
WO2023126992A1 (fr) * 2021-12-27 2023-07-06 三菱電機株式会社 Dispositif de climatisation extérieur

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