WO2024252526A1 - Climatiseur - Google Patents

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Publication number
WO2024252526A1
WO2024252526A1 PCT/JP2023/021033 JP2023021033W WO2024252526A1 WO 2024252526 A1 WO2024252526 A1 WO 2024252526A1 JP 2023021033 W JP2023021033 W JP 2023021033W WO 2024252526 A1 WO2024252526 A1 WO 2024252526A1
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WO
WIPO (PCT)
Prior art keywords
heat exchanger
air
refrigerant
temperature
main
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Pending
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PCT/JP2023/021033
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English (en)
Japanese (ja)
Inventor
尚平 石村
俊光 鎌田
惇 川島
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Priority to PCT/JP2023/021033 priority Critical patent/WO2024252526A1/fr
Publication of WO2024252526A1 publication Critical patent/WO2024252526A1/fr
Anticipated expiration legal-status Critical
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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
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing

Definitions

  • This disclosure relates to an air conditioner with a humidification function.
  • Air conditioners with a humidification function can prevent the air in the room from drying out by operating the humidification function during air conditioning operation.
  • An example of an air conditioner with a humidification function is the air conditioner of Patent Document 1.
  • the air conditioner of Patent Document 1 condenses water vapor contained in the outside air in a sub-outdoor unit installed on the exterior wall near the indoor unit, and uses this water for humidification, providing a waterless humidification function that does not require the supply of moisture from outside.
  • the air conditioner of Patent Document 1 minimizes the length of the duct that transports humidified air, preventing the growth of mold and bacteria.
  • the auxiliary outdoor heat exchanger that produces condensed water used for humidification and the main outdoor heat exchanger built into the main outdoor unit are connected in series in the refrigeration cycle. Therefore, when the dew point temperature of the outside air is below zero degrees Celsius and the refrigerant pressure of the auxiliary outdoor heat exchanger is set so that the surface temperature of the auxiliary outdoor heat exchanger is below zero degrees Celsius to produce condensed water, the refrigerant pressure of the main outdoor heat exchanger downstream will necessarily be lower than that. As a result, the surface temperature of the main outdoor heat exchanger will be below zero degrees Celsius.
  • the present disclosure has been made in consideration of these points, and aims to provide an air conditioner that can maintain indoor comfort by continuing heating operation while producing water to create humidified air under operating conditions where the dew point temperature of the outside air is below freezing.
  • the air conditioning system comprises a refrigerant circuit having a main circuit in which at least a compressor, an indoor heat exchanger, a main expansion valve, and a main outdoor heat exchanger are connected in sequence by refrigerant piping and in which a refrigerant circulates; an auxiliary outdoor heat exchanger connected in parallel to the main outdoor heat exchanger; a humidifier that humidifies air taken in from the outside using condensed water generated in the auxiliary outdoor heat exchanger and discharges the humidified air; and a control device, and the control device has a defrost heating operation mode in which the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger is maintained at a temperature above zero degrees Celsius to melt frost adhering to the auxiliary outdoor heat exchanger and generate condensed water, while at the same time maintaining the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger at a temperature lower than the temperature of the outside air and maintaining the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger at a temperature higher than the
  • the auxiliary outdoor heat exchanger is connected in parallel to the main outdoor heat exchanger, and in the defrost heating operation mode, the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger is maintained at a temperature above zero degrees Celsius to melt the frost adhering to the auxiliary outdoor heat exchanger and generate condensed water, while at the same time maintaining the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger at a temperature lower than the temperature of the outdoor air. Therefore, even under operating conditions where the dew point temperature of the outdoor air is below freezing, the air conditioner can melt the frost formed on the auxiliary outdoor heat exchanger and generate condensed water to make humidified air.
  • the air conditioner maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger at a temperature higher than the indoor air temperature, so that the room can be heated to maintain indoor comfort.
  • the air conditioner can continue heating operation while generating water to make humidified air, thereby maintaining indoor comfort.
  • FIG. 1 is a schematic diagram of a refrigerant circuit of an air-conditioning apparatus according to a first embodiment.
  • 1 is a schematic diagram showing a humidifier of an air conditioning apparatus according to a first embodiment.
  • FIG. 4 is a schematic diagram showing a phase change of a refrigerant in a water-collection heating operation mode of the refrigerant circuit of the air-conditioning apparatus according to the first embodiment.
  • FIG. 4 is a ph diagram showing the changes in refrigerant pressure and enthalpy in the water-collection heating operation mode of the refrigerant circuit of the air-conditioning apparatus according to embodiment 1.
  • FIG. 4 is a schematic diagram showing a phase change of a refrigerant in a modified example of the water-collection heating operation mode of the refrigerant circuit of the air-conditioning apparatus according to Embodiment 1.
  • FIG. A ph diagram showing changes in refrigerant pressure and enthalpy in a modified water-collection heating operation mode of the refrigerant circuit of the air conditioning apparatus of embodiment 1.
  • 3 is a schematic diagram showing a phase change of a refrigerant in a defrost heating operation mode of the refrigerant circuit of the air conditioner according to the first embodiment.
  • FIG. 3 is a ph diagram showing changes in refrigerant pressure and enthalpy in a defrost heating operation mode of the refrigerant circuit of the air conditioning apparatus according to embodiment 1.
  • FIG. 2 is a schematic diagram showing a phase change of a refrigerant in a cooling operation mode of the refrigerant circuit of the air conditioner according to the first embodiment.
  • FIG. 4 is a ph diagram showing changes in refrigerant pressure and enthalpy in a cooling operation mode of the refrigerant circuit of the air conditioning apparatus according to embodiment 1.
  • FIG. FIG. 6 is a schematic diagram of a refrigerant circuit of an air-conditioning apparatus according to a second embodiment.
  • FIG. 11 is a schematic diagram illustrating a humidifier according to a second embodiment.
  • FIG. 11 is a schematic diagram showing a phase change of a refrigerant in a water-collection heating operation mode of a refrigerant circuit of an air-conditioning apparatus according to embodiment 2.
  • FIG. A ph diagram showing changes in refrigerant pressure and enthalpy in the water-collection heating operation mode of the refrigerant circuit of the air conditioning apparatus of embodiment 2.
  • FIG. 11 is a schematic diagram showing a phase change of a refrigerant in a defrost heating operation mode of a refrigerant circuit of an air conditioner according to embodiment 2.
  • FIG. 11 is a schematic diagram showing a phase change of a refrigerant in a cooling operation mode of a refrigerant circuit of an air-conditioning apparatus according to a second embodiment.
  • FIG. 11 is a schematic diagram showing an auxiliary outdoor unit of an air conditioning apparatus according to a third embodiment.
  • Fig. 1 is a schematic diagram of a refrigerant circuit 1 of an air-conditioning apparatus 100 according to the first embodiment.
  • a main outdoor unit 10 In the air-conditioning apparatus 100, a main outdoor unit 10, an indoor unit 20, and an auxiliary outdoor unit 30 are connected via refrigerant piping to form a refrigerant circuit 1.
  • the main outdoor unit 10 has a compressor 14, a four-way valve 15, a main outdoor heat exchanger 11, a main expansion valve 13, a first sub-expansion valve 16, and a second sub-expansion valve 17 on the refrigerant circuit 1.
  • the indoor unit 20 has an indoor heat exchanger 21 on the refrigerant circuit 1.
  • the auxiliary outdoor unit 30 has a sub outdoor heat exchanger 31, a temperature adjustment device 34, a third sub-expansion valve 35, and a pressure reducing mechanism 36 on the refrigerant circuit 1.
  • the refrigerant circuit 1 has a main circuit 2, a first bypass circuit 3, and a second bypass circuit 4.
  • the main circuit 2 is configured by connecting a compressor 14, a four-way valve 15, an indoor heat exchanger 21, a main expansion valve 13, a main outdoor heat exchanger 11, and a first sub-expansion valve 16 in sequence with refrigerant piping.
  • the first bypass circuit 3 has a first bypass pipe 3a, a pressure reducing mechanism 36, a temperature adjustment device 34, a sub-exterior heat exchanger 31, and a second sub-expansion valve 17.
  • the first bypass pipe 3a branches off from between the indoor heat exchanger 21 of the main circuit 2 and the main expansion valve 13, and is connected between the main outdoor heat exchanger 11 and the compressor 14.
  • the main circuit 2 is equipped with a first sub-expansion valve 16 and a four-way valve 15, and the first bypass pipe 3a is connected between the first sub-expansion valve 16 and the four-way valve 15.
  • the first bypass pipe 3a is provided with, in order from the upstream side, a pressure reducing mechanism 36, a temperature adjustment device 34, the sub-exterior heat exchanger 31, and the second sub-expansion valve 17.
  • the sub-exterior heat exchanger 31 is provided in the first bypass pipe 3a, and is connected in parallel to the main outdoor heat exchanger 11.
  • the second bypass circuit 4 has a second bypass pipe 4a and a third sub-expansion valve 35.
  • the second bypass pipe 4a branches off from between the compressor 14 and the indoor heat exchanger 21 of the main circuit 2 and is connected to between the pressure reducing mechanism 36 and the temperature adjustment device 34 in the first bypass pipe 3a.
  • the main circuit 2 is equipped with a four-way valve 15, and the second bypass pipe 4a branches off from between the four-way valve 15 of the main circuit 2 and the indoor heat exchanger 21.
  • the second bypass pipe 4a is provided with a third sub-expansion valve 35.
  • the compressor 14 sucks in the refrigerant and compresses it to a high temperature and high pressure state.
  • the compressor 14 is a volumetric compressor capable of varying the operating frequency.
  • the compressor 14 is not limited to being driven with a variable operating frequency, and may be a constant speed compressor.
  • the four-way valve 15 is connected to the discharge side of the compressor 14 and switches the flow of the refrigerant discharged from the compressor 14.
  • the four-way valve 15 switches the circulation direction of the refrigerant discharged from the compressor 14 between heating operation and cooling operation.
  • the four-way valve 15 switches the direction of the refrigerant toward the indoor heat exchanger 21 during heating operation, and switches the direction of the refrigerant toward the main outdoor heat exchanger 11 during cooling operation.
  • the air conditioning device 100 only needs to be capable of at least heating operation, and therefore the four-way valve 15 can be omitted.
  • the indoor heat exchanger 21 is a fin-tube type heat exchanger including a pipe through which the refrigerant flows and fins into which the pipe is inserted.
  • the indoor heat exchanger 21 is not limited to a fin-tube type heat exchanger, but may be a plate type heat exchanger.
  • the main expansion valve 13 expands the refrigerant.
  • the main expansion valve 13 is formed, for example, of an electronic expansion valve or a temperature type expansion valve whose opening can be adjusted.
  • the main outdoor heat exchanger 11 is a fin-tube type heat exchanger including a pipe through which the refrigerant flows and fins into which the pipe is inserted.
  • the main outdoor heat exchanger 11 is not limited to a fin-tube type heat exchanger, but may be a plate type heat exchanger.
  • the first sub-expansion valve 16 expands the refrigerant.
  • the first sub-expansion valve 16 is formed, for example, of an electronic expansion valve or a temperature type expansion valve whose opening can be adjusted.
  • the pressure reducing mechanism 36 reduces the pressure of the refrigerant.
  • the pressure reducing mechanism 36 is configured with a fixed restriction such as a capillary tube, but it may also be an electric expansion valve that can change the flow path area.
  • the temperature adjusting device 34 is a device that adjusts the temperature of the refrigerant.
  • the temperature adjusting device 34 is equipped with a valve that adjusts the pressure of the refrigerant, and is a device that adjusts the temperature of the refrigerant by adjusting the pressure of the refrigerant.
  • the temperature adjusting device 34 is equipped with, for example, an electronic expansion valve that can adjust the opening degree as a valve that adjusts the pressure of the refrigerant.
  • the auxiliary outdoor heat exchanger 31 is a fin-tube type heat exchanger including piping through which the refrigerant flows and fins into which the piping is inserted.
  • the auxiliary outdoor heat exchanger 31 is not limited to a fin-tube type heat exchanger, and may be a plate type heat exchanger.
  • the second sub-expansion valve 17 and the third sub-expansion valve 35 expand the refrigerant.
  • the second sub-expansion valve 17 and the third sub-expansion valve 35 are formed, for example, by electronic expansion valves or temperature-type expansion valves whose opening can be adjusted.
  • the air conditioning device 100 also has a main outdoor fan 12 that blows air to the main outdoor heat exchanger 11, a secondary outdoor fan 32 that blows air to the secondary outdoor heat exchanger 31, and an indoor fan 22 that blows air to the indoor heat exchanger 21.
  • the main outdoor fan 12 is disposed in the main outdoor unit 10
  • the secondary outdoor fan 32 is disposed in the secondary outdoor unit 30, and the indoor fan 22 is disposed in the indoor unit 20.
  • the air conditioning device 100 has a drain pan 33.
  • the drain pan 33 is arranged in the auxiliary outdoor unit 30.
  • the drain pan 33 is arranged below the auxiliary outdoor heat exchanger 31, and is a container that collects condensed water that is generated in the auxiliary outdoor heat exchanger 31 and falls under its own weight.
  • the arrangement of the devices constituting the refrigerant circuit 1 of the air conditioner 100 is not limited to the arrangement shown in the figure.
  • the main outdoor unit 10 only needs to have at least the compressor 14, the main expansion valve 13, and the main outdoor heat exchanger 11.
  • the auxiliary outdoor unit 30 only needs to have at least the auxiliary outdoor heat exchanger 31 and the humidifier 40.
  • the indoor unit 20 only needs to have at least the indoor heat exchanger 21.
  • the other devices constituting the refrigerant circuit 1 may be arranged in a device other than the device shown in the figure.
  • the temperature adjustment device 34 is in the auxiliary outdoor unit 30 in the example shown in the figure, but it may be arranged in the main outdoor unit 10.
  • the air conditioner 100 is configured separately for the main outdoor unit 10 and the auxiliary outdoor unit 30, it may be configured in a single housing.
  • the air conditioning device 100 also has a control device 50 that controls the entire air conditioning device 100.
  • the control device 50 is composed of dedicated hardware, or a CPU (Central Processing Unit, also called a central processing unit, processing device, arithmetic unit, microprocessor, microcomputer, or processor) that executes programs stored in memory.
  • CPU Central Processing Unit
  • CPU Central Processing Unit
  • control device 50 When the control device 50 is dedicated hardware, the control device 50 may be, for example, a single circuit, a composite circuit, an application specific integrated circuit (ASIC), a field-programmable gate array (FPGA), or a combination of these. Each of the functional units realized by the control device 50 may be realized by separate hardware, or each functional unit may be realized by a single piece of hardware.
  • ASIC application specific integrated circuit
  • FPGA field-programmable gate array
  • each function executed by the control device 50 is realized by software, firmware, or a combination of software and firmware.
  • Software and firmware are written as programs and stored in memory.
  • the CPU realizes each function of the control device 50 by reading and executing the programs stored in the memory.
  • the memory is, for example, non-volatile or volatile semiconductor memory such as RAM, ROM, flash memory, EPROM, EEPROM, etc.
  • control device 50 may be realized by dedicated hardware, and some by software or firmware.
  • the air conditioning apparatus 100 has a control device 50, which controls the entire air conditioning apparatus 100, but the following configuration may also be used. As shown by the dotted lines in FIG. 1, the air conditioning apparatus 100 has a main outdoor unit control device 51, a sub-outdoor unit control device 52, and an indoor unit control device 53 for the main outdoor unit 10, the sub-outdoor unit 30, and the indoor unit 20, respectively, and these may work together to control the entire air conditioning apparatus 100.
  • the control device 50 has multiple operation modes, and operates in the operation mode selected by the user.
  • the operation mode is selected by operating a remote control (not shown).
  • the control device 50 controls the opening and closing or adjustment of the opening degree of multiple valves provided in the air conditioning device 100 according to the operation mode.
  • the control device 50 has a heating operation mode and a cooling operation mode as multiple operation modes.
  • the heating operation mode has a water collection heating operation mode and a defrost heating operation mode.
  • the control device 50 has three operation modes: the water collection heating operation mode, the defrost heating operation mode, and the cooling operation mode.
  • the control device 50 operates by alternatively selecting one of the three operation modes.
  • the water collection heating operation mode is a mode in which, while performing heating operation to warm the room in which the indoor unit 20 is installed, water is collected to be used to generate humidified air in the humidifier 40 described below.
  • the defrost heating operation mode is a mode in which, while performing heating operation, frost adhering to the main outdoor heat exchanger 11 is removed and water is collected to be used to generate humidified air in the humidifier 40 described below.
  • the cooling operation mode is a mode in which the room in which the indoor unit 20 is installed is cooled.
  • the air conditioning system 100 also includes a humidifier 40 that generates humidified air using the condensed water collected in the drain pan 33.
  • the humidifier 40 is disposed in the auxiliary outdoor unit 30.
  • the humidifier 40 humidifies air taken in from the outside (hereinafter, outside air) using condensed water generated in the auxiliary outdoor heat exchanger 31, and discharges the humidified air.
  • the humidified air discharged from the humidifier 40 is supplied to the indoor unit 20.
  • the humidifier 40 has a configuration in which a humidifying element 43, an air preheating device 42, a humidified air heating device 44, and a humidifying fan 41 are arranged in a housing 46 having an air passage 46a through which outside air flows.
  • the humidifier 40 also includes a humidifying duct 45 that guides the humidified air generated in the housing 46 to the indoor unit 20.
  • the humidifying element 43 is made of a material that retains water. It is desirable for the humidifying element 43 to be made of a material that has both the ability to retain water by capillary force, such as a nonwoven fabric or porous material, and the ability to allow air to flow through it, expanding the area of direct contact with the water.
  • the humidifying element 43 is placed below the drain pan 33, and humidifies the outside air passing through the humidifying element 43 with condensed water guided from the drain pan 33 to the humidifying element 43.
  • the air preheating device 42 has an air preheating heater 42a, which is, for example, an electric heater.
  • the air preheating device 42 is disposed upstream of the humidifying element 43 in the direction of the air flow formed by the humidifying fan 41, and heats the outside air supplied to the humidifying element 43.
  • the humidified air heating device 44 has a humidified air heater 44a, which is, for example, an electric heater.
  • the humidified air heating device 44 is disposed downstream of the humidifying element 43 in the air flow direction formed by the humidifying fan 41, and heats the humidified air humidified by the humidifying element 43.
  • the humidifying fan 41 takes in outside air into the housing 46 and generates an airflow that passes through the air passage 46a.
  • the humidifying fan 41 is provided downstream of the humidified air heating device 44 in the air flow direction, but it may also be provided upstream of the air preheating device 42.
  • the humidifier 40 takes in outside air into the housing 46 by driving the humidifier fan 41, heats it in the air preheater 42, and then supplies it to the humidifier element 43.
  • the humidifier 40 is mainly driven in the winter when the heating operation mode is operated, and the outside air taken into the housing 46 is assumed to be in a temperature range of about 0 to 7 degrees Celsius. The amount of saturated water vapor in this temperature range is insufficient to humidify the heated air inside the room.
  • the humidifier 40 heats the outside air in the air passage 46a through which the outside air flows with the air preheater 42 to reduce the relative humidity of the outside air, and changes the air state to one that is easy to adsorb moisture in the humidifier element 43 that it passes through next.
  • the heated outside air passes through the humidification element 43.
  • the humidification element 43 holds condensed water guided from the drain pan 33, and the heated outside air evaporates the water equivalent to a satisfactory amount of humidification into water vapor.
  • the outside air passing through the humidification element 43 comes into direct contact with the water vapor and is humidified, becoming humidified air with a relative humidity of nearly 100 percent.
  • the humidified air humidified by the humidification element 43 is heated by the humidified air heater 44 and transported into the room via the humidification duct 45.
  • the humidifier 40 generates humidified air using condensed water and supplies the humidified air into the room via the humidification duct 45.
  • the humidified air humidified by the humidifying element 43 is cooled by the humidifying duct 45 when it is transported indoors through the humidifying duct 45.
  • the outer surface of the humidifying duct 45 is cooled to the temperature of the outside air, and the inner surface is cooled by thermal conduction in the thickness direction of the wall of the humidifying duct 45.
  • the relative humidity of the humidified air flowing into the humidifying duct 45 is 100%, even a small amount of cooling causes the water vapor contained in the humidified air to change phase to water, causing condensation on the inner surface of the humidifying duct 45. Condensation can cause mold, which deteriorates the quality of the humidified air after mold growth.
  • the humidifying device 40 has a humidified air heater 44 between the humidifying element 43 and the humidifying duct 45, which increases the temperature of the humidified air and reduces the relative humidity, thereby avoiding condensation on the inner surface due to heat exchange with the outside air through the wall of the humidifying duct 45.
  • FIG. 3 is a schematic diagram showing a phase change of the refrigerant in the water-collection heating operation mode of the refrigerant circuit 1 of the air-conditioning apparatus 100 according to the first embodiment.
  • the phase change of the refrigerant in the water-collection heating operation mode is shown by different types of lines.
  • the arrows indicate the flow direction of the refrigerant.
  • the superheated gas refrigerant discharged from the compressor 14 passes through point A and the four-way valve 15, and then branches into two paths passing through points B and E, respectively.
  • the distribution ratio of the refrigerant to each of these paths is adjusted by the opening degree of the third sub-expansion valve 35.
  • the opening degree of the third sub-expansion valve 35 is determined according to the heating capacity required by the indoor unit 20. For example, when the indoor load is large, the opening degree of the third sub-expansion valve 35 is reduced to increase the refrigerant flow rate supplied to the indoor heat exchanger 21. This opening degree control of the third sub-expansion valve 35 is also performed in the defrost heating operation mode described later.
  • the refrigerant that passes through point B exchanges heat with the indoor air in the indoor heat exchanger 21.
  • the air is heated by exchanging heat with the refrigerant, heating the room.
  • the refrigerant condenses by exchanging heat with the air, and passes through point C as a supercooled liquid.
  • the refrigerant that passes through point C branches into two routes: one that passes through point D and heads toward the main outdoor heat exchanger 11, and the other that flows into the first bypass pipe 3a, passes through point F, etc., and heads toward the auxiliary outdoor heat exchanger 31.
  • the refrigerant that passes through point C branches into two routes and flows in parallel to the main outdoor heat exchanger 11 and the auxiliary outdoor heat exchanger 31.
  • the subcooled liquid refrigerant that has passed through point D is reduced in pressure as it passes through the main expansion valve 13, becoming a two-phase gas-liquid refrigerant and passing through point I.
  • the refrigerant that has passed through point I exchanges heat with the outside air in the main exterior heat exchanger 11, causing the liquid refrigerant to evaporate and become more dry, and then passes through point J and the first sub-expansion valve 16 in that order.
  • the refrigerant that flows into the first bypass pipe 3a passes through the pressure reducing mechanism 36, merges with the superheated gas refrigerant that passed through point E, and becomes a two-phase gas-liquid refrigerant that flows into the temperature adjustment device 34.
  • the refrigerant that flows into the temperature adjustment device 34 is reduced in pressure and becomes a two-phase gas-liquid refrigerant whose pressure-equivalent saturation temperature is lower than the dew point temperature of the outside air, passing through point G.
  • the gas-liquid two-phase refrigerant that has passed through point G exchanges heat with the outside air in the auxiliary outdoor heat exchanger 31, and the liquid refrigerant contained in the gas-liquid two-phase refrigerant evaporates, increasing the dryness.
  • the water vapor contained in the outside air is cooled to a temperature lower than the dew point on the surface of the auxiliary outdoor heat exchanger 31 and changes phase to water or frost.
  • the water vapor contained in the outside air condenses to produce condensed water.
  • the produced condensed water falls from the auxiliary outdoor heat exchanger 31 and collects in the drain pan 33.
  • the refrigerant that has passed through the auxiliary outdoor heat exchanger 31 passes through point H and the second sub-expansion valve 17 in that order, merges with the refrigerant that has passed through the first sub-expansion valve 16, passes through the four-way valve 15 and point K, and is then sucked into the compressor 14.
  • Figure 4 is a p-h diagram showing the change in refrigerant pressure and enthalpy in the water collection heating operation mode of the refrigerant circuit 1 of the air conditioning apparatus 100 according to embodiment 1.
  • Points A to K in Figure 4 represent the refrigerant pressure and enthalpy at points A to K in Figure 3.
  • the change in enthalpy from point G to point H in Figure 4 represents the heat exchange between the refrigerant and air in the auxiliary outdoor heat exchanger 31.
  • Also shown in Figure 4 are the isotherms of the outdoor dew point temperature, outdoor temperature, and indoor air temperature.
  • the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 at point G is set lower than the dew point temperature of the outside air by adjusting the opening of the temperature adjustment device 34, and the water vapor contained in the outside air changes phase to liquid or solid on the surface of the auxiliary outdoor heat exchanger 31.
  • the enthalpy change from point I to point J in Figure 4 represents heat exchange with the outside air in the main outdoor heat exchanger 11.
  • the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 is set higher than the dew point temperature of the outside air and lower than the outside air temperature by adjusting the opening of the main expansion valve 13. As a result, no condensation or frost forms on the surface of the main outdoor heat exchanger 11, and the main outdoor heat exchanger 11 maintains a state in which the air flow resistance is low and the amount of air passing through it is large.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 at a temperature lower than the dew point temperature of the outside air in the water collection heating operation mode. This allows the air conditioning device 100 to generate and obtain water vapor in the outside air as condensed water in the auxiliary outdoor heat exchanger 31.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 at a temperature lower than the dew point temperature of the outdoor air, while at the same time maintaining the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 at a temperature higher than the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 and lower than the temperature of the outdoor air.
  • the air conditioning device 100 can make the main outdoor heat exchanger 11 function as an evaporator and absorb heat from the outdoor air.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 mounted in the indoor unit 20 at a temperature higher than the indoor air temperature. In this way, the air conditioning device 100 heats the room.
  • the air conditioning apparatus 100 causes refrigerant to flow through the main outdoor heat exchanger 11 and uses the main outdoor heat exchanger 11 as an evaporator, but if it is desired to obtain a large amount of condensed water, it is more effective to not cause refrigerant to flow through the main outdoor heat exchanger 11, and to supply the entire amount to the auxiliary outdoor heat exchanger 31.
  • This modified example is an example in which no refrigerant flows through the main outdoor heat exchanger 11, and the entire amount is supplied to the auxiliary outdoor heat exchanger 31, and will be described using Figures 5 and 6.
  • FIG. 5 is a schematic diagram showing the phase change of the refrigerant in a modified water-collection heating operation mode of the refrigerant circuit 1 of the air-conditioning apparatus 100 according to embodiment 1.
  • the phase change of the refrigerant in the water-collection heating operation mode is shown by different line types.
  • the arrows indicate the flow direction of the refrigerant.
  • FIG. 6 is a p-h diagram showing the change in the pressure and enthalpy of the refrigerant in a modified water-collection heating operation mode of the refrigerant circuit 1 of the air-conditioning apparatus 100 according to embodiment 1. Points A to K in FIG. 6 represent the pressure and enthalpy of the refrigerant at points A to K in FIG. 5.
  • points D, I, and J where the refrigerant does not flow are omitted in FIG. 5.
  • the change in enthalpy from point G to point H in FIG. 6 represents the heat exchange between the refrigerant and the air in the auxiliary outdoor heat exchanger 31.
  • FIG. 6 the isotherms of the outdoor dew point temperature, the outdoor temperature, and the indoor air temperature are shown.
  • the air conditioning device 100 closes the main expansion valve 13 and the first sub-expansion valve 16. As a result, the entire amount of refrigerant that has passed through the indoor heat exchanger 21 passes through the temperature adjustment device 34 and then flows into the sub-exterior heat exchanger 31. As a result, the air conditioning device 100 can generate and obtain more condensed water in the sub-exterior heat exchanger 31 compared to the above-mentioned water collection heating operation mode described using Figures 3 and 4.
  • the auxiliary outdoor heat exchanger 31 in the water collection heating operation mode, while performing heating operation, the auxiliary outdoor heat exchanger 31 generates water to be used to generate humidified air in the humidifier 40.
  • the water collection heating operation mode when the dew point temperature of the outside air is high and the surface temperature of the auxiliary outdoor heat exchanger 31 is higher than zero degrees Celsius, the water vapor contained in the outside air on the surface of the auxiliary outdoor heat exchanger 31 changes phase to water and flows down the surface of the auxiliary outdoor heat exchanger 31 under its own weight and falls into the drain pan 33.
  • the water collected in the drain pan 33 is guided to the humidifier 40 as described above and used to humidify the room.
  • the air conditioning apparatus 100 when the dew point temperature of the outside air is high and the surface temperature of the auxiliary outdoor heat exchanger 31 is higher than zero degrees Celsius, the air conditioning apparatus 100 generates water to be used for humidification in the water collection heating operation mode, and can humidify the room.
  • the air conditioner 100 has a defrost heating operation mode that provides heat to the auxiliary outdoor heat exchanger 31 while continuing heating operation, melting the frost into water, and the water is collected in the drain pan 33, making it possible to humidify the room.
  • FIG. 7 is a schematic diagram showing a phase change of the refrigerant in the defrost heating operation mode of the refrigerant circuit 1 of the air-conditioning apparatus 100 according to the first embodiment.
  • the phase change of the refrigerant in the defrost heating operation mode is shown by different types of lines.
  • the arrows indicate the flow direction of the refrigerant.
  • the order in which the refrigerant flows through the refrigerant circuit 1 is the same as in the water collection heating operation mode shown in Fig. 3.
  • the conditions for setting the opening degree of the temperature adjustment device 34 are different between the defrost heating operation mode and the water collection heating operation mode.
  • the opening degree of the temperature adjustment device 34 is set so that the temperature of the refrigerant flowing into the auxiliary outdoor heat exchanger 31 is lower than the dew point temperature of the outside air.
  • the air conditioning device 100 makes the refrigerant supplied to the auxiliary outdoor heat exchanger 31 a low-pressure two-phase gas-liquid refrigerant lower than the dew point temperature of the outside air.
  • the air conditioning device 100 cools the outside air to a temperature lower than the dew point temperature by supplying a low-pressure two-phase gas-liquid refrigerant lower than the dew point temperature of the outside air to the auxiliary outdoor heat exchanger 31, thereby changing the phase of the water vapor contained in the outside air to water or frost.
  • the air conditioner 100 sets the opening degree of the temperature adjustment device 34 smaller than in the water collection heating operation mode to reduce the pressure drop amount compared to the water collection heating operation mode, and supplies superheated gas refrigerant at 0 degrees Celsius or higher to the auxiliary outdoor heat exchanger 31.
  • the superheated gas refrigerant is supplied to the auxiliary outdoor heat exchanger 31, and the superheated gas refrigerant gives heat to the frost, melting the frost and changing its phase to water.
  • the air conditioner 100 causes the auxiliary outdoor heat exchanger 31, of the auxiliary outdoor heat exchanger 31 and the main outdoor heat exchanger 11 connected in parallel, to function as a condenser. Then, the water generated by the melting frost falls from the auxiliary outdoor heat exchanger 31 and collects in the drain pan 33, and the refrigerant condenses to reduce the dryness and enter a gas-liquid two-phase state.
  • the refrigerant condensed in the indoor heat exchanger 21 by releasing heat to the indoor air is evaporated in the main outdoor heat exchanger 11 by collecting heat from the outdoor air to become a two-phase gas-liquid refrigerant with a high dryness.
  • the air conditioning device 100 causes the main outdoor heat exchanger 11, of the auxiliary outdoor heat exchanger 31 and the main outdoor heat exchanger 11 connected in parallel, to function as an evaporator.
  • the two-phase gas-liquid refrigerant after passing through the main outdoor heat exchanger 11 is mixed with the two-phase gas-liquid refrigerant flowing out from the auxiliary outdoor heat exchanger 31, so that the refrigerant drawn into the compressor 14 has a wetness that is acceptable for drawing into the compressor 14, and indoor heating can be continued.
  • the air conditioning apparatus 100 maintains the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 at a temperature above zero degrees Celsius in the defrost heating operation mode, melting the frost adhering to the auxiliary outdoor heat exchanger 31 and generating condensed water to be used for humidifying the room.
  • the air conditioning apparatus 100 maintains the main outdoor heat exchanger 11 at a temperature lower than the outdoor air temperature to absorb heat from the outdoor air.
  • the air conditioning apparatus 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature higher than the indoor air temperature, and continues heating operation.
  • Fig. 8 is a p-h diagram showing the change in refrigerant pressure and enthalpy in the defrost heating operation mode of the refrigerant circuit 1 of the air conditioning device 100 according to embodiment 1.
  • Points A to K in Fig. 8 represent the refrigerant pressure and enthalpy at points A to K in Fig. 5.
  • Also shown in Fig. 8 are isotherms for the outdoor dew point temperature, zero degrees Celsius, outdoor temperature, and indoor air temperature.
  • the temperature of the superheated gas at point G is maintained above zero degrees Celsius by adjusting the opening of the temperature adjustment device 34, and the superheated gas refrigerant that flows into the auxiliary outdoor heat exchanger 31 exchanges heat with the frost on the surface of the auxiliary outdoor heat exchanger 31 and condenses, reducing enthalpy from point G to point H.
  • the pressure equivalent saturation temperature of the main outdoor heat exchanger 11 is maintained at a temperature lower than the outdoor air temperature by adjusting the opening of the main expansion valve 13, and the refrigerant passing through the main outdoor heat exchanger 11 absorbs heat from the outdoor air. This allows the air conditioning device 100 to continue heating the room.
  • FIG. 9 is a schematic diagram showing a phase change of the refrigerant in the cooling operation mode of the refrigerant circuit 1 of the air conditioner 100 according to the first embodiment.
  • the phase change of the refrigerant in the cooling operation mode is shown by different types of lines.
  • the arrows indicate the flow direction of the refrigerant.
  • the flow direction of the refrigerant discharged from the compressor 14 is different from that in the water collection heating operation mode shown in FIG. 3 and the defrost heating operation mode shown in FIG. 5.
  • the flow direction of the refrigerant discharged from the compressor 14 is a direction toward point B and point E.
  • the flow direction of the refrigerant discharged from the compressor 14 is a direction toward point J and point H.
  • This switching of the refrigerant flow direction is obtained by the action of the four-way valve 15.
  • the third sub-expansion valve 35 is fully closed, and the refrigerant does not flow in the refrigerant path passing through point E.
  • the refrigerant discharged from the compressor 14 passes through the four-way valve 15 and then branches into a route that passes through point J and a route that passes through point H.
  • the distribution ratio of the refrigerant flow rate to these two routes is adjusted by the valve opening of both the first sub-expansion valve 16 and the second sub-expansion valve 17.
  • the refrigerant that passes through point J exchanges heat with the outside air in the main exterior heat exchanger 11 and condenses, becoming a supercooled liquid and passing through point I.
  • the refrigerant that passes through point I is decompressed as it passes through the main expansion valve 13, becoming a gas-liquid two-phase refrigerant and passing through point D.
  • the refrigerant that has passed point H exchanges heat with the outside air in the auxiliary outdoor heat exchanger 31, and the refrigerant condenses into a supercooled liquid and passes point G.
  • the refrigerant that has passed point G is reduced in pressure as it passes through the temperature adjustment device 34, becoming a two-phase gas-liquid refrigerant and passing point F.
  • the refrigerant that has passed point F passes through the pressure reduction mechanism 36, merges with the refrigerant that has passed point D, and passes point C.
  • the refrigerant that has passed point C exchanges heat with the indoor air in the indoor heat exchanger 21, cooling the air to cool the room, and evaporating the liquid refrigerant to increase its dryness.
  • the refrigerant then passes through point B, the four-way valve 15, and point K, before being sucked into the compressor 14.
  • Figure 10 is a p-h diagram showing the change in refrigerant pressure and enthalpy in the cooling operation mode of the refrigerant circuit 1 of the air conditioning apparatus 100 according to embodiment 1.
  • Points A to K in Figure 10 represent the refrigerant pressure and enthalpy at points A to K in Figure 9. Note that point E, where the refrigerant does not flow, is omitted from Figure 10.
  • the change in enthalpy from point J to point I in Figure 10 represents heat exchange with outside air in the main outdoor heat exchanger 11, and the change in enthalpy from point H to point G represents heat exchange with outside air in the auxiliary outdoor heat exchanger 31.
  • both the main outdoor heat exchanger 11 and the auxiliary outdoor heat exchanger 31 are used to condense the refrigerant through heat exchange with the outside air, minimizing the rise in high pressure in the refrigeration cycle under operating conditions where the outside air temperature is high.
  • the refrigerant is expanded and its pressure is reduced by the action of the main expansion valve 13, temperature adjustment device 34, and pressure reduction mechanism 36, and the pressure of the gas-liquid two-phase refrigerant flowing into the indoor heat exchanger 21 is adjusted so that its equivalent saturation temperature is lower than the indoor air temperature.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 and the auxiliary outdoor heat exchanger 31 at a temperature higher than the temperature of the outside air in the cooling operation mode. Furthermore, the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature lower than the indoor air temperature, thereby cooling the room.
  • the air-conditioning apparatus 100 of the first embodiment includes a refrigerant circuit 1 having a main circuit 2 in which at least a compressor 14, an indoor heat exchanger 21, a main expansion valve 13, and a main outdoor heat exchanger 11 are connected in sequence by refrigerant piping, and in which a refrigerant circulates.
  • the air-conditioning apparatus 100 includes an auxiliary outdoor heat exchanger 31 connected in parallel to the main outdoor heat exchanger 11, a humidifier 40A that humidifies air taken in from the outside using condensed water generated in the auxiliary outdoor heat exchanger 31 and discharges the humidified air, and a control device 50.
  • the control device 50 has a defrost heating operation mode in which the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 is maintained at a temperature equal to or higher than zero degrees Celsius, frost adhering to the auxiliary outdoor heat exchanger 31 is melted, condensed water is generated, and at the same time, the control device 50 maintains the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 at a temperature lower than the temperature of the outdoor air, and the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature higher than the indoor air temperature.
  • the auxiliary outdoor heat exchanger 31 is connected in parallel to the main outdoor heat exchanger 11, and in the defrost heating operation mode, the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 is maintained at a temperature above zero degrees Celsius to melt the frost adhering to the auxiliary outdoor heat exchanger 31 and generate condensed water, while at the same time maintaining the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 at a temperature lower than the temperature of the outside air. Therefore, even under operating conditions where the dew point temperature of the outside air is below freezing, the air conditioning apparatus 100 can melt the frost formed on the auxiliary outdoor heat exchanger 31 and generate condensed water to make humidified air.
  • the air conditioning apparatus 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature higher than the indoor air temperature, so that the room can be heated to maintain indoor comfort.
  • the air conditioning device 100 can maintain indoor comfort by continuing heating operation while producing water to create humidified air.
  • the humidifier 40 comprises a housing 46 having an air passage 46a therein through which air passes, and a humidifier element 43 that is disposed within the housing 46, holds condensed water generated in the auxiliary outdoor heat exchanger 31, and humidifies the air passing through the air passage 46a with the condensed water.
  • the humidifier 40 comprises an air preheating device 42 that heats the air to be supplied to the humidifier element 43, and a humidified air heating device 44 that heats the humidified air humidified by the humidifier element 43.
  • the air conditioning apparatus 100 has a humidifier 40 with the above-described configuration, which allows the humidified air to be kept at a high temperature and prevents the water contained in the humidified air from re-condensing in the humidifier duct 45.
  • the refrigerant circuit 1 includes a first bypass circuit 3 having a first bypass pipe 3a branched off between the indoor heat exchanger 21 and the main expansion valve 13 and connected between the main outdoor heat exchanger 11 and the compressor 14, an auxiliary outdoor heat exchanger 31 provided in the first bypass pipe 3a, and a temperature adjustment device 34 having a valve for adjusting the pressure of the refrigerant and adjusting the temperature of the refrigerant flowing into the auxiliary outdoor heat exchanger 31 by adjusting the pressure of the refrigerant.
  • the control device 50 controls the opening degree of the valve of the temperature adjustment device 34 to make the temperature of the refrigerant flowing into the auxiliary outdoor heat exchanger 31 a temperature above zero degrees Celsius.
  • the air conditioning device 100 can melt the frost that has formed in the auxiliary outdoor heat exchanger 31 and generate condensed water to make humidified air by using the temperature adjustment device 34 to raise the temperature of the refrigerant flowing into the auxiliary outdoor heat exchanger 31 to a temperature above zero degrees Celsius.
  • the air conditioning device 100 includes a first sub-expansion valve 16 provided between the main outdoor heat exchanger 11 and the compressor 14 of the main circuit 2, a pressure reducing mechanism 36 provided upstream of the temperature adjustment device 34 in the first bypass pipe 3a, and a second sub-expansion valve 17 provided downstream of the sub outdoor heat exchanger 31 in the first bypass pipe 3a.
  • the refrigerant circuit 1 includes a second bypass circuit 4.
  • the second bypass circuit 4 has a second bypass pipe 4a that branches off from between the compressor 14 and the indoor heat exchanger 21 and is connected between the pressure reducing mechanism 36 and the temperature adjustment device 34, and a third sub-expansion valve 35 provided in the second bypass pipe 4a.
  • the air conditioning device 100 can adjust the refrigerant flow rate supplied to the indoor heat exchanger 21 according to the heating capacity required by the indoor unit 20, depending on the opening setting of the third sub-expansion valve 35.
  • the air preheating device 42 is equipped with an air preheating heater 42a, and the humidified air heating device 44 is equipped with a humidified air heater 44a.
  • the above configuration allows the air conditioning device 100 to use a heater as a heat source to heat the outside air.
  • the control device 50 has a water collection heating operation mode.
  • the water collection heating operation mode is a mode in which the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 is maintained at a temperature lower than the dew point temperature of the outside air, while the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 is maintained at a temperature higher than the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 and lower than the outside air temperature, and the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 is maintained at a temperature higher than the indoor air temperature.
  • the control device 50 alternatively selects between the defrost heating operation mode and the water collection heating operation mode.
  • the air conditioning device 100 can maintain indoor comfort by humidifying the room while performing heating operation, regardless of whether the defrost heating operation mode or the water collection heating operation mode is selected.
  • the main circuit 2 is equipped with a four-way valve 15 that switches the flow direction of the refrigerant discharged from the compressor 14 to a direction toward the main outdoor heat exchanger 11 or a direction toward the indoor heat exchanger 21.
  • the control device 50 has a cooling operation mode that switches the four-way valve 15 to a direction toward the indoor heat exchanger 21, and maintains the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 and the auxiliary outdoor heat exchanger 31 at a temperature higher than the outdoor air temperature, and maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature lower than the indoor air temperature.
  • the control device 50 alternatively selects between a defrost heating operation mode, a water collection heating operation mode, and a cooling operation mode.
  • the air conditioning device 100 can maintain indoor comfort by humidifying the room while performing heating operation, regardless of whether the defrost heating operation mode or the water collection heating operation mode is selected, and can also cool the room when cooling operation is selected.
  • the second embodiment differs from the first embodiment in the configuration of the humidifier 40.
  • the following description will focus on the differences between the second embodiment and the first embodiment, and the configuration not described in the second embodiment is the same as that in the first embodiment.
  • FIG. 11 is a schematic diagram of the refrigerant circuit 1 of an air conditioning apparatus 100 according to embodiment 2.
  • the air conditioning apparatus 100 has a humidifier 40A.
  • the humidifier 40A differs from the humidifier 40A in that it uses the refrigerant flowing through the refrigerant circuit 1 as a heat source for heating the outside air, and is equipped with a heat exchanger that performs heat exchange using the refrigerant flowing through the refrigerant circuit 1.
  • the configuration of the refrigerant circuit 1 of the air conditioning apparatus 100 differs from that of embodiment 1 due to the humidifier 40A being equipped with a heat exchanger.
  • the refrigerant circuit 1 of the second embodiment differs from that of the first embodiment in the configuration of the first bypass circuit 3 and the second bypass circuit 4.
  • the pressure reducing mechanism 36 is eliminated, and a first on-off valve 37 is provided at the installation position of the pressure reducing mechanism 36.
  • the first on-off valve 37 is configured as a solenoid valve.
  • the second bypass pipe 4a branches off between the compressor 14 and the indoor heat exchanger 21 and has a main pipe 4aa provided with a third sub-expansion valve 35, and a first branch pipe 4b1 and a second branch pipe 4b2 branching off from the main pipe 4aa.
  • the first branch pipe 4b1 branches off from the main pipe 4aa and is connected between the temperature adjustment device 34 and the sub-outdoor heat exchanger 31 in the first bypass pipe 3a.
  • the second branch pipe 4b2 branches off from the main pipe 4aa, passes through the humidifier 40A, and is connected between the first opening/closing valve 37 and the temperature adjustment device 34 in the first bypass pipe 3a.
  • the second branch pipe 4b2 is provided with a primary side heat exchanger 42b and a secondary side heat exchanger 44b as shown in FIG. 12 described later.
  • the primary heat exchanger 42b and the secondary heat exchanger 44b are arranged such that the primary heat exchanger 42b is located downstream and the secondary heat exchanger 44b is located upstream in the refrigerant flow direction.
  • FIG. 12 is a schematic diagram showing a humidifier 40A according to the second embodiment.
  • the humidifier 40A differs from the humidifier 40 of the first embodiment in the configuration of the air preheater 42 and the humidified air heater 44.
  • the humidifier 40 has a configuration in which the air preheater 42 includes an air preheater 42a, and the humidified air heater 44 includes a humidified air heater 44a.
  • the humidifier 40A has a configuration in which the air preheater 42 includes an air preheater 42a and a primary heat exchanger 42b, and the humidified air heater 44 includes a humidified air heater 44a and a secondary heat exchanger 44b.
  • the air preheater 42 preheats the air to be supplied to the humidifier element 43 with both the air preheater 42a and the primary heat exchanger 42b.
  • the humidified air heating device 44 heats the air to be supplied to the humidifying duct 45 by both the humidified air heater 44a and the secondary side heat exchanger 44b.
  • the primary side heat exchanger 42b and the secondary side heat exchanger 44b are configured as heat exchangers that exchange heat between the refrigerant and the air.
  • the primary side heat exchanger 42b and the secondary side heat exchanger 44b are fin-tube type heat exchangers that include piping through which the refrigerant flows and fins into which the piping is inserted.
  • the primary side heat exchanger 42b and the secondary side heat exchanger 44b are not limited to fin-tube type heat exchangers, and may be finless heat exchangers that do not have fins.
  • the primary side heat exchanger 42b is disposed upstream of the air preheater 42a in the flow of outside air
  • the secondary side heat exchanger 44b is disposed upstream of the humidified air heater 44a and downstream of the humidification element 43 in the flow of outside air.
  • the refrigerant flowing through the second branch pipe 4b2 of the second bypass circuit 4 flows through the primary side heat exchanger 42b and the secondary side heat exchanger 44b.
  • the refrigerant flows through the primary side heat exchanger 42b and the secondary side heat exchanger 44b in the order of the secondary side heat exchanger 44b and the primary side heat exchanger 42b.
  • the humidifier 40A reduces the required input to the air preheater 42a and the humidified air heater 44a by utilizing the heat of the refrigerant to heat the outside air passing through the air passage 46a through the action of the primary side heat exchanger 42b and the secondary side heat exchanger 44b.
  • the humidifier 40A is configured with a heat exchanger through which the refrigerant of the refrigerant circuit 1 flows in both the air preheater 42 and the humidified air heater 44, but is not limited to this configuration.
  • the humidifier 40A may also be configured with a heat exchanger through which the refrigerant of the refrigerant circuit 1 flows in one of the air preheater 42 and the humidified air heater 44.
  • Fig. 13 is a schematic diagram showing a phase change of the refrigerant in the water collection heating operation mode of the refrigerant circuit 1 of the air conditioner 100 according to embodiment 2.
  • the first on-off valve 37 and the second on-off valve 38 are closed.
  • the phase change of the refrigerant in the water collection heating operation mode is represented by different types of lines.
  • the arrows indicate the flow direction of the refrigerant.
  • the superheated gas refrigerant discharged from the compressor 14 passes through point A and the four-way valve 15, and branches into two paths that pass through points B and D, respectively.
  • the distribution ratio of the refrigerant to these paths is adjusted by the opening degree of the third sub-expansion valve 35.
  • the refrigerant that passes through point B exchanges heat with the indoor air in the indoor heat exchanger 21, heating the air and heating the room, and the refrigerant condenses into a subcooled liquid and passes through point C.
  • the refrigerant that passes through points C and H in sequence is reduced in pressure as it passes through the main expansion valve 13, becoming a two-phase gas-liquid refrigerant and passing through point I.
  • the refrigerant that passes through point I exchanges heat with the outside air in the main outdoor heat exchanger 11, causing the liquid refrigerant to evaporate and increase in dryness, and then passes through point J and the first sub-expansion valve 16 in sequence.
  • the superheated gas refrigerant that has passed through point D flows into the humidifier 40A.
  • the superheated gas refrigerant that has flowed into the humidifier 40A is cooled by heat exchange with humidified air in the secondary heat exchanger 44b, and is then further cooled by heat exchange with air, i.e., outside air, in the primary heat exchanger 42b, changing phase to a supercooled liquid and passing through point E.
  • the refrigerant that has passed through point E is decompressed as it passes through the temperature adjustment device 34 and changes to a two-phase gas-liquid state.
  • This two-phase gas-liquid refrigerant exchanges heat with the outside air in the auxiliary outdoor heat exchanger 31, and the liquid refrigerant contained in the two-phase gas-liquid refrigerant evaporates, increasing the dryness.
  • the water vapor contained in the outside air is cooled to a temperature lower than the dew point on the surface of the auxiliary outdoor heat exchanger 31 and changes phase to water or frost.
  • the water falls from the auxiliary outdoor heat exchanger 31 and is collected in the drain pan 33.
  • the refrigerant that has passed through the auxiliary outdoor heat exchanger 31 passes through point G and the second sub-expansion valve 17 in this order, merges with the refrigerant that has passed through the first sub-expansion valve 16, passes through the four-way valve 15 and point J, and is then sucked into the compressor 14.
  • Figure 14 is a p-h diagram showing the change in refrigerant pressure and enthalpy in the water collection heating operation mode of the refrigerant circuit 1 of the air conditioning apparatus 100 according to embodiment 2.
  • Points A to K in Figure 14 represent the refrigerant pressure and enthalpy at points A to K in Figure 13. Note that point H is not shown in Figure 14.
  • the change in enthalpy from point F to point G in Figure 14 represents the heat exchange with air in the auxiliary outdoor heat exchanger 31.
  • the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 is set lower than the dew point temperature of the outside air by adjusting the opening of the temperature adjustment device 34, and the water vapor contained in the outside air changes phase to liquid or solid on the surface of the auxiliary outdoor heat exchanger 31.
  • the enthalpy change from point H to point I in Figure 14 represents the heat exchange with the outside air in the main outdoor heat exchanger 11.
  • the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 is set higher than the dew point temperature of the outside air and lower than the outside air temperature by adjusting the opening of the main expansion valve 13, and a state of low air flow resistance and large airflow is maintained without causing condensation or frost on the surface of the main outdoor heat exchanger 11.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 mounted in the auxiliary outdoor unit 30 at a temperature lower than the dew point temperature of the outdoor air. This allows the air conditioning device 100 to obtain water vapor in the outdoor air as condensed water.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 at a temperature lower than the dew point temperature of the outdoor air, while at the same time maintaining the refrigerant pressure equivalent saturation temperature of the main outdoor heat exchanger 11 at a temperature higher than the refrigerant pressure equivalent saturation temperature of the auxiliary outdoor heat exchanger 31 and lower than the temperature of the outdoor air.
  • the air conditioning device 100 can make the main outdoor heat exchanger 11 function as an evaporator and absorb heat from the outdoor air.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 mounted in the indoor unit 20 at a temperature higher than the indoor air temperature. In this way, the air conditioning device 100 heats the room.
  • the enthalpy change from point D to point E in Figure 14 represents the condensation of the refrigerant due to heat exchange with the outside air in the secondary side heat exchanger 44b and the primary side heat exchanger 42b.
  • the air conditioning apparatus 100 of embodiment 2 uses the heat of the refrigerant to heat the outside air in the primary side heat exchanger 42b and the secondary side heat exchanger 44b. Therefore, the air conditioning apparatus 100 of embodiment 2 reduces the required input of the air preheating heater 42a and the humidified air heater 44a.
  • Fig. 15 is a schematic diagram showing the phase change of the refrigerant in the defrost heating operation mode of the refrigerant circuit 1 of the air conditioner 100 according to the second embodiment.
  • the phase change of the refrigerant in the defrost heating operation mode is shown by different line types.
  • the arrows indicate the flow direction of the refrigerant.
  • the first opening/closing valve 37 and the temperature adjustment device 34 are closed, and the second opening/closing valve 38 is opened.
  • the air conditioner 100 supplies superheated gas refrigerant to the auxiliary outdoor heat exchanger 31 by opening and closing these valves, and the superheated gas refrigerant gives heat to the frost, causing the frost to melt and change phase to water and collect in the drain pan 33, and the refrigerant is condensed to reduce the dryness and become in a gas-liquid two-phase state.
  • the refrigerant that has condensed to a supercooled liquid by releasing heat to the indoor air in the indoor heat exchanger 21 is evaporated in the main outdoor heat exchanger 11 by collecting heat from the outdoor air to become a two-phase gas-liquid refrigerant with a high dryness.
  • the two-phase gas-liquid refrigerant is mixed with the two-phase gas-liquid refrigerant flowing out of the auxiliary outdoor heat exchanger 31, so that the refrigerant drawn into the compressor 14 has a wetness that is acceptable for drawing into the compressor 14, allowing indoor heating to continue.
  • the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperatures of the main outdoor heat exchanger 11 and the auxiliary outdoor heat exchanger 31 at a temperature lower than the outdoor air temperature in the defrost heating operation mode. Furthermore, the air conditioning device 100 maintains the refrigerant pressure equivalent saturation temperature of the indoor heat exchanger 21 at a temperature higher than the indoor air temperature.
  • the first opening/closing valve 37 is closed, and the flow of refrigerant to the primary heat exchanger 42b and the secondary heat exchanger 44b is blocked.
  • the humidifier 40A the flow of refrigerant to the primary heat exchanger 42b and the secondary heat exchanger 44b is blocked, and therefore the air flowing through the air passage 46a of the humidifier 40A cannot be heated by heat exchange with the refrigerant. Therefore, the humidifier 40A continues the humidification operation by heating the air flowing through the air passage 46a of the humidifier 40A using the air preheater 42a and the humidified air heater 44a.
  • Figure 16 is a p-h diagram showing the change in refrigerant pressure and enthalpy in the defrost heating operation mode of the refrigerant circuit 1 of the air conditioning apparatus 100 according to embodiment 2.
  • Points A to L in Figure 16 represent the refrigerant pressure and enthalpy at points A to L in Figure 15. Note that points E and F, where the refrigerant does not flow, and point H are not shown in Figure 16.
  • the air conditioning apparatus 100 maintains the temperature of the superheated gas at point F above zero degrees Celsius by selecting the diameter of the second opening/closing valve 38.
  • the air conditioning apparatus 100 melts the frost adhering to the auxiliary outdoor heat exchanger 31, and condenses the superheated gas refrigerant from point F to point G through heat exchange between the superheated gas and the frost, thereby reducing the enthalpy.
  • the air conditioning device 100 maintains the pressure-equivalent saturation temperature of the refrigerant passing through the main outdoor heat exchanger 11 at a temperature lower than the outdoor air temperature, allowing the room to continue to be heated.
  • FIG. 17 is a schematic diagram showing a phase change of the refrigerant in the cooling operation mode of the refrigerant circuit 1 of the air conditioner 100 according to the second embodiment.
  • the phase change of the refrigerant in the cooling operation mode is shown by different line types.
  • the arrows indicate the flow direction of the refrigerant.
  • the flow direction of the refrigerant discharged from the compressor 14 is different from that in the water collection heating operation mode shown in FIG. 3 and the defrost heating operation mode shown in FIG. 5.
  • the flow direction of the refrigerant discharged from the compressor 14 is a direction toward point B and point D.
  • the flow direction of the refrigerant discharged from the compressor 14 is a direction toward point J and point G.
  • This switching of the refrigerant flow direction is obtained by the action of the four-way valve 15.
  • the air conditioning apparatus 100 fully closes the third sub-expansion valve 35 and also closes the second opening/closing valve 38, so that no refrigerant flows through the refrigerant path passing through points D and L and through the humidifier 40A.
  • the refrigerant discharged from the compressor 14 passes through the four-way valve 15 and then branches into a route that passes through point J and a route that passes through point G.
  • the distribution ratio of the refrigerant flow rate to these two routes is adjusted by the valve opening of both the first sub-expansion valve 16 and the second sub-expansion valve 17.
  • the refrigerant that passes through point J exchanges heat with the outside air in the main exterior heat exchanger 11 and condenses, becoming a subcooled liquid and passing through point I.
  • the refrigerant that passes through point I is decompressed as it passes through the main expansion valve 13, becoming a gas-liquid two-phase refrigerant and passing through point H.
  • the refrigerant that has passed point G exchanges heat with the outside air in the auxiliary outdoor heat exchanger 31, and the refrigerant condenses into a supercooled liquid and passes point F.
  • the refrigerant that has passed point F is reduced in pressure as it passes through the temperature adjustment device 34, becoming a two-phase gas-liquid refrigerant and passing point E.
  • the refrigerant that has passed point E passes through the first opening and closing valve 37, merges with the refrigerant that has passed point H, and passes point C.
  • the refrigerant that has passed point C exchanges heat with the indoor air in the indoor heat exchanger 21, cooling the air to cool the room, and evaporating the liquid refrigerant to increase its dryness.
  • the refrigerant then passes through point B, the four-way valve 15, and point K, before being sucked into the compressor 14.
  • the air conditioning apparatus 100 of the second embodiment has the same effects as the first embodiment, and also has the following effects.
  • the humidifier 40A is provided with a primary side heat exchanger 42b and a secondary side heat exchanger 44b, so that the required input to the air preheater 42a and the humidified air heater 44a can be reduced, and power consumption in the heating operation mode can be reduced compared to a configuration that does not have the primary side heat exchanger 42b and the secondary side heat exchanger 44b.
  • the air preheating device 42 is configured to include an air preheater 42a and a primary side heat exchanger 42b as a heat source for heating the outside air, but it may be configured to include only the primary side heat exchanger 42b.
  • the humidified air heating device 44 is configured to include a humidified air heater 44a and a secondary side heat exchanger 44b as a heat source for heating the outside air, but it may be configured to include only the secondary side heat exchanger 44b.
  • the air preheating device 42 and the humidified air heating device 44 may use a refrigerant as a heat source for heating the outside air, and may be configured to include a heat exchanger without a heater.
  • Fig. 18 is a schematic diagram showing the auxiliary outdoor unit 30 of the air conditioning apparatus 100 according to embodiment 3.
  • thick arrows indicate the flow of refrigerant
  • thick outline arrows indicate the flow of outside air
  • thin dotted arrows indicate the flow of drain water, which is condensed water
  • thin solid arrows indicate electrical input.
  • the auxiliary outdoor unit 30 has an auxiliary outdoor heat exchanger 31, a drain pan 33, and a humidifier 40, and these components are arranged in this order from top to bottom.
  • the auxiliary outdoor unit 30 is equipped with the humidifier 40 of embodiment 1, but it may also be configured with the humidifier 40A of embodiment 2.
  • the auxiliary outdoor unit 30 and the indoor unit 20 are connected via an indoor unit-auxiliary outdoor unit communication pipe group 60 that passes through a piping hole 71 pre-drilled in the exterior wall 70 of the house.
  • the indoor unit-auxiliary outdoor unit communication pipe group 60 has a gas pipe 61 and a liquid pipe 62 that connect the indoor heat exchanger 21 and the auxiliary outdoor heat exchanger 31, and a humidification hose 63 through which humidified air passes.
  • the indoor unit-auxiliary outdoor unit communication pipe group 60 also has electrical wiring 64 that is connected to the indoor unit control device 53, and a drain hose 65 that guides condensed water generated in the indoor heat exchanger 21 to the humidifier 40.
  • the auxiliary outdoor unit 30 and the main outdoor unit 10 are connected via a main outdoor unit-auxiliary outdoor unit communication pipe group 68.
  • the main outdoor unit-auxiliary outdoor unit communication pipe group 68 has a first communication pipe 68a through which high-temperature, high-pressure gas refrigerant flows, a second communication pipe 68b through which low-temperature, low-pressure two-phase gas-liquid refrigerant flows, and a third communication pipe 68c through which high-pressure liquid refrigerant flows.
  • the main outdoor unit-auxiliary outdoor unit communication pipe group 68 also has electrical wiring 64a connected to the indoor unit control device 53, and a drain hose 65a that communicates with the drain hose 65.
  • the auxiliary outdoor unit 30 has a first connection port 66 and a second connection port 69.
  • the first connection port 66 is a connection port to the indoor unit-auxiliary outdoor unit communication pipe group 60. It is desirable that the first connection ports 66 are concentrated near the top surface of the auxiliary outdoor unit 30 in order to reduce the size of the indoor unit-auxiliary outdoor unit communication pipe group 60. It is desirable that the first connection port 66 is covered by a cover 67 because it would spoil the aesthetics if the piping hole 71 and the indoor unit-auxiliary outdoor unit communication pipe group 60 were exposed.
  • the second connection port 69 is a connection port for the main outdoor unit - auxiliary outdoor unit communication pipe group 68. It is desirable that the second connection ports 69 are concentrated near the bottom surface of the auxiliary outdoor unit 30.
  • the piping connection configuration of the auxiliary outdoor unit 30 is as described above, and the auxiliary outdoor unit 30 is connected to the indoor unit 20 from the first connection port 66 via the indoor unit-auxiliary outdoor unit communication pipe group 60, and is connected to the main outdoor unit 10 from the second connection port 69 via the main outdoor unit-auxiliary outdoor unit communication pipe group 68.
  • the operation of the auxiliary outdoor unit 30 is as described above.
  • the auxiliary outdoor unit 30 maintains the surface temperature of the auxiliary outdoor heat exchanger 31 at a temperature lower than the dew point temperature of the outside air by the action of the heat pump, and generates condensed water from the water vapor of the outside air.
  • the generated condensed water is collected by its own weight in the drain pan 33 arranged directly below the auxiliary outdoor heat exchanger 31.
  • the condensed water collected in the drain pan 33 is supplied by its own weight to the humidification element 43 of the humidification device 40 arranged directly below the drain pan 33.
  • the condensed water supplied to the humidification element 43 is held in the humidification element 43 by the action of the capillary force of the humidification element 43.
  • the air conditioning device 100 does not require a water pump to pump up the condensed water accumulated in the drain pan 33 and supply it to the humidifier 40, and the energy consumption required for humidification can be reduced.

Landscapes

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

Abstract

L'invention concerne un climatiseur comprenant : un circuit de fluide frigorigène ayant un circuit principal dans lequel au moins un compresseur, un échangeur de chaleur intérieur, un détendeur principal et un échangeur de chaleur extérieur principal sont reliés de manière séquentielle par une tuyauterie de fluide frigorigène, et dans lequel circule un fluide frigorigène ; un sous-échangeur de chaleur extérieur qui est relié en parallèle à l'échangeur de chaleur extérieur principal ; un humidificateur qui utilise de l'eau de condensation générée dans le sous-échangeur de chaleur extérieur pour humidifier l'air aspiré depuis l'extérieur, et évacue l'air humidifié ; et un dispositif de commande. Le dispositif de commande a un mode de fonctionnement de chauffage de dégivrage dans lequel la température de saturation équivalente à la pression de fluide frigorigène du sous-échangeur de chaleur extérieur est maintenue à une température égale ou supérieure à zéro degré Celsius et le givre adhérant au sous-échangeur de chaleur extérieur est fondu pour générer de l'eau de condensation, tandis que, simultanément, la température de saturation équivalente à la pression de fluide frigorigène de l'échangeur de chaleur extérieur principal est maintenue à une température inférieure à la température de l'air extérieur et la température de saturation équivalente à la pression de fluide frigorigène de l'échangeur de chaleur intérieur est maintenue à une température supérieure à la température d'air intérieur.
PCT/JP2023/021033 2023-06-06 2023-06-06 Climatiseur Pending WO2024252526A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/JP2023/021033 WO2024252526A1 (fr) 2023-06-06 2023-06-06 Climatiseur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2023/021033 WO2024252526A1 (fr) 2023-06-06 2023-06-06 Climatiseur

Publications (1)

Publication Number Publication Date
WO2024252526A1 true WO2024252526A1 (fr) 2024-12-12

Family

ID=93795400

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2023/021033 Pending WO2024252526A1 (fr) 2023-06-06 2023-06-06 Climatiseur

Country Status (1)

Country Link
WO (1) WO2024252526A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05203205A (ja) * 1992-01-23 1993-08-10 Matsushita Refrig Co Ltd 空気調和機における加湿器
JPH05306856A (ja) * 1992-04-30 1993-11-19 Hitachi Ltd 空冷式冷凍装置
JP2010038401A (ja) * 2008-08-01 2010-02-18 Panasonic Corp 空気調和機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05203205A (ja) * 1992-01-23 1993-08-10 Matsushita Refrig Co Ltd 空気調和機における加湿器
JPH05306856A (ja) * 1992-04-30 1993-11-19 Hitachi Ltd 空冷式冷凍装置
JP2010038401A (ja) * 2008-08-01 2010-02-18 Panasonic Corp 空気調和機

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