WO2022244182A1 - Dispositif de ventilation - Google Patents

Dispositif de ventilation Download PDF

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Publication number
WO2022244182A1
WO2022244182A1 PCT/JP2021/019157 JP2021019157W WO2022244182A1 WO 2022244182 A1 WO2022244182 A1 WO 2022244182A1 JP 2021019157 W JP2021019157 W JP 2021019157W WO 2022244182 A1 WO2022244182 A1 WO 2022244182A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
air
temperature
refrigerant
outdoor
Prior art date
Application number
PCT/JP2021/019157
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English (en)
Japanese (ja)
Inventor
宗史 池田
皓亮 宮脇
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.)
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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 PCT/JP2021/019157 priority Critical patent/WO2022244182A1/fr
Priority to JP2023522114A priority patent/JP7550976B2/ja
Publication of WO2022244182A1 publication Critical patent/WO2022244182A1/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
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • 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
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/56—Heat recovery units

Definitions

  • the present disclosure relates to a ventilation device that performs ventilation while suppressing changes in indoor temperature and humidity.
  • Patent Literature 1 proposes a technique for preventing frost from adhering to the surface of a heat exchanger installed in an exhaust passage. Specifically, in the ventilation device of Patent Document 1, when the outside air temperature is low, the rotation of the sensible heat exchange rotor that recovers heat from the high temperature side to the low temperature side between the supply air and the exhaust air and the circulation of the refrigerant in the refrigerant circuit is stopped to increase the temperature of the exhaust path and prevent frost formation.
  • the present disclosure is intended to solve the above problems, and aims to provide a ventilation system that can maintain ventilation volume and reduce energy loss at the same time even when the outside air temperature is low.
  • a ventilator includes an exhaust passage through which exhaust air is discharged to the outside, an air supply passage through which air supplied to the room flows, an exhaust fan arranged in the exhaust passage, and an exhaust fan arranged in the air supply passage.
  • a supply air fan a total heat exchanger that exchanges heat between the exhaust air and the supply air, and a refrigerant circuit that includes a compressor, a first heat exchanger, a first expansion device, and a second heat exchanger; 1 heat exchanger is arranged upstream of the total enthalpy heat exchanger in the supply air flow of the supply air line, and heats the air entering the total enthalpy heat exchanger when the outside air temperature is below the threshold.
  • the ventilation system of the present disclosure since the supplied air is heated by the first heat exchanger and made to flow into the total heat exchanger, frost formation on the total heat exchanger can be suppressed. As a result, even when the outside air temperature is low, the heat recovery between the supply air and the exhaust air can be realized using the total heat exchanger, and both the maintenance of the ventilation amount and the reduction of the energy loss can be achieved.
  • FIG. 1 is a schematic configuration diagram of a ventilator according to Embodiment 1;
  • FIG. 1 is a perspective view of a ventilation unit according to Embodiment 1.
  • FIG. 4 is a flow chart showing the operation of the ventilator according to Embodiment 1.
  • FIG. 4 is a diagram illustrating the flow of air and refrigerant during normal ventilation operation of the ventilator according to Embodiment 1;
  • FIG. 4 is a diagram illustrating the flow of air and refrigerant during frost formation suppression ventilation operation of the ventilation system according to Embodiment 1;
  • 4 is a diagram showing heat recovery efficiency of the ventilation system according to Embodiment 1.
  • FIG. FIG. 5 is a schematic configuration diagram of a ventilator according to Embodiment 2;
  • FIG. 5 is a schematic configuration diagram of a ventilator according to Embodiment 2;
  • FIG. 8 is a perspective view of a ventilation unit according to Embodiment 2;
  • FIG. 10 is a diagram illustrating the flow of air and refrigerant during normal ventilation operation of the ventilation device according to Embodiment 2;
  • FIG. 10 is a diagram for explaining the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator according to Embodiment 2;
  • FIG. 9 is a diagram showing heat recovery efficiency of a ventilation system according to Embodiment 2;
  • FIG. 11 is a schematic configuration diagram of a ventilator according to Embodiment 3;
  • FIG. 11 is a perspective view of a ventilation unit according to Embodiment 3;
  • 10 is a flow chart showing the operation of the ventilator according to Embodiment 3.
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during heating ventilation operation of the ventilation device according to Embodiment 3;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during frost formation suppression ventilation operation of the ventilator according to Embodiment 3;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during the cooling ventilation operation of the ventilator according to Embodiment 3;
  • FIG. 11 is a diagram showing heat recovery efficiency of a ventilation system according to Embodiment 3;
  • FIG. 11 is a schematic configuration diagram of a ventilator according to Embodiment 4;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during heating ventilation operation of the ventilation device according to Embodiment 4;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during frost formation suppression ventilation operation of the ventilator according to Embodiment 4;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during the cooling ventilation operation of the ventilator according to Embodiment 4;
  • FIG. 11 is a diagram showing heat recovery efficiency of a ventilation system according to Embodiment 4;
  • FIG. 11 is a schematic configuration diagram of a ventilator according to Embodiment 5;
  • FIG. 11 is a perspective view of a ventilation unit according to Embodiment 5;
  • FIG. 12 is a diagram illustrating a first state of the air route switching device according to Embodiment 5;
  • FIG. 12 is a diagram for explaining a second state of the air route switching device according to Embodiment 5;
  • FIG. 15 is a diagram illustrating a third state of the air route switching device according to Embodiment 5;
  • FIG. 12 is a diagram for explaining the flow of air and refrigerant during normal ventilation operation of the ventilator according to Embodiment 5;
  • FIG. 11 is a diagram for explaining the flow of air and refrigerant during frost formation suppression ventilation operation of the ventilator according to Embodiment 5;
  • FIG. 14 is a perspective view of the ventilation unit according to Embodiment 5 during frost formation suppression ventilation operation;
  • FIG. 1 is a schematic configuration diagram of a ventilator 1 according to Embodiment 1.
  • the ventilator 1 includes an outdoor unit 100 installed in an outdoor space 301, a ventilation unit 200 installed in a ceiling space 302, and a connection pipe connecting the outdoor unit 100 and the ventilation unit 200. 11 and 13.
  • the ventilation unit 200 may be installed in the indoor space 303 .
  • the outdoor unit 100 includes a compressor 10 , a first expansion device 14 , an outdoor heat exchanger 15 , an outdoor fan 30 and a controller 90 .
  • the ventilation unit 200 includes a first heat exchanger 12, a total heat exchanger 50, an air supply path 51, an air supply fan 52, an exhaust path 53, an exhaust fan 54, and a first supply air temperature sensor 91. , and an outside air temperature sensor 92 .
  • the compressor 10, the first expansion device 14 and the outdoor heat exchanger 15 of the outdoor unit 100, the first heat exchanger 12 of the ventilation unit 200, and the connecting pipes 11 and 13 are connected, A refrigerant circuit is formed.
  • the compressor 10 is, for example, a capacity-controllable inverter compressor.
  • the compressor 10 draws refrigerant and compresses it to a high temperature and high pressure state.
  • a discharge port of the compressor 10 is connected to a connection pipe 11 .
  • the first heat exchanger 12 is, for example, a fin-tube heat exchanger.
  • the first heat exchanger 12 exchanges heat between the air in the outdoor space 301 taken into the air supply path 51 and the refrigerant.
  • the first heat exchanger 12 has one end connected to the connection pipe 11 and the other end connected to the connection pipe 13 .
  • the first heat exchanger 12 functions as a condenser in the frost formation suppression ventilation operation described later.
  • the first heat exchanger 12 may be a corrugated heat exchanger or the like.
  • the first throttle device 14 is, for example, an electronic expansion valve whose opening is variably controlled.
  • the first expansion device 14 decompresses and expands the refrigerant.
  • the first expansion device 14 has one end connected to the connection pipe 13 and the other end connected to the outdoor heat exchanger 15 .
  • the first expansion device 14 may be a capillary tube or an electromagnetic valve.
  • the outdoor heat exchanger 15 is, for example, a fin-tube heat exchanger.
  • the outdoor heat exchanger 15 exchanges heat between the air in the outdoor space 301 supplied by the outdoor fan 30 and the refrigerant.
  • the outdoor heat exchanger 15 has one end connected to the first expansion device 14 and the other end connected to the suction port of the compressor 10 .
  • the outdoor heat exchanger 15 functions as an evaporator in the frost formation suppression ventilation operation described later.
  • the outdoor heat exchanger 15 may be a corrugated heat exchanger or the like.
  • the outdoor fan 30 is, for example, a propeller fan, a sirocco fan, or a cross-flow fan driven by a motor.
  • the outdoor fan 30 draws air from the outdoor space 301 and supplies the air to the outdoor heat exchanger 15 .
  • FIG. 2 is a perspective view of the ventilation unit 200 according to Embodiment 1.
  • the ventilation unit 200 includes an air supply passage 51 through which air is supplied from the outdoor space 301 to the indoor space 303, and an exhaust passage through which air is discharged from the indoor space 303 to the outdoor space 301. a path 53;
  • supply air the air supplied from the outdoor space 301 to the indoor space 303
  • exhaust air the air discharged from the indoor space 303 to the outdoor space 301
  • the air OA in the outdoor space 301, the air SA supplied to the indoor space 303, the air RA in the indoor space 303, and the air EA discharged to the outdoor space 301 are respectively indicated by an arrow.
  • the air OA in the outdoor space 301 heat-exchanged in the first heat exchanger 12 is indicated by an arrow as air OAe.
  • a first heat exchanger 12 , a total heat exchanger 50 , and an air supply fan 52 are arranged in the air supply path 51 of the ventilation unit 200 .
  • a total heat exchanger 50 and an exhaust fan 54 are arranged in the exhaust path 53 of the ventilation unit 200 .
  • the first heat exchanger 12 is arranged in the air supply path 51 between the inlet of the air supply path 51 and the total heat exchanger 50 .
  • the first heat exchanger 12 is arranged upstream of the total heat exchanger 50 in the flow of supply air in the supply air path 51 .
  • the first heat exchanger 12 functions as a condenser and heats the air flowing into the total heat exchanger 50 in the frost formation suppression ventilation operation described later.
  • the total heat exchanger 50 is, for example, a static total heat exchanger.
  • the total heat exchanger 50 exchanges heat between supply air supplied by the supply fan 52 and exhaust air supplied by the exhaust fan 54 .
  • the total heat exchanger 50 is arranged between the first heat exchanger 12 and the air supply fan in the air supply path 51, and is arranged between the inlet of the exhaust path 53 and the exhaust fan 54 in the exhaust path 53. be.
  • the total heat exchanger 50 exchanges heat between the air OA taken from the outdoor space 301 and the air RA taken from the indoor space 303 in the normal ventilation operation described later. Further, the total heat exchanger 50 exchanges heat between the air OAe heated by the first heat exchanger 12 and the air RA taken from the indoor space 303 in the frost formation suppression ventilation operation described later.
  • the total heat exchanger 50 may be a rotary total heat exchanger or the like.
  • the air supply fan 52 and the exhaust fan 54 are, for example, sirocco fans.
  • the air supply fan 52 is arranged at the outlet of the air supply path 51 and supplies the air in the outdoor space 301 to the indoor space 303 .
  • the exhaust fan 54 is arranged at the outlet of the exhaust path 53 and exhausts the air in the indoor space 303 to the outdoor space 301 .
  • the air supply fan 52 and the exhaust fan 54 may be propeller fans or the like.
  • the air supply fan 52 and the exhaust fan 54 may be arranged at the inlet of the air supply path 51 and the inlet of the exhaust path 53, respectively.
  • an air supply duct 401 is connected to the outlet of the air supply path 51 of the ventilation unit 200, and the air SA that has passed through the air supply path 51 is supplied from the air supply duct 401 to the indoor space 303.
  • An exhaust duct 402 is connected to the entrance of the exhaust path 53 of the ventilation unit 200 , and the air RA in the indoor space 303 is taken into the exhaust path 53 from the exhaust duct 402 .
  • the control device 90 is configured by, for example, an analog circuit, a digital circuit, a CPU and memory, or a combination of two or more of these.
  • the control device 90 is communicably connected to a first supply air temperature sensor 91, an outside air temperature sensor 92, a plurality of various sensors (not shown), and an input device such as a remote controller (not shown).
  • the first supply air temperature sensor 91 is, for example, a thermistor.
  • the first supply air temperature sensor 91 is arranged between the first heat exchanger 12 and the total heat exchanger 50 in the supply air passage 51 of the ventilation unit 200 .
  • the first supply air temperature sensor 91 measures the temperature of air passing through the first heat exchanger 12 and flowing into the total heat exchanger 50 .
  • the outside air temperature sensor 92 is, for example, a thermistor.
  • the outside air temperature sensor 92 is arranged at the entrance of the air supply path 51 of the ventilation unit 200 and measures the outside air temperature, which is the temperature of the air in the outdoor space 301 .
  • the control device 90 performs overall control of the ventilation device 1 based on information measured by the first supply air temperature sensor 91, the outside air temperature sensor 92, and other various sensors, and instructions from an input device such as a remote controller. . Specifically, the control device 90 controls the operating frequency of the compressor 10, the rotation speed of the outdoor fan 30, the opening degree of the first throttle device 14, the rotation speeds of the air supply fan 52 and the exhaust fan 54, and the like. Controlling the rotational speeds of the outdoor fan 30, the air supply fan 52, and the exhaust fan 54 also includes ON/OFF switching. Note that the control device 90 may be provided in the ventilation unit 200 .
  • FIG. 3 is a flow chart showing the operation of the ventilator 1 according to the first embodiment.
  • the operation of the ventilator 1 is started by operating a remote controller or the like.
  • the outside air temperature of the outdoor space 301 is measured by the outside air temperature sensor 92 (S1).
  • S2 the outside air temperature sensor 92
  • S2 the threshold is the temperature at which frost formation occurs in the total heat exchanger 50, and is 0° C., for example.
  • FIG. 4 is a diagram illustrating the flow of air and refrigerant during normal ventilation operation of the ventilation device 1 according to Embodiment 1.
  • FIG. 4 the normal ventilation operation when the outside air temperature is lower than the temperature of the indoor space 303 will be described.
  • the flow of supply air is indicated by dashed line arrows
  • the flow of exhaust air is indicated by dashed line arrows.
  • control device 90 stops the compressor 10 and the outdoor fan 30 and drives the air supply fan 52 and the exhaust fan 54 .
  • Low-temperature and low-humidity air taken from the outdoor space 301 into the air supply passage 51 passes through the first heat exchanger 12 and passes through the total heat exchanger 50.
  • flow into The total heat exchanger 50 includes low-temperature, low-humidity air that has passed through the first heat exchanger 12 and high-temperature, high-humidity air (for example, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg) flowing through the exhaust path 53. heat exchange.
  • Medium-temperature and medium-humidity (for example, temperature 10 to 15° C., absolute humidity 5 to 10 g/kg) air heated and humidified by the total heat exchanger 50 is pressurized by the air supply fan 52 and passed through the air supply duct 401. , is supplied to the indoor space 303 .
  • High-temperature and high-humidity for example, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg
  • air taken into the exhaust passage 53 from the indoor space 303 through the exhaust duct 402 flows into the total heat exchanger 50.
  • the total heat exchanger 50 exchanges heat between low-temperature and low-humidity air (eg, temperature of 0 to 5° C., absolute humidity of 0 to 5 g/kg) flowing through the air supply path 51 and high-temperature, high-humidity air flowing through the exhaust path 53.
  • Low-temperature and low-humidity air eg, temperature of 0 to 5° C., absolute humidity of 0 to 5 g/kg
  • Air cooled and dehumidified by the total heat exchanger 50 and having medium temperature and medium humidity for example, a temperature of 5 to 15° C. and an absolute humidity of 5 to 10 g/kg
  • medium temperature and medium humidity for example, a temperature of 5 to 15° C. and an absolute humidity of 5
  • FIG. 5 is a diagram illustrating the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator 1 according to the first embodiment.
  • the flow of supply air is indicated by dashed line arrows
  • the flow of exhaust air is indicated by dashed line arrows.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54. Further, the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the first supply air temperature sensor 91 becomes equal to or higher than a preset temperature.
  • the preset temperature is a temperature at which frost formation on the total heat exchanger 50 can be suppressed, and is 0° C., for example.
  • the control device 90 controls the opening degree of the first expansion device 14 so that the dryness of the refrigerant sucked into the compressor 10 is such that excessive liquid return to the compressor 10 can be suppressed.
  • the dryness that can suppress excessive liquid return to the compressor 10 is, for example, 0.9 or more.
  • Low-temperature and low-humidity air (for example, a temperature of 0° C. or less and an absolute humidity of 0 to 5 g/kg) taken into the air supply passage 51 from the outdoor space 301 flows into the first heat exchanger 12 .
  • the first heat exchanger 12 functions as a condenser, and exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 and high-temperature (for example, 0 to 50° C.) refrigerant.
  • the medium temperature and low humidity air heated by the first heat exchanger 12 flows into the total heat exchanger 50 .
  • the medium-temperature and medium-humidity air heated by the first heat exchanger 12 is air at a temperature that can suppress frost formation on the total heat exchanger 50.
  • the temperature is 0° C. and the absolute humidity is 0 to 5 g. / kg of air.
  • the total heat exchanger 50 combines medium-temperature and low-humidity air heated by the first heat exchanger 12 with high-temperature and high-humidity air (eg, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg) flowing through the exhaust path 53. heat exchange.
  • Medium-temperature and medium-humidity (for example, temperature 10 to 15° C., absolute humidity 5 to 10 g/kg) air heated and humidified by the total heat exchanger 50 is pressurized by the air supply fan 52 and passed through the air supply duct 401. , is supplied to the indoor space 303 .
  • High-temperature and high-humidity for example, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg
  • air taken into the exhaust passage 53 from the indoor space 303 through the exhaust duct 402 flows into the total heat exchanger 50.
  • the total heat exchanger 50 mixes medium temperature and low humidity air (for example, temperature 0° C., absolute humidity 0 to 5 g/kg) heated by the first heat exchanger 12 and high temperature and high humidity air flowing through the exhaust path 53. exchange heat.
  • Air cooled and dehumidified by the total heat exchanger 50 and having medium temperature and medium humidity for example, a temperature of 5 to 15° C. and an absolute humidity of 5 to 10 g/kg
  • medium temperature and medium humidity for example, a temperature of 5 to 15° C. and an absolute humidity of 5 to 10 g/kg
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the first heat exchanger 12 via the connecting pipe 11 .
  • the first heat exchanger 12 exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 from the outdoor space 301 and high-temperature, high-pressure gas refrigerant.
  • the first throttling device 14 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the first expansion device 14 flows into the outdoor heat exchanger 15 .
  • the outdoor heat exchanger 15 exchanges heat between the air in the outdoor space 301 supplied from the outdoor fan 30 and the low-temperature, low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the outdoor heat exchanger 15 is sucked into the compressor 10 again.
  • FIG. 6 is a diagram showing the heat recovery efficiency of the ventilator 1 according to Embodiment 1.
  • FIG. FIG. 6 shows the operation of the air supply fan 52 and the exhaust fan 54 and the heat recovery efficiency of each of sensible heat and latent heat. Further, in FIG. 6 , the fan operation and heat recovery efficiency in the comparative example are indicated by broken lines, and the fan operation and heat recovery efficiency in the present embodiment are indicated by solid lines.
  • the ventilation system of the comparative example is configured such that the air supply fan and the exhaust fan are stopped when the frost formation condition of the total heat exchanger is satisfied.
  • the heat recovery efficiency ⁇ se of sensible heat and the heat recovery efficiency ⁇ la of latent heat were calculated using the following formulas.
  • ⁇ se Q sensible heat_total heat exchanger /Q sensible heat_maximum heat quantity
  • ⁇ la Q latent heat_total heat exchanger /Q latent heat_maximum amount of heat
  • Q sensible heat_total heat exchanger is the amount of sensible heat exchanged in the total heat exchanger 50
  • Q sensible heat_maximum heat amount is the maximum amount that can recover the temperature (sensible heat) difference between indoor air and outdoor air.
  • Q latent heat_total heat exchanger is the amount of latent heat exchanged in the total heat exchanger 50
  • Q latent heat_maximum heat amount is the maximum amount of heat exchange that can recover the difference in humidity (latent heat) between indoor air and outdoor air. be.
  • the ventilation operation is continued without stopping the operation of the air supply fan 52 and the exhaust fan 54 even when the outside air temperature is 0° C. or less, which is the frost condition. can do.
  • the ventilation operation is continued without stopping the operation of the air supply fan 52 and the exhaust fan 54 even when the outside air temperature is 0° C. or less, which is the frost condition. can do.
  • it is possible to suppress an increase in the carbon dioxide concentration in the indoor space 303 due to stoppage of ventilation, and a deterioration in the sanitation of the indoor space 303 such as retention of bacteria or viruses.
  • the heat exchange by the total heat exchanger 50 is continued even when the outside air temperature is 0° C. or less, which is the frosting condition, so that the exhaust gas discharged from the indoor space 303 to the outdoor space 301 sensible and latent heat can be recovered from the
  • the first heat exchanger 12 heats the supply air in the frost suppression ventilation operation, so that the absolute humidity difference required for latent heat exchange can be maintained at the same level as in the normal ventilation operation.
  • it is possible to maintain the ventilation volume of the ventilator 1 and reduce the energy loss.
  • control device 90 may stop the outdoor fan 30 when the outside air temperature is equal to or lower than the threshold.
  • frost formation on the outdoor heat exchanger 15 is suppressed during the frost suppression operation, and stable control of the supply air temperature becomes possible.
  • the heat radiation of the first heat exchanger 12 is due to the amount of heat recovered from the input of the compressor 10 and other heat sources including the exhaust path (when piping etc. constituting the refrigerant circuit are provided around it). shall be When the outdoor fan 30 is stopped, a piping and a valve connecting the upstream and downstream of the outdoor heat exchanger 15 may be provided to bypass the outdoor heat exchanger 15 .
  • FIG. 7 is a schematic configuration diagram of a ventilator 1A according to Embodiment 2. As shown in FIG. In addition, in the ventilator 1A of FIG. 7, the same components as those of the ventilator 1 of Embodiment 1 are given the same reference numerals, and the description thereof is omitted.
  • a ventilator 1A of the present embodiment differs from the ventilator 1 of Embodiment 1 in the configuration of an outdoor unit 100A and a ventilation unit 200A.
  • An outdoor unit 100A of the present embodiment includes a compressor 10 and a control device 90.
  • the ventilation unit 200A of the present embodiment includes, in addition to the same components as those of the first embodiment, a first expansion device 14, a second heat exchanger 16, and a first refrigerant temperature sensor 93. .
  • the second heat exchanger 16 is arranged in the exhaust path 53 of the ventilation unit 200A, thereby making it possible to recover heat from the exhaust gas flowing through the exhaust path 53. As shown in FIG.
  • the first expansion device 14 has the same configuration as in Embodiment 1, with one end connected to the first heat exchanger 12 and the other end connected to the second heat exchanger 16 .
  • the second heat exchanger 16 is, for example, a fin-tube heat exchanger.
  • the second heat exchanger 16 exchanges heat between the air supplied from the exhaust fan 54 and the refrigerant.
  • the second heat exchanger 16 has one end connected to the first expansion device 14 and the other end connected to the connecting pipe 13 .
  • the second heat exchanger 16 functions as an evaporator in a frost formation suppression ventilation operation, which will be described later.
  • the second heat exchanger 16 may be a corrugated heat exchanger or the like.
  • FIG. 8 is a perspective view of a ventilation unit 200A according to Embodiment 2.
  • a first heat exchanger 12, a total heat exchanger 50, and an air supply fan 52 are arranged in the air supply path 51 of the ventilation unit 200A.
  • a total heat exchanger 50, a second heat exchanger 16, and an exhaust fan 54 are arranged in the exhaust path 53 of the ventilation unit 200A.
  • the first expansion device 14 is arranged in the exhaust passage 53 in FIG. 7, it may be arranged in the air supply passage 51 or other places.
  • the second heat exchanger 16 is arranged between the total heat exchanger 50 and the exhaust fan 54 in the exhaust path 53 .
  • the second heat exchanger 16 is arranged downstream of the total heat exchanger 50 in the exhaust flow of the exhaust passage 53 .
  • the second heat exchanger 16 functions as an evaporator and cools the air that has passed through the total heat exchanger 50 in the frost formation suppression ventilation operation described later.
  • the control device 90 of the present embodiment can communicate with a first supply air temperature sensor 91, an outside air temperature sensor 92, a first refrigerant temperature sensor 93, a plurality of various sensors (not shown), and an input device such as a remote controller (not shown). Connected.
  • the first coolant temperature sensor 93 is, for example, a thermistor.
  • the first refrigerant temperature sensor 93 is arranged in the pipe connecting the second heat exchanger 16 and the first expansion device 14 and measures the temperature of the refrigerant flowing into the second heat exchanger 16 .
  • the control device 90 controls the compressor 10, the outdoor fan 30, the first expansion device 14, and the air supply fan 52 based on information measured by each temperature sensor and other various sensors and instructions from an input device such as a remote controller. , and the exhaust fan 54 .
  • ⁇ Ventilator operation> The operation of the ventilator 1A will be described.
  • 1 A of ventilators of this Embodiment perform a normal ventilation operation and a frost formation suppression ventilation operation.
  • a flow chart of the operation of the ventilator 1A is the same as in FIG. That is, when the outside air temperature measured by the outside air temperature sensor 92 is higher than the temperature at which frost formation occurs in the total heat exchanger 50, the control device 90 executes the normal ventilation operation. Further, when the outside air temperature measured by the outside air temperature sensor 92 is equal to or lower than the temperature at which frost formation occurs in the total heat exchanger 50, the control device 90 executes the frost formation suppression ventilation operation. For each run, the air and refrigerant flows are described below.
  • FIG. 9 is a diagram illustrating the flow of air and refrigerant during normal ventilation operation of the ventilator 1A according to the second embodiment. Below, the normal ventilation operation when the temperature of the outdoor space 301 is lower than the temperature of the indoor space 303 will be described. In FIG. 9, the flow of supply air is indicated by broken line arrows, and the flow of exhaust air is indicated by dashed line arrows.
  • control device 90 stops the compressor 10 and the outdoor fan 30 and drives the air supply fan 52 and the exhaust fan 54 .
  • the air flow in the air supply passage 51 during the normal ventilation operation of the present embodiment is the same as the air flow in the air supply passage 51 during the normal ventilation operation of the first embodiment.
  • the air flow in the exhaust passage 53 will be explained.
  • the total heat exchanger 50 exchanges heat between low-temperature and low-humidity air (eg, temperature of 0 to 5° C., absolute humidity of 0 to 5 g/kg) flowing through the air supply path 51 and high-temperature, high-humidity air flowing through the exhaust path 53.
  • Air cooled and dehumidified by the total heat exchanger 50 and having a medium temperature and medium humidity (for example, a temperature of 5 to 15° C. and an absolute humidity of 5 to 10 g/kg) passes through the second heat exchanger 16 and is pressurized by the exhaust fan 54. , is discharged to the outdoor space 301 .
  • FIG. 10 is a diagram for explaining the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator 1A according to Embodiment 2.
  • FIG. 10 the flow of supply air is indicated by dashed arrows, and the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54.
  • the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the first supply air temperature sensor 91 becomes equal to or higher than a preset temperature in the frost formation suppression ventilation operation.
  • the preset temperature is a temperature at which frost formation on the total heat exchanger 50 can be suppressed, and is 0° C., for example.
  • the control device 90 controls the opening degree of the first expansion device 14 so that the refrigerant temperature measured by the first refrigerant temperature sensor 93 is equal to or higher than a preset temperature.
  • the preset temperature is a temperature at which frost formation on the second heat exchanger 16 can be suppressed, and is 0° C., for example.
  • the control device 90 may control the degree of opening of the first expansion device 14 so that the degree of dryness that can suppress excessive liquid return to the compressor 10, for example, 0.9 or more.
  • the air flow in the air supply passage 51 during the frost formation suppression ventilation operation of the present embodiment is the same as the air flow in the air supply passage 51 during the frost formation suppression ventilation operation of the first embodiment.
  • the air flow in the exhaust passage 53 will be explained.
  • the total heat exchanger 50 exchanges heat between low-temperature, low-humidity air (for example, temperature of 0° C. and absolute humidity of 0 to 5 g/kg) flowing through the air supply path 51 and high-temperature, high-humidity air flowing through the exhaust path 53 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air that has passed through the total heat exchanger 50 and the low-temperature (for example, ⁇ 50° C. to 10° C.) refrigerant.
  • the low-temperature and low-humidity air (for example, temperature of 0° C. and absolute humidity of 0 to 5 g/kg) cooled by the second heat exchanger 16 is pressurized by the exhaust fan 54 and discharged to the outdoor space 301 .
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the first heat exchanger 12 via the connecting pipe 11 .
  • the first heat exchanger 12 exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 from the outdoor space 301 and high-temperature, high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the first heat exchanger 12 flows into the first throttle device 14 .
  • the first throttling device 14 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the first expansion device 14 flows into the second heat exchanger 16 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature, low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the second heat exchanger 16 is again sucked into the compressor 10 via the connecting pipe 13 .
  • FIG. 11 is a diagram showing the heat recovery efficiency of the ventilator 1A according to the second embodiment.
  • FIG. 11 shows the operation of the air supply fan 52 and the exhaust fan 54 and the heat recovery efficiency of each of sensible heat and latent heat. Further, in FIG. 11, the fan operation and heat recovery efficiency in the comparative example are indicated by broken lines, and the fan operation and heat recovery efficiency in the present embodiment are indicated by solid lines.
  • the ventilation system of the comparative example is configured such that the air supply fan and the exhaust fan are stopped when the frost formation condition of the total heat exchanger is satisfied.
  • the heat recovery efficiency ⁇ se of sensible heat and the heat recovery efficiency ⁇ la of latent heat were calculated using the following formulas.
  • Q sensible heat_second heat exchanger is the amount of heat exchanged in the second heat exchanger 16 .
  • ⁇ se (Q sensible heat_total heat exchanger + Q sensible heat_second heat exchanger )/Q sensible heat_maximum amount of heat
  • ⁇ la Q latent heat_total heat exchanger /Q latent heat_maximum amount of heat
  • the ventilator 1A of the present embodiment by arranging the second heat exchanger 16 in the exhaust path 53 of the ventilation unit 200A, when the outside air temperature, which is the frost formation condition, is 0° C. or less, Also, sensible heat can be recovered from the exhaust air in the indoor space 303 with higher efficiency than in the first embodiment. Heat is recovered from the exhaust gas to the refrigerant by flowing a refrigerant having a lower temperature than the exhaust gas that has passed through the total heat exchanger 50 through the second heat exchanger 16, and the heat is transferred to the supply air passing through the first heat exchanger 12. This is because it can be reused for heating. This makes it possible to maintain the ventilation volume of the ventilator 1A and reduce the energy loss. In addition, there is no need to install a separate humidifier or the like in order to suppress the temperature drop in the indoor space 303 due to ventilation, and additional energy consumption can be suppressed.
  • FIG. 12 is a schematic configuration diagram of a ventilator 1B according to Embodiment 3. As shown in FIG. In addition, in the ventilator 1B of FIG. 12, the same components as those of the ventilator 1A of the second embodiment are assigned the same reference numerals, and the description thereof is omitted.
  • a ventilator 1B of the present embodiment differs from the ventilator 1A of the second embodiment in the configuration of an outdoor unit 100B and a ventilation unit 200B.
  • An outdoor unit 100 ⁇ /b>B of the present embodiment includes a compressor 10 , a control device 90 and a channel switching valve 19 .
  • the ventilation unit 200B of the present embodiment has the same components as those of the second embodiment, in addition to the third heat exchanger 17, the second expansion device 18, the second supply air temperature sensor 94, the second refrigerant A temperature sensor 95 and an indoor temperature sensor 96 are provided.
  • the ventilation system 1 ⁇ /b>B of the present embodiment can supply air having a temperature equivalent to that of the indoor space 303 .
  • the third heat exchanger 17 is, for example, a fin-tube heat exchanger.
  • the third heat exchanger 17 exchanges heat between the air supplied from the air supply fan 52 and the refrigerant.
  • the third heat exchanger 17 has one end connected to the connecting pipe 11 and the other end connected to the second expansion device 18 .
  • the third heat exchanger 17 functions as a condenser during heating ventilation operation and frost formation suppression ventilation operation, which will be described later, and functions as an evaporator during cooling ventilation operation.
  • the third heat exchanger 17 may be a corrugated heat exchanger or the like.
  • the second throttle device 18 is, for example, an electronic expansion valve whose opening is variably controlled.
  • the second expansion device 18 decompresses and expands the refrigerant.
  • the second expansion device 18 has one end connected to the third heat exchanger 17 and the other end connected to a pipe connecting the first expansion device 14 and the second heat exchanger 16 .
  • the second expansion device 18 may be a capillary tube or an electromagnetic valve.
  • the channel switching valve 19 is, for example, a four-way valve.
  • the flow path switching valve 19 switches between a refrigerant flow path in the heating/ventilation operation and the frost formation suppression ventilation operation, which will be described later, and a refrigerant flow path in the cooling/ventilation operation.
  • the heat exchanger acting as a condenser is switched.
  • the flow path switching valve 19 is connected to the discharge side of the compressor 10 , the connecting pipes 11 and 13 , and the suction side of the compressor 10 .
  • the flow path switching valve 19 is arranged so that the discharge side of the compressor 10 and the connecting pipe 11 communicate with each other and the connecting pipe 13 communicates with the suction side of the compressor 10 during the heating ventilation operation and the frost formation suppression ventilation operation. Switch the coolant flow path.
  • the third heat exchanger 17 functions as a condenser
  • the second heat exchanger 16 functions as an evaporator.
  • the first heat exchanger 12 and the third heat exchanger 17 function as condensers
  • the second heat exchanger 16 functions as an evaporator.
  • the flow path switching valve 19 changes the flow path of the refrigerant so that the discharge side of the compressor 10 and the connecting pipe 13 communicate with each other and the connecting pipe 11 communicates with the suction side of the compressor 10 during the cooling and ventilation operation. switch.
  • the second heat exchanger 16 functions as a condenser
  • the third heat exchanger 17 functions as an evaporator during cooling and ventilation operation.
  • the channel switching valve 19 may be a combination of a three-way valve and a two-way valve.
  • FIG. 13 is a perspective view of a ventilation unit 200B according to Embodiment 3.
  • the air supply path 51 of the ventilation unit 200B includes a first heat exchanger 12, a total heat exchanger 50, a third heat exchanger 17, and an air supply fan 52. placed.
  • a total heat exchanger 50, a second heat exchanger 16, and an exhaust fan 54 are arranged in the exhaust path 53 of the ventilation unit 200B.
  • the first expansion device 14 is arranged in the exhaust passage 53 and the second expansion device 18 is arranged in the air supply passage 51.
  • the present invention is not limited to this. It may be located in the exhaust path 53 or elsewhere.
  • the third heat exchanger 17 is arranged between the total heat exchanger 50 and the air supply fan 52 in the air supply path 51 .
  • the third heat exchanger 17 is arranged downstream of the total heat exchanger 50 in the flow of supply air in the supply air path 51 .
  • the third heat exchanger 17 heats the supply air that has passed through the total heat exchanger 50 during the heating ventilation operation and the frost formation suppression ventilation operation, and heats the supply air that has passed through the total heat exchanger 50 during the cooling ventilation operation. Cooling.
  • the control device 90 of the present embodiment includes a first supply air temperature sensor 91, an outside air temperature sensor 92, a first refrigerant temperature sensor 93, a second supply air temperature sensor 94, a second refrigerant temperature sensor 95, an indoor temperature sensor 96 and It is communicably connected to a plurality of various sensors (not shown) and an input device such as a remote controller (not shown).
  • the second supply air temperature sensor 94 is, for example, a thermistor.
  • the second supply air temperature sensor 94 is arranged between the third heat exchanger 17 and the supply air fan 52 in the supply air path 51 of the ventilation unit 200B.
  • a second supply air temperature sensor 94 measures the temperature of the air that passes through the third heat exchanger 17 and is supplied to the indoor space 303 .
  • the second coolant temperature sensor 95 is, for example, a thermistor.
  • the second refrigerant temperature sensor 95 is arranged in the pipe connecting the third heat exchanger 17 and the second expansion device 18, and measures the temperature of the refrigerant flowing into the third heat exchanger 17 during the cooling/ventilating operation.
  • the indoor temperature sensor 96 is, for example, a thermistor.
  • the indoor temperature sensor 96 is arranged at the entrance of the exhaust path 53 of the ventilation unit 200B and measures the indoor temperature, which is the temperature of the air in the indoor space 303 .
  • the control device 90 controls the compressor 10, the flow path switching valve 19, the first throttle device 14, the second It controls the throttling device 18 , the air supply fan 52 and the exhaust fan 54 .
  • FIG. 14 is a flow chart showing the operation of the ventilator 1B according to the third embodiment. The operation of the ventilator 1B is started by operating a remote controller or the like.
  • the outdoor temperature sensor 92 and the indoor temperature sensor 96 measure the outdoor temperature of the outdoor space 301 and the indoor temperature of the indoor space 303 (S11). Then, it is determined whether or not the outside air temperature is equal to or higher than the room temperature (S12). If the outside air temperature is equal to or higher than the indoor temperature (S12: YES), the cooling/ventilating operation is performed (S13). On the other hand, if the outdoor temperature is lower than the indoor temperature (S12: NO), it is determined whether the outdoor temperature is higher than the threshold (S14).
  • the threshold is the temperature at which frost formation occurs in the total heat exchanger 50, and is 0° C., for example.
  • the heating ventilation operation is executed (S15).
  • the frost formation suppression ventilation operation is executed (S16). Then, it is determined whether or not to end the operation of the ventilator 1B (S17). If the operation of the ventilator 1B is not to be ended (S17: NO), the process returns to step S11 and the subsequent processes are repeated.
  • the cooling ventilation operation is executed.
  • the heating ventilation operation or the frost formation suppression ventilation operation is executed according to the outdoor temperature. For each run, the air and refrigerant flows are described below.
  • FIG. 15 is a diagram for explaining the flow of air and refrigerant during heating ventilation operation of the ventilation device 1B according to the third embodiment.
  • the flow of supply air is indicated by dashed arrows
  • the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54. Further, the control device 90 switches the flow path switching valve 19 so that the discharge side of the compressor 10 and the connection pipe 11 are communicated, and the connection pipe 13 and the suction side of the compressor 10 are communicated.
  • the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the second supply air temperature sensor 94 becomes the same temperature as the room temperature (for example, 20 to 30° C.). Controller 90 closes first throttle device 14 to block the flow of refrigerant to first heat exchanger 12 .
  • control device 90 controls the second expansion device 18 so that the refrigerant temperature measured by the first refrigerant temperature sensor 93 becomes a temperature that can suppress frost formation on the second heat exchanger 16, for example, 0° C. or higher. to control the opening of the Alternatively, the control device 90 may control the opening degree of the second expansion device 18 so that the degree of dryness that can suppress excessive liquid return to the compressor 10, for example, 0.9 or more.
  • Low-temperature and low-humidity air taken from the outdoor space 301 into the air supply path 51 passes through the first heat exchanger 12 and passes through the total heat exchanger. Flow into 50.
  • the total heat exchanger 50 exchanges heat between low-temperature, low-humidity air flowing through the air supply path 51 and high-temperature, high-humidity (for example, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg) air flowing through the exhaust path 53. do.
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air flowing out of the total heat exchanger 50 and the high-temperature (for example, 0 to 50° C.) refrigerant.
  • the high-temperature and medium-humidity air eg, temperature 20 to 30° C., absolute humidity 5 to 10 g/kg
  • the air is supplied to the indoor space 303 via the air supply duct 401 .
  • the air flow in the exhaust path 53 during the heating and ventilation operation of the present embodiment is the same as the air flow in the exhaust path 53 during the frost formation suppression ventilation operation of the second embodiment.
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the third heat exchanger 17 via the flow path switching valve 19 and the connecting pipe 11 .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the third heat exchanger 17 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the second expansion device 18 flows into the second heat exchanger 16 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the second heat exchanger 16 is sucked into the compressor 10 again via the connecting pipe 13 and the flow path switching valve 19 .
  • FIG. 16 is a diagram for explaining the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator 1B according to Embodiment 3.
  • FIG. 16 the flow of supply air is indicated by dashed arrows, and the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54. Further, the control device 90 switches the flow path switching valve 19 so that the discharge side of the compressor 10 and the connection pipe 11 are communicated, and the connection pipe 13 and the suction side of the compressor 10 are communicated.
  • the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the second supply air temperature sensor 94 becomes the same temperature as the indoor space 303 (for example, 20 to 30° C.).
  • the control device 90 controls the opening of the first expansion device 14 so that the measured value of the first supply air temperature sensor 91 becomes a temperature at which frost formation in the total heat exchanger 50 can be suppressed, for example, 0° C. or higher.
  • control device 90 opens the second expansion device 18 so that the measured value of the first refrigerant temperature sensor 93 becomes a temperature that can suppress frost formation in the second heat exchanger 16, for example, 0° C. or higher. control the degree.
  • control device 90 may control the opening degree of the second expansion device 18 so that the degree of dryness that can suppress excessive liquid return to the compressor 10, for example, 0.9 or more.
  • Low-temperature and low-humidity air (for example, a temperature of 0° C. or less and an absolute humidity of 0 to 5 g/kg) taken into the air supply passage 51 from the outdoor space 301 flows into the first heat exchanger 12 .
  • the first heat exchanger 12 exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 from the outdoor space 301 and high-temperature (for example, 0 to 50° C.) refrigerant.
  • the medium temperature and low humidity air heated by the first heat exchanger 12 flows into the total heat exchanger 50 .
  • the medium-temperature and medium-humidity air heated by the first heat exchanger 12 is air at a temperature that can suppress frost formation on the total heat exchanger 50.
  • the temperature is 0° C. and the absolute humidity is 0 to 5 g. /kg of air.
  • the total heat exchanger 50 combines medium-temperature and low-humidity air heated by the first heat exchanger 12 with high-temperature and high-humidity air (eg, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg) flowing through the exhaust path 53. heat exchange.
  • the medium-temperature and medium-humidity (for example, temperature 10 to 15° C., absolute humidity 5 to 10 g/kg) air heated and humidified by the total heat exchanger 50 flows into the third heat exchanger 17 .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air flowing out of the total heat exchanger 50 and the high-temperature (for example, 0 to 50° C.) refrigerant.
  • the high-temperature and medium-humidity air (eg, temperature 20 to 30° C., absolute humidity 5 to 10 g/kg) heated to the same temperature as the indoor space 303 by the third heat exchanger 17 is pressurized by the air supply fan 52, The air is supplied to the indoor space 303 via the air supply duct 401 .
  • the air flow in the exhaust path 53 during the frost formation suppression ventilation operation of the present embodiment is the same as the air flow in the exhaust path 53 during the frost formation suppression ventilation operation of the second embodiment.
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the first heat exchanger 12 and the third heat exchanger 17 via the flow path switching valve 19 and the connecting pipe 11 .
  • the first heat exchanger 12 exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 from the outdoor space 301 and high-temperature, high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the first heat exchanger 12 flows into the first throttle device 14 .
  • the first expansion device 14 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature and high pressure two-phase or liquid refrigerant condensed in the third heat exchanger 17 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the first expansion device 14 and the second expansion device 18 flows into the second heat exchanger 16 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the second heat exchanger 16 is sucked into the compressor 10 again via the connecting pipe 13 and the flow path switching valve 19 .
  • FIG. 17 is a diagram illustrating the flow of air and refrigerant during the cooling ventilation operation of the ventilation device 1B according to the third embodiment.
  • the flow of supply air is indicated by broken line arrows
  • the flow of exhaust air is indicated by dashed line arrows.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54. Further, the control device 90 switches the flow path switching valve 19 so that the discharge side of the compressor 10 and the connection pipe 13 are communicated, and the connection pipe 11 and the suction side of the compressor 10 are communicated.
  • the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the second supply air temperature sensor 94 becomes the same temperature as the indoor space 303 (for example, 20 to 30° C.).
  • the control device 90 also closes the first expansion device 14 to block the flow of refrigerant to the first heat exchanger 12 .
  • control device 90 controls the second refrigerant temperature so that the refrigerant temperature in the third heat exchanger 17 measured by the second refrigerant temperature sensor 95 is lower than the temperature of the indoor space 303 (for example, 20° C. or lower).
  • the opening degree of the diaphragm device 18 is controlled.
  • High-temperature and high-humidity (for example, temperature of 35° C. or higher, absolute humidity of 15 to 20 g/kg) air taken from the outdoor space 301 into the air supply path 51 passes through the first heat exchanger 12 and passes through the total heat exchanger 50.
  • flow into The total heat exchanger 50 exchanges heat between high-temperature, high-humidity air flowing through the air supply path 51 and low-temperature, low-humidity air flowing through the exhaust path 53 (for example, temperature 20 to 30° C., absolute humidity 5 to 10 g/kg). .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air flowing out of the total heat exchanger 50 and the low-temperature (for example, 0 to 10° C.) refrigerant.
  • the low-temperature and low-humidity air (for example, temperature 25 to 30° C., absolute humidity 5 to 10 g/kg) that has been cooled and dehumidified to the same temperature as the indoor space 303 by the third heat exchanger 17 is boosted by the air supply fan 52. , is supplied to the interior space 303 via the air supply duct 401 .
  • Low-temperature and low-humidity for example, temperature of 25 to 30° C., absolute humidity of 5 to 10 g/kg
  • air taken into the exhaust passage 53 from the indoor space 303 through the exhaust duct 402 flows into the total heat exchanger 50 .
  • the total heat exchanger 50 exchanges heat between high-temperature, high-humidity air flowing through the air supply passage 51 and low-temperature, low-humidity air flowing through the exhaust passage 53 .
  • the medium-temperature and medium-humidity for example, temperature 30 to 35° C., absolute humidity 10 to 15 g/kg
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air flowing out of the total heat exchanger 50 and the high-temperature (for example, 40 to 50° C.) refrigerant.
  • the high-temperature and medium-humidity air (for example, temperature 40-50° C., absolute humidity 10-15 g/kg) heated by the second heat exchanger 16 is pressurized by the exhaust fan 54 and discharged to the outdoor space 301 .
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the second heat exchanger 16 via the flow path switching valve 19 and the connecting pipe 13 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the second heat exchanger 16 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the second expansion device 18 flows into the third heat exchanger 17 .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the third heat exchanger 17 is sucked into the compressor 10 again via the connecting pipe 11 and the flow path switching valve 19 .
  • FIG. 18 is a diagram showing the heat recovery efficiency of the ventilator 1B according to Embodiment 3.
  • FIG. FIG. 18 shows the operation of the air supply fan 52 and the exhaust fan 54 and the heat recovery efficiency of each of sensible heat and latent heat. Further, in FIG. 18, the fan operation and heat recovery efficiency in the comparative example are indicated by dashed lines, and the fan operation and heat recovery efficiency in the present embodiment are indicated by solid lines.
  • the ventilation system of the comparative example is configured such that the air supply fan and the exhaust fan are stopped when the frost formation condition of the total heat exchanger is satisfied.
  • the third heat exchanger 17 functions as an evaporator or a condenser. Also in the case of the operation of , it is possible to supply air having a temperature equivalent to that of the indoor space 303 . As a result, deterioration of indoor comfort such as a decrease in room temperature of the indoor space 303 due to ventilation can be suppressed.
  • the ventilator 1B of the present embodiment by arranging the second heat exchanger 16 in the exhaust path 53 of the ventilation unit 200B, the exhaust of the indoor space 303 is sensible heat can be recovered with high efficiency.
  • the refrigerant having a higher or lower temperature than the exhaust gas that has passed through the total heat exchanger 50 is caused to flow through the second heat exchanger 16, thereby recovering cold or hot heat from the exhaust gas to the third heat exchanger 17.
  • This is because it can be reused for cooling or heating to the supply air in.
  • This makes it possible to maintain the ventilation volume of the ventilator 1B and reduce the energy loss.
  • the first heat exchanger 12 and the third heat exchanger 17 are made to function as condensers, so that the air is discharged from the indoor space 303 to the outdoor space 301. It is possible to recover sensible heat from exhaust gas with high efficiency. This is because the heat recovered from the exhaust gas to the refrigerant can be reused for heating the supply air in the first heat exchanger 12 and the third heat exchanger 17 . As a result, it is possible to reduce the energy loss due to exhaust to the outdoor space 301 accompanying ventilation.
  • FIG. 19 is a schematic configuration diagram of a ventilator 1C according to Embodiment 4. As shown in FIG. In addition, in the ventilator 1C of FIG. 19, the same components as those of the ventilator 1B of Embodiment 3 are given the same reference numerals, and the description thereof is omitted.
  • a ventilator 1C of the present embodiment differs from the ventilator 1B of the third embodiment in the configuration of an outdoor unit 100C.
  • the outdoor unit 100C of the present embodiment includes a compressor 10, an outdoor heat exchanger 15, a control device 90, a flow path switching valve 19, a third expansion device 20, and an outdoor fan 30.
  • a ventilation unit 200B of this embodiment is the same as that of the third embodiment.
  • 1 C of ventilators of this Embodiment can supply the indoor space 303 and the same temperature supply air similarly to Embodiment 3.
  • the third throttle device 20 is, for example, an electronic expansion valve whose opening is variably controlled.
  • the third expansion device 20 decompresses and expands the refrigerant.
  • the third expansion device 20 has one end connected to the connection pipe 13 and the other end connected to the outdoor heat exchanger 15 .
  • the third expansion device 20 may be a capillary tube or an electromagnetic valve.
  • the control device 90 of the present embodiment includes a first supply air temperature sensor 91, an outside air temperature sensor 92, a first refrigerant temperature sensor 93, a second supply air temperature sensor 94, an indoor temperature sensor 96 and a plurality of various sensors (not shown), It is also communicably connected to an input device such as a remote controller (not shown).
  • the control device 90 controls the compressor 10, the flow path switching valve 19, the first throttle device 14, The second throttle device 18, the third throttle device 20, the air supply fan 52, the exhaust fan 54, and the outdoor fan 30 are controlled.
  • the operation of the ventilator 1C will be described.
  • the ventilation system 1C performs a heating ventilation operation, a frost formation suppression ventilation operation, and a cooling ventilation operation.
  • a flow chart of the operation of the ventilator 1C is the same as in FIG. That is, in the ventilator 1C, when the outside air temperature is equal to or higher than the indoor temperature, the cooling/ventilating operation is performed. Further, when the outdoor temperature is lower than the indoor temperature, the heating ventilation operation or the frost formation suppression ventilation operation is executed according to the outdoor temperature. For each run, the air and refrigerant flows are described below.
  • FIG. 20 is a diagram illustrating the flow of air and refrigerant during the heating ventilation operation of the ventilator 1C according to the fourth embodiment.
  • the flow of supply air is indicated by dashed arrows
  • the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the control device 90 drives the compressor 10, the air supply fan 52, and the exhaust fan 54.
  • the control device 90 controls the operating frequency of the compressor 10, the flow path of the flow path switching valve 19, and the opening degree of the first expansion device 14 in the same manner as during the heating and ventilation operation of the third embodiment. Further, the control device 90 controls the second expansion device 18, the third expansion device 20 and the outdoor fan 30 depending on whether it is desired to maximize the heat recovery from the exhaust gas or when it is desired to avoid frost formation in the second heat exchanger 16. Toggle control of
  • the controller 90 controls the temperature measured by the first coolant temperature sensor 93 to be lower than the ambient temperature measured by the ambient temperature sensor 92, such as -10°C to 0°C.
  • the opening degrees of the second diaphragm device 18 and the third diaphragm device 20 are controlled so that Also, in this case, the controller 90 stops the outdoor fan 30 .
  • the controller 90 sets the measured value of the first refrigerant temperature sensor 93 to a temperature at which frost formation on the second heat exchanger 16 can be suppressed, for example, 0°C.
  • the opening degrees of the second diaphragm device 18 and the third diaphragm device 20 are controlled as described above. Further, in this case, the control device 90 operates the outdoor fan 30 when the amount of heat absorbed by the second heat exchanger 16 is less than the amount of heat generated by the first heat exchanger 12 and the third heat exchanger 17. .
  • the controller 90 stops the outdoor fan 30 when the amount of heat absorbed by the second heat exchanger 16 is greater than the amount of heat generated by the first heat exchanger 12 and the third heat exchanger 17 . That is, the control device 90 performs heat exchange in the outdoor heat exchanger 15 according to the balance between the amount of heat to be heated and the amount of heat to be absorbed in the first heat exchanger 12, the second heat exchanger 16, and the third heat exchanger 17. It controls the driving and stopping of the outdoor fan 30 as shown in FIG. Note that the rotation speed of the outdoor fan 30 may be controlled according to the balance between the heating amount and the heat absorption amount in the first heat exchanger 12 , the second heat exchanger 16 , and the third heat exchanger 17 . The control device 90 performs the same control as when frost formation on the second heat exchanger 16 is to be avoided even when frost formation occurs on the second heat exchanger 16 .
  • the air flow in the air supply path 51 and the exhaust path 53 during the heating and ventilation operation of the present embodiment is the same as the air flow in the air supply path 51 and the exhaust path 53 during the heating and ventilation operation of the third embodiment. .
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the third heat exchanger 17 via the flow path switching valve 19 and the connecting pipe 11 .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the third heat exchanger 17 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the second expansion device 18 flows into the second heat exchanger 16 .
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature and low-pressure two-phase or gas refrigerant evaporated in the second heat exchanger 16 is sucked into the compressor 10 again via the connecting pipe 13, the third expansion device 20, the outdoor heat exchanger 15, and the flow path switching valve 19. be done.
  • the outdoor heat exchanger 15 exchanges heat between the refrigerant and the outdoor air depending on the situation.
  • FIG. 21 is a diagram illustrating the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator 1C according to the fourth embodiment.
  • the flow of supply air is indicated by dashed line arrows
  • the flow of exhaust air is indicated by dashed line arrows.
  • the control device 90 drives the compressor 10, the air supply fan 52 and the exhaust fan 54.
  • the control device 90 controls the operating frequency of the compressor 10, the flow path of the flow path switching valve 19, and the opening degree of the first throttle device 14 in the same manner as during the frost formation suppression ventilation operation of the third embodiment.
  • the control device 90 controls the second expansion device 18, the third expansion device 20, and the outdoor fan 30 depending on whether it is desired to maximize heat recovery from the exhaust gas or to avoid frost formation in the second heat exchanger 16. switch.
  • the specific control in this case is the same as the control during heating/ventilation operation.
  • the air flow in the air supply path 51 and the air exhaust path 53 during the frost formation suppression ventilation operation of the present embodiment is similar to the air flow in the air supply path 51 and the air exhaust path 53 during the frost formation suppression ventilation operation of the third embodiment. is the same as
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the first heat exchanger 12 and the third heat exchanger 17 via the flow path switching valve 19 and the connecting pipe 11 .
  • the first heat exchanger 12 exchanges heat between low-temperature, low-humidity air taken into the air supply passage 51 from the outdoor space 301 and high-temperature, high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the first heat exchanger 12 flows into the first throttle device 14 .
  • the first expansion device 14 decompresses the low-temperature and high-pressure liquid refrigerant.
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the third heat exchanger 17 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature and low-pressure two-phase or gas refrigerant evaporated in the second heat exchanger 16 is sucked into the compressor 10 again via the connecting pipe 13, the third expansion device 20, the outdoor heat exchanger 15, and the flow path switching valve 19. be done.
  • the outdoor heat exchanger 15 exchanges heat between the refrigerant and the outdoor air depending on the situation.
  • FIG. 22 is a diagram for explaining the flow of air and refrigerant during the cooling ventilation operation of the ventilator 1C according to the fourth embodiment.
  • the flow of supply air is indicated by dashed arrows
  • the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the control device 90 drives the compressor 10, the air supply fan 52 and the exhaust fan 54.
  • the control device 90 controls the operating frequency of the compressor 10, the flow path of the flow path switching valve 19, and the opening degrees of the first expansion device 14 and the second expansion device 18 in the same manner as in the cooling/ventilation operation of the third embodiment. do.
  • the control device 90 operates the outdoor fan 30 when the amount of heat released by the second heat exchanger 16 is less than the amount of heat absorbed by the first heat exchanger 12 and the third heat exchanger 17 .
  • the controller 90 stops the outdoor fan 30 when the amount of heat released by the second heat exchanger 16 is greater than the amount of heat absorbed by the first heat exchanger 12 and the third heat exchanger 17 .
  • the air flow in the air supply path 51 and the air exhaust path 53 during the cooling/ventilating operation of the present embodiment is the same as the air flow in the air supply path 51 and the air exhaust path 53 during the cooling/ventilating operation of the third embodiment. .
  • the compressor 10 sucks a low-temperature, low-pressure gas refrigerant, compresses it, and discharges a high-temperature, high-pressure gas refrigerant.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 10 flows into the second heat exchanger 16 via the flow path switching valve 19 , the outdoor heat exchanger 15 , the third expansion device 20 and the connecting pipe 13 .
  • the outdoor heat exchanger 15 exchanges heat between the refrigerant and the outdoor air depending on the situation.
  • the second heat exchanger 16 exchanges heat between the medium-temperature and medium-humidity air heated and humidified by the total heat exchanger 50 and the high-temperature and high-pressure gas refrigerant.
  • the low temperature, high pressure two-phase or liquid refrigerant condensed in the second heat exchanger 16 flows into the second throttle device 18 .
  • the second throttling device 18 reduces the pressure of the low temperature, high pressure two-phase or liquid refrigerant.
  • the low-temperature, low-pressure two-phase refrigerant decompressed by the second expansion device 18 flows into the third heat exchanger 17 .
  • the third heat exchanger 17 exchanges heat between the medium-temperature and medium-humidity air cooled and dehumidified by the total heat exchanger 50 and the low-temperature and low-pressure two-phase refrigerant.
  • the low-temperature, low-pressure two-phase or gaseous refrigerant evaporated in the third heat exchanger 17 is sucked into the compressor 10 again via the connection pipe 11 and the flow path switching valve 19 .
  • FIG. 23 is a diagram showing the heat recovery efficiency of the ventilator 1C according to the fourth embodiment.
  • FIG. 23 shows the operation of the air supply fan 52 and the exhaust fan 54 and the heat recovery efficiency of each of sensible heat and latent heat. Further, in FIG. 23 , the fan operation and heat recovery efficiency in the comparative example are indicated by dashed lines, and the fan operation and heat recovery efficiency in the present embodiment are indicated by solid lines.
  • the ventilation system of the comparative example is configured such that the air supply fan and the exhaust fan are stopped when the frost formation condition of the total heat exchanger is satisfied.
  • the outdoor unit 100C is provided with the outdoor heat exchanger 15, and the heat balance among the first heat exchanger 12, the second heat exchanger 16 and the third heat exchanger 17 is balanced.
  • the outdoor fan 30 By controlling the operation of the outdoor fan 30, excessive heating or cooling of the supplied air, or insufficient heating or cooling, can be suppressed when there is no such fan. As a result, it is possible to suppress deterioration of indoor comfort, such as fluctuations in the room temperature of the indoor space 303 due to ventilation.
  • the outdoor heat exchanger 15 functions as an evaporator in the heating and ventilation operation, so that sensible heat is efficiently extracted from the exhaust air in the indoor space 303. can be recovered. This is because the temperature of the refrigerant flowing through the second heat exchanger 16 can be made below the temperature at which frost formation occurs in the second heat exchanger 16 . Even if frost formation occurs in the second heat exchanger 16, by temporarily using the outdoor heat exchanger 15, the amount of heat recovered from the exhaust gas by the second heat exchanger 16 is maintained at the same level. Defrosting can be performed by increasing the temperature of the refrigerant flowing through the second heat exchanger 16 . As a result, it is possible to further reduce the energy loss due to exhaust to the outdoor space 301 accompanying ventilation.
  • FIG. 24 is a schematic configuration diagram of a ventilator 1D according to Embodiment 5. As shown in FIG. In the ventilator 1D of FIG. 24, the same components as those of the ventilator 1 of FIG.
  • a ventilator 1D of the present embodiment differs from the ventilator 1 of the first embodiment in the configuration of a ventilation unit 200C.
  • a ventilation unit 200 ⁇ /b>C of the present embodiment includes an air path switching device 55 in addition to the same components as those of the first embodiment.
  • the outdoor unit 100 of this embodiment is the same as that of the first embodiment.
  • the ventilator 1D of the present embodiment is capable of suppressing frost formation in the total heat exchanger 50 even when the outside air temperature is 0° C. or less, which is the frost formation condition.
  • the configuration of the refrigerant circuit of the ventilator 1D is the same as the configuration of the refrigerant circuit of the ventilator 1 of the first embodiment.
  • FIG. 25 is a perspective view of a ventilation unit 200C according to Embodiment 5.
  • FIG. 25 As shown in FIGS. 24 and 25, an air path switching device 55, a first heat exchanger 12, a total heat exchanger 50, and an air supply fan 52 are arranged in the air supply path 51 of the ventilation unit 200C. be.
  • a total heat exchanger 50 and an exhaust fan 54 are arranged in the exhaust path 53 of the ventilation unit 200C.
  • FIG. 26 is a diagram illustrating the first state of the air passage switching device 55 according to the fifth embodiment.
  • FIG. 27 is a diagram illustrating the second state of the air path switching device 55 according to the fifth embodiment.
  • FIG. 28 is a diagram for explaining the third state of the air passage switching device 55 according to the fifth embodiment.
  • the air path switching device 55 includes a partition portion 551 and a movable portion 552 that is moved by a motor (not shown).
  • the partition part 551 divides the air passage between the inlet of the air supply passage 51 and the inlet of the total heat exchanger 50 into the first air passage in which the first heat exchanger 12 is not arranged and the first air passage in which the first heat exchanger 12 is arranged. It is provided so as to be separated from the arranged second air passage.
  • the second air passage in which the first heat exchanger 12 is arranged is blocked by the movable portion 552 of the air passage switching device 55, so that the air flows through the first air passage. Only the supply air, ie the supply air that does not pass through the first heat exchanger 12 , enters the total heat exchanger 50 .
  • the first air duct in which the first heat exchanger 12 is not arranged is closed by the movable portion 552 of the air duct switching device 55, so that the second air duct , that is, only the supply air that has passed through the first heat exchanger 12 flows into the total heat exchanger 50 .
  • FIG. 26 in the first state, the second air duct in which the first heat exchanger 12 is not arranged is blocked by the movable portion 552 of the air passage switching device 55, so that the second air duct , that is, only the supply air that has passed through the first heat exchanger 12 flows into the total heat exchanger 50 .
  • both the first air passage in which the first heat exchanger 12 is not arranged and the second air passage in which the first heat exchanger 12 is arranged are opened.
  • the supply air that has passed through the first heat exchanger 12 and the supply air that has not passed through the first heat exchanger 12 flow into the total heat exchanger 50 .
  • the control device 90 of the present embodiment is communicably connected to a first supply air temperature sensor 91, an outside air temperature sensor 92, a plurality of various sensors (not shown), and an input device such as a remote controller (not shown).
  • the control device 90 controls the compressor 10, the outdoor fan 30, the first expansion device 14, and the air supply fan 52 based on information measured by each temperature sensor and other various sensors and instructions from an input device such as a remote controller. , the exhaust fan 54 and the air path switching device 55 are controlled.
  • the operation of the ventilator 1D will be described.
  • the ventilation system 1D of the present embodiment performs a normal ventilation operation and a frost formation suppression ventilation operation.
  • a flow chart of the operation of the ventilator 1D is the same as in FIG. That is, when the outside air temperature measured by the outside air temperature sensor 92 is higher than the temperature at which frost formation occurs in the total heat exchanger 50, the control device 90 executes the normal ventilation operation. Further, when the outside air temperature measured by the outside air temperature sensor 92 is equal to or lower than the temperature at which frost formation occurs in the total heat exchanger 50, the control device 90 executes the frost formation suppression ventilation operation. For each run, the air and refrigerant flows are described below.
  • FIG. 29 is a diagram for explaining the flow of air and refrigerant during the normal ventilation operation of the ventilator 1D according to Embodiment 5.
  • FIG. 29 the flow of supply air is indicated by dashed arrows, and the flow of exhaust gas is indicated by dashed-dotted arrows.
  • the normal ventilation operation when the temperature of the outdoor space 301 is lower than the temperature of the indoor space 303 will be described.
  • control device 90 stops the compressor 10 and the outdoor fan 30 and drives the air supply fan 52 and the exhaust fan 54 . Further, the control device 90 switches the air path switching device 55 to the first state so that the supply air flows through the first air path that does not pass through the first heat exchanger 12 .
  • Low-temperature and low-humidity air for example, temperature of 0 to 5° C., absolute humidity of 0 to 5 g/kg
  • the total heat exchanger 50 exchanges heat between low-temperature, low-humidity air flowing through the air supply path 51 and high-temperature, high-humidity (for example, temperature 20 to 30° C., absolute humidity 5 to 15 g/kg) air flowing through the exhaust path 53. do.
  • Medium-temperature and medium-humidity (for example, temperature 10 to 15° C., absolute humidity 5 to 10 g/kg) air heated and humidified by the total heat exchanger 50 is pressurized by the air supply fan 52 and passed through the air supply duct 401. , is supplied to the indoor space 303 .
  • the flow of air in the exhaust passage 53 and the flow of refrigerant in the refrigerant circuit during normal ventilation operation in this embodiment are the same as in the first embodiment.
  • FIG. 30 is a diagram for explaining the flow of air and refrigerant during the frost formation suppression ventilation operation of the ventilator 1D according to Embodiment 5.
  • FIG. 31 is a perspective view of the ventilation unit 200C according to Embodiment 5 during frost formation suppression ventilation operation.
  • the control device 90 drives the compressor 10, the outdoor fan 30, the air supply fan 52 and the exhaust fan 54.
  • the control device 90 controls the operating frequency of the compressor 10 and the opening degree of the first expansion device 14 in the same manner as during the frost formation suppression ventilation operation of the first embodiment.
  • the control device 90 shifts to the second state or the third state so that the measured value of the first supply air temperature sensor 91 becomes a temperature that can suppress frost formation in the total heat exchanger 50, for example, 0° C. or higher.
  • the air path switching device 55 is controlled to switch.
  • the control device 90 switches the air path switching device 55 so that all the supply air passes through the first heat exchanger 12. Switch to 2 states. Further, when the measured value of the first supply air temperature sensor 91 approaches 0° C., the control device 90 switches the air path switching device 55 to the third state.
  • the air flow in the air supply path 51 and the air exhaust path 53 during the frost formation suppression ventilation operation of the present embodiment and the refrigerant flow in the refrigerant circuit are the same as those in the air supply path 51 during the frost formation suppression ventilation operation of the first embodiment. and the flow of air in the exhaust passage 53 and the flow of refrigerant in the refrigerant circuit.
  • the ventilator 1D of the present embodiment by providing the air path switching device 55, a constant speed compressor or the like can be applied, and the cost of the ventilator can be reduced.
  • the first state in which air does not pass through the first heat exchanger 12 is set during normal ventilation operation.
  • the angle of the movable portion 552 of the air passage switching device 55 may be controlled to control the amount of air passing through the first air passage and the second air passage according to the measurement value of the first supply air temperature sensor 91 .
  • the ventilators 1A to 1C of the second to fourth embodiments may be configured to include the air path switching device 55 of the fifth embodiment.
  • the outdoor air temperature sensor 92 and the indoor temperature sensor 96 are not essential components of the ventilation device 1 and can be omitted.
  • the control device 90 may acquire the outdoor air temperature and the indoor temperature from an outdoor air temperature sensor and an indoor temperature sensor provided separately from the ventilation device 1 .
  • the controller 90 controls the operating frequency of the compressor 10 so that the measured value of the second supply air temperature sensor 94 is equal to the room temperature.
  • the control device 90 controls the operating frequency of the compressor 10 so that the measured value of the second supply air temperature sensor 94 is equal to the preset temperature of the ventilator 1B or 1C. good too.
  • 1, 1A, 1B, 1C, 1D ventilator 10 compressor, 11 connecting pipe, 12 first heat exchanger, 13 connecting pipe, 14 first expansion device, 15 outdoor heat exchanger, 16 second heat exchanger, 17 Third heat exchanger, 18 Second throttle device, 19 Flow path switching valve, 20 Third throttle device, 30 Outdoor fan, 50 Total heat exchanger, 51 Air supply path, 52 Air supply fan, 53 Exhaust path, 54 Exhaust fan, 55 air route switching device, 90 control device, 91 first supply air temperature sensor, 92 outside air temperature sensor, 93 first refrigerant temperature sensor, 94 second supply air temperature sensor, 95 second refrigerant temperature sensor 96 room temperature Sensor, 100, 100A, 100B, 100C Outdoor unit, 200, 200A, 200B, 200C Ventilation unit, 301 Outdoor space, 302 Ceiling space, 303 Indoor space, 401 Air supply duct, 402 Exhaust duct, 551 Partition, 552 Movable Department.

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

Abstract

Un dispositif de ventilation selon la présente invention comprend : un trajet d'échappement à travers lequel s'écoule de l'air d'échappement devant être émis vers l'extérieur ; un trajet d'alimentation en air à travers lequel s'écoule de l'air fourni à l'intérieur ; un ventilateur d'évacuation qui est disposé sur le trajet d'échappement ; un ventilateur d'alimentation en air qui est disposé sur le trajet d'alimentation en air ; un échangeur de chaleur total qui échange de la chaleur entre l'air d'échappement et l'air fourni ; et un circuit de liquide de refroidissement qui inclut un compresseur, un premier échangeur de chaleur, un premier dispositif de restriction et un premier échangeur de chaleur, le premier échangeur de chaleur étant disposé en amont de l'échangeur de chaleur total le long de l'écoulement d'air fourni dans le trajet d'alimentation en air et chauffant l'air qui s'écoule dans l'échangeur de chaleur total lorsque la température d'air extérieur est inférieure ou égale à une valeur seuil.
PCT/JP2021/019157 2021-05-20 2021-05-20 Dispositif de ventilation WO2022244182A1 (fr)

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PCT/JP2021/019157 WO2022244182A1 (fr) 2021-05-20 2021-05-20 Dispositif de ventilation
JP2023522114A JP7550976B2 (ja) 2021-05-20 2021-05-20 換気装置

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Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6219632A (ja) * 1985-07-18 1987-01-28 Mitsubishi Electric Corp 熱交換形換気装置
JPS63176968A (ja) * 1987-01-14 1988-07-21 ダイキン工業株式会社 空気調和機の低温保護装置
JP2010107059A (ja) * 2008-10-28 2010-05-13 Mitsubishi Electric Corp 冷凍空調装置
JP2013047590A (ja) * 2011-08-29 2013-03-07 Chofu Seisakusho Co Ltd デシカント換気扇
JP2014142100A (ja) * 2013-01-23 2014-08-07 Denso Corp 暖房システム
JP2015143599A (ja) * 2014-01-31 2015-08-06 三菱電機株式会社 冷凍サイクル装置
WO2017037816A1 (fr) * 2015-08-31 2017-03-09 三菱電機株式会社 Dispositif de ventilation
JP2019082308A (ja) * 2017-10-31 2019-05-30 東プレ株式会社 換気装置
EP3572738A2 (fr) * 2018-05-23 2019-11-27 AT-Air Oy Ensemble de traitement de l'air, procédé de fonctionnement d'un ensemble de traitement de l'air et procédé de mise à niveau d'un ensemble de traitement de l'air

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6219632A (ja) * 1985-07-18 1987-01-28 Mitsubishi Electric Corp 熱交換形換気装置
JPS63176968A (ja) * 1987-01-14 1988-07-21 ダイキン工業株式会社 空気調和機の低温保護装置
JP2010107059A (ja) * 2008-10-28 2010-05-13 Mitsubishi Electric Corp 冷凍空調装置
JP2013047590A (ja) * 2011-08-29 2013-03-07 Chofu Seisakusho Co Ltd デシカント換気扇
JP2014142100A (ja) * 2013-01-23 2014-08-07 Denso Corp 暖房システム
JP2015143599A (ja) * 2014-01-31 2015-08-06 三菱電機株式会社 冷凍サイクル装置
WO2017037816A1 (fr) * 2015-08-31 2017-03-09 三菱電機株式会社 Dispositif de ventilation
JP2019082308A (ja) * 2017-10-31 2019-05-30 東プレ株式会社 換気装置
EP3572738A2 (fr) * 2018-05-23 2019-11-27 AT-Air Oy Ensemble de traitement de l'air, procédé de fonctionnement d'un ensemble de traitement de l'air et procédé de mise à niveau d'un ensemble de traitement de l'air

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