CN111630326B - Air conditioner - Google Patents

Air conditioner Download PDF

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Publication number
CN111630326B
CN111630326B CN201880087258.6A CN201880087258A CN111630326B CN 111630326 B CN111630326 B CN 111630326B CN 201880087258 A CN201880087258 A CN 201880087258A CN 111630326 B CN111630326 B CN 111630326B
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China
Prior art keywords
indoor
temperature
condition
satisfied
dehumidification
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CN201880087258.6A
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Chinese (zh)
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CN111630326A (en
Inventor
三浦脩
师井直纪
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Daikin Industries Ltd
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Daikin Industries Ltd
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Priority to CN202110055789.0A priority Critical patent/CN112856728B/en
Publication of CN111630326A publication Critical patent/CN111630326A/en
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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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/54—Control or safety arrangements characterised by user interfaces or communication using one central controller connected to several sub-controllers
    • 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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/56—Remote control
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • 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
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/65—Electronic processing for selecting an operating mode
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/75—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity for maintaining constant air flow rate or air velocity
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/74—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity
    • F24F11/77—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling air flow rate or air velocity by controlling the speed of ventilators
    • 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
    • F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
    • F24F11/79—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure for controlling the direction of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—Control systems characterised by their outputs; Constructional details thereof
    • F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • 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
    • F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
    • F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
    • 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
    • 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
    • F24F11/87—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units
    • F24F11/871—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling absorption or discharge of heat in outdoor units by controlling outdoor fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/20—Humidity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/10—Pressure
    • F24F2140/12—Heat-exchange fluid pressure

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Physics & Mathematics (AREA)
  • Signal Processing (AREA)
  • Thermal Sciences (AREA)
  • Fluid Mechanics (AREA)
  • Fuzzy Systems (AREA)
  • Mathematical Physics (AREA)
  • Human Computer Interaction (AREA)
  • Air Conditioning Control Device (AREA)

Abstract

A control unit (6) of an air conditioning device (1) stops a compressor (21) when a predetermined thermal shutdown condition is satisfied during a dehumidification operation, and has a thermal shutdown temperature condition based on an indoor temperature and a thermal shutdown humidity condition based on an indoor humidity as determination elements for determining whether the thermal shutdown condition is satisfied. In addition, during the dehumidification operation, when the thermal shutdown temperature condition is satisfied but the thermal shutdown humidity condition is not satisfied, the control unit (6) does not stop the compressor (21), but controls the capacity of the compressor (21) and the air volume of the indoor fan (32) so that the evaporation temperature of the refrigerant in the indoor heat exchanger (31) is lower than the dew-point temperature of the indoor air.

Description

Air conditioner
Technical Field
An air conditioner performs a dehumidifying operation.
Background
Conventionally, there are air conditioners as follows: the refrigerant circuit is formed by connecting a compressor, an outdoor heat exchanger, an expansion mechanism and an indoor heat exchanger. In this air conditioner, a dehumidification operation may be performed in which the refrigerant sealed in the refrigerant circuit is circulated in the order of the compressor, the outdoor heat exchanger, the expansion mechanism, and the indoor heat exchanger. In this dehumidification operation, as shown in patent document 1 (japanese patent application laid-open No. 2004-76973), when the indoor temperature reaches the target indoor temperature, a thermal shutdown is performed to stop the compressor.
Disclosure of Invention
As described above, in the air conditioner of patent document 1, when the indoor temperature reaches the target indoor temperature during the dehumidification operation, it is determined that the thermal shutdown condition is satisfied and the thermal shutdown is performed.
However, in such a dehumidification operation, in a state where the indoor dehumidification is insufficient, the indoor temperature may reach the target indoor temperature and the heat shut-off may be performed, and there is a possibility that the indoor person feels uncomfortable due to the insufficient indoor dehumidification.
The air conditioning apparatus according to claim 1 includes a refrigerant circuit, an indoor fan, and a control unit. The refrigerant circuit is configured by connecting a compressor, an outdoor heat exchanger, an expansion mechanism, and an indoor heat exchanger. The indoor fan delivers indoor air to the indoor heat exchanger. The control unit performs a dehumidification operation in which the refrigerant sealed in the refrigerant circuit is circulated in the order of the compressor, the outdoor heat exchanger, the expansion mechanism, and the indoor heat exchanger. In the dehumidification operation, the control unit stops the compressor when a predetermined thermal shutdown condition is satisfied, and the control unit has a thermal shutdown temperature condition based on the indoor temperature and a thermal shutdown humidity condition based on the indoor humidity as a determination element for determining whether the thermal shutdown condition is satisfied. In the dehumidification operation, when the thermal shutdown temperature condition is satisfied but the thermal shutdown humidity condition is not satisfied, the control unit does not stop the compressor when the indoor temperature satisfies the thermal shutdown temperature condition, but controls the capacity of the compressor and the air volume of the indoor fan so that the evaporation temperature of the refrigerant in the indoor heat exchanger is lower than the dew-point temperature of the indoor air.
Here, even if the hot shut-off temperature condition is satisfied, the hot shut-off is not performed, and the dehumidification of the room is continued in a state where condensation of the room air is reliably generated in the indoor heat exchanger. Therefore, compared to the case where the thermal shutdown is performed when the thermal shutdown temperature condition is satisfied, the dehumidification amount can be increased, and the possibility that the indoor person feels uncomfortable due to insufficient dehumidification in the room can be reduced.
Regarding the air conditioning apparatus according to claim 2, in the air conditioning apparatus according to claim 1, the control unit performs the following control: the air volume of the indoor fan is controlled to a minimum air volume, and the capacity of the compressor is reduced in a range where the evaporation temperature is lower than the dew point temperature.
Here, since the heat exchange between the refrigerant and the indoor air can be suppressed by reducing the flow rate of the refrigerant that exchanges heat in the indoor heat exchanger and the air volume of the indoor air, a decrease in the indoor temperature can be suppressed, and the possibility that the indoor temperature is too low and causes discomfort to indoor people can be reduced.
Regarding the air conditioning apparatus according to claim 3, in the air conditioning apparatus according to claim 2, the control unit performs the following control: the capacity of the compressor is reduced until the indoor temperature rises.
Here, by reducing the flow rate of the refrigerant that exchanges heat in the indoor heat exchanger to a flow rate at which dehumidification is performed without lowering the indoor temperature, the possibility of discomfort to the indoor person can be further reduced.
Regarding the air conditioning apparatus according to claim 4, in the air conditioning apparatus according to claim 2 or 3, the control unit performs the following control: the capacity of the compressor is reduced in a range of the lower limit value of the evaporation temperature or more.
Here, the possibility that condensation occurs near the air outlet of the indoor unit housing the indoor heat exchanger due to excessive cooling of the indoor air in the indoor heat exchanger can be reduced.
Regarding the air conditioning apparatus according to claim 5, in the air conditioning apparatus according to claim 4, the control unit lowers the lower limit value of the evaporation temperature during the dehumidification operation.
Here, the range in which the evaporation temperature is reduced can be expanded, and the evaporation temperature can be reliably made lower than the dew point temperature.
Regarding the air conditioning apparatus according to claim 6, in the air conditioning apparatus according to claim 5, the control unit determines the lower limit of the evaporation temperature based on the indoor temperature and the indoor humidity.
Here, the range in which the evaporation temperature is reduced can be expanded in consideration of the indoor temperature and the indoor humidity, and therefore the occurrence of dew condensation can be suppressed as much as possible.
Regarding the air conditioning apparatus according to claim 7, in any one of the air conditioning apparatuses according to claims 1 to 6, the control unit is configured to be able to select a plurality of dehumidification operation modes having different dehumidification levels as the dehumidification operation.
Here, the dehumidifying operation can be performed according to the demand of the dehumidification level of the indoor person.
Regarding the air conditioning apparatus according to aspect 8, in the air conditioning apparatus according to aspect 7, the control unit changes the heat shut-off temperature condition to the low temperature side as the dehumidification level of the selected dehumidification operation mode is higher.
Here, the higher the dehumidification level is, the less likely the 1 st heat shutdown temperature condition is satisfied, so the dehumidification amount can be increased until the 1 st heat shutdown temperature condition is satisfied.
Drawings
Fig. 1 is a schematic configuration diagram of an air conditioner according to an embodiment of the present disclosure.
Fig. 2 is an external perspective view of an indoor unit constituting the air conditioner.
Fig. 3 is a schematic side sectional view of the indoor unit, which is a sectional view taken along line I-O-I of fig. 2.
Fig. 4 is a control block diagram of the air conditioner.
Fig. 5 is a control flowchart during the cooling operation.
Fig. 6 is a control flowchart (mode selection) during the dehumidification operation.
Fig. 7 is a control flowchart during the dehumidification operation (dehumidification operation mode L, M, H).
Fig. 8 is a flowchart showing dehumidification continuation control in modification a.
Fig. 9 is a flowchart showing dehumidification continuation control in modification B.
Detailed Description
Hereinafter, embodiments of the air conditioner will be described with reference to the drawings.
(1) Equipment structure
Fig. 1 is a schematic configuration diagram of an air conditioner 1 according to an embodiment of the present disclosure.
< entirety >
The air conditioner 1 is an apparatus for conditioning indoor air in a building or the like by a vapor compression refrigeration cycle. The air conditioning apparatus 1 mainly has an outdoor unit 2, an indoor unit 3, a liquid refrigerant communication tube 4 connecting the outdoor unit 2 and the indoor unit 3, and a gas refrigerant communication tube 5. The vapor compression-type refrigerant circuit 10 of the air-conditioning apparatus 1 is configured by connecting the outdoor unit 2 and the indoor unit 3 via the liquid refrigerant communication tube 4 and the gas refrigerant communication tube 5.
< outdoor unit >
The outdoor unit 2 is installed outdoors (on a roof of a building, near an outer wall surface of a building, or the like). As described above, the outdoor unit 2 is connected to the indoor unit 3 via the liquid refrigerant communication tube 4 and the gas refrigerant communication tube 5, and constitutes a part of the refrigerant circuit 10. The outdoor unit 2 mainly includes a compressor 21, a four-way switching valve 23, an outdoor heat exchanger 24, and an expansion valve 25.
The compressor 21 is a mechanism that compresses a low-pressure refrigerant in the refrigeration cycle to a high pressure. Here, as the compressor 21, a compressor of a closed structure in which a positive displacement compression element (not shown) such as a rotary type or a scroll type is rotationally driven by a compressor motor 22 is used. Here, the compressor motor 22 can control the capacity of the compressor 21 by controlling the rotation speed (frequency) by an inverter or the like.
The four-way switching valve 23 is a valve for switching the flow direction of the refrigerant at the time of switching between the cooling operation, the dehumidifying operation, and the heating operation. The four-way switching valve 23 can connect the discharge side of the compressor 21 and the gas side of the outdoor heat exchanger 24 during the cooling operation or the dehumidifying operation, and connect the gas side of the indoor heat exchanger 31 (described later) and the suction side of the compressor 21 (see the solid line of the four-way switching valve 23 in fig. 1) via the gas refrigerant communication tube 5. The four-way switching valve 23 is capable of connecting the discharge side of the compressor 21 and the gas side of the indoor heat exchanger 31 via the gas refrigerant communication tube 5 during the heating operation, and connecting the gas side of the outdoor heat exchanger 24 and the suction side of the compressor 21 (see the broken line of the four-way switching valve 23 in fig. 1).
The outdoor heat exchanger 24 functions as a radiator of the refrigerant during the cooling operation or the dehumidifying operation, and functions as an evaporator of the refrigerant during the heating operation. The liquid side of the outdoor heat exchanger 24 is connected to the expansion valve 25, and the gas side is connected to the four-way switching valve 23.
The expansion valve 25 is an expansion mechanism as follows: the high-pressure liquid refrigerant having dissipated heat in the outdoor heat exchanger 24 can be decompressed before being sent to the indoor heat exchanger 31 in the cooling operation or the dehumidifying operation, and the high-pressure liquid refrigerant having dissipated heat in the indoor heat exchanger 31 can be decompressed before being sent to the outdoor heat exchanger 24 in the heating operation. Here, as the expansion valve 25, an electric expansion valve capable of opening degree control is used.
The outdoor unit 2 is provided with an outdoor fan 26, and the outdoor fan 26 sucks outdoor air into the unit, supplies the outdoor air to the outdoor heat exchanger 24, and then discharges the outdoor air to the outside of the unit. That is, the outdoor heat exchanger 24 is a heat exchanger that radiates or evaporates the refrigerant using outdoor air as a cooling source or a heating source. The outdoor fan 26 is driven to rotate by an outdoor fan motor 27.
Various sensors are provided in the outdoor unit 2. Specifically, the outdoor unit 2 is provided with a suction pressure sensor 28 that detects a suction pressure Ps of the compressor 21.
< refrigerant communication pipe >
The refrigerant communication tubes 4 and 5 are refrigerant tubes that are constructed on site when the air-conditioning apparatus 1 is installed in an installation site such as a building. One end of the liquid refrigerant communication tube 4 is connected to the expansion valve 25 side of the indoor unit 2, and the other end of the liquid refrigerant communication tube 4 is connected to the liquid side of the indoor heat exchanger 31 of the indoor unit 3. One end of the gas refrigerant communication tube 5 is connected to the four-way switching valve 23 side of the indoor unit 2, and the other end of the gas refrigerant communication tube 5 is connected to the gas side of the indoor heat exchanger 31 of the indoor unit 3.
< indoor Unit >
The indoor unit 3 is installed indoors (in a building). As described above, the indoor unit 3 is connected to the outdoor unit 2 via the liquid refrigerant communication tube 4 and the gas refrigerant communication tube 5, and constitutes a part of the refrigerant circuit 10. The indoor unit 3 mainly has an indoor heat exchanger 31 and an indoor fan 32.
Here, as the indoor unit 3, an indoor unit of a so-called ceiling-embedded type is adopted. As shown in fig. 2 and 3, the indoor unit 3 includes a housing 41 that houses constituent devices therein. The casing 41 is composed of a casing body 41a and a decorative panel 42 disposed below the casing body 41 a. As shown in fig. 2, the housing body 41a is configured to be inserted into an opening formed in the ceiling U. Also, the decorative panel 42 is configured to be embedded in an opening of the ceiling U. Here, fig. 2 is an external perspective view of the indoor unit 3. Fig. 3 is a schematic side sectional view of the indoor unit 3, and is a sectional view taken along line I-O-I of fig. 2.
The case body 41a is a box-like body having a substantially 8-sided shape in which long sides and short sides are alternately formed in a plan view, and has an opening on a lower surface thereof. The housing main body 41a has: a top plate 43 having a substantially 8-sided shape in which long sides and short sides are alternately continuous; and a side plate 44 extending downward from the peripheral edge of the top plate 43.
The decorative panel 42 is a plate-like body having a substantially polygonal shape (here, a substantially rectangular shape) in plan view that constitutes the lower surface of the casing 41, and is mainly composed of a panel main body 42a fixed to the lower end portion of the casing main body 41 a. The panel main body 42a has, at a substantially central position thereof, an intake port 45 for taking in air in the room, and a blow-out port 46 formed so as to surround the intake port 45 in a plan view and blowing out the air into the room. The suction port 45 is a substantially rectangular opening. The suction port 45 is provided with a suction grill 47 and a suction filter 48 for removing dust from the air sucked through the suction port 45. The outlet 46 has: a plurality of (4 in this case) side air outlets 46a formed along each side of the quadrangle of the panel main body 42 a; and a plurality of (4 in this case) corner blow-out ports 46b formed at the corners of the panel main body 42 a. Each of the side air outlets 46a is provided with a plurality of (4 in this case) airflow direction changing blades 49 capable of changing the airflow direction angle in the vertical direction of the air blown out into the room from each of the side air outlets. The airflow direction changing blade 49 is a plate-shaped member that extends long and narrow along the longitudinal direction of the side air outlet 46 a. The airflow direction changing blade 49 is rotatable about a longitudinal axis to change the vertical airflow direction angle.
The indoor heat exchanger 31 and the indoor fan 32 are mainly disposed inside the casing main body 41 a.
The indoor heat exchanger 31 is a heat exchanger that functions as an evaporator of the refrigerant during the cooling operation or the dehumidifying operation, and functions as a radiator of the refrigerant during the heating operation. The liquid side of the outdoor heat exchanger 31 is connected to the liquid refrigerant communication tube 4, and the gas side is connected to the gas refrigerant communication tube 5. The indoor heat exchanger 31 is a heat exchanger that is disposed in a curved manner so as to surround the periphery of the indoor fan 32 in a plan view. The indoor heat exchanger 31 performs heat exchange between the refrigerant and the indoor air sucked into the casing main body 41a by the indoor fan 32. A drain pan 31a is disposed below the indoor heat exchanger 31, and the drain pan 31a receives drain water generated by condensation of moisture in the indoor air by the indoor heat exchanger 31. The drain pan 31a is mounted on the lower portion of the housing body 41 a.
The indoor fan 32 is a fan that sucks in indoor air into the casing body 41a through the suction port 45 of the decorative panel 42 and blows out the indoor air from the casing body 41a into the room through the discharge port 46 of the decorative panel 42. That is, the indoor heat exchanger 31 is a heat exchanger that radiates or evaporates the refrigerant by using indoor air as a cooling source or a heating source. Here, as the indoor fan 32, a centrifugal fan that sucks in indoor air from below and blows it out toward the outer peripheral side in a plan view is used. The indoor fan 32 is driven and rotated by an indoor fan motor 33 provided at the center of the top plate 43 of the casing main body 41 a. Here, the indoor fan motor 33 can control the rotation speed (frequency) by an inverter or the like, and thereby can control the air volume of the indoor fan 32. Specifically, 4 air volumes, that is, the maximum air volume H, the moderate air volume M smaller than the air volume H, the small air volume L smaller than the air volume M, and the minimum air volume LL smaller than the air volume L, are prepared as the air volumes of the indoor fans 32. Here, the air volume LL is an air volume that cannot be set by an indoor person through a remote controller 60 (described later).
Various sensors are provided in the indoor unit 3. Specifically, the indoor unit 3 is provided with an indoor temperature sensor 34 and an indoor humidity sensor 35 that detect the temperature (indoor temperature Tr) and the humidity (indoor humidity Hr) of the indoor air sucked into the indoor unit 3.
(2) Control structure
Fig. 4 is a control block diagram of the air conditioner 1.
< entirety >
In order to control the operation of the constituent devices, the air conditioner 1 as a refrigeration apparatus includes a controller 6, and the controller 6 is connected to the outdoor side controller 20, the indoor side controller 30, and the remote controller 60 via a transmission line or a communication line. The outdoor-side controller 20 is provided in the indoor unit 2. The indoor-side controller 30 is provided in the indoor unit 3. The remote controller 60 is disposed indoors. Here, the control units 20 and 30 and the remote controller 60 are connected by wire via a transmission line or a communication line, but may be connected wirelessly.
< outdoor side control part >
As described above, the outdoor-side controller 20 is provided in the outdoor unit 2, and mainly includes the outdoor-side CPU 20a, the outdoor-side transmitter 20b, and the outdoor-side memory 20 c. The indoor-side control unit 20 can receive a detection signal of the suction pressure sensor 28.
The outdoor CPU 20a is connected to the outdoor transmission unit 20b and the outdoor storage unit 20 c. The heat source-side transmitter 20b transmits control data and the like to and from the indoor-side controller 30 a. The outdoor-side storage unit 20c stores control data and the like. The outdoor-side CPU 20a transmits, reads, and writes control data and the like via the outdoor-side transmission unit 20b or the outdoor-side storage unit 20c, and controls operations of the constituent devices 21, 23, 25, and 26 and the like provided in the outdoor unit 2.
< indoor side control part >
As described above, the indoor-side control unit 30 is provided in the indoor unit 3, and mainly includes the indoor-side CPU 30a, the indoor-side transmission unit 30b, the indoor-side storage unit 30c, and the indoor-side communication unit 30 d. The indoor-side controller 30 can receive detection signals from the indoor temperature sensor 34 and the indoor humidity sensor 35.
The indoor CPU 30a is connected to the indoor transfer unit 30b, the indoor storage unit 30c, and the indoor storage unit 30 d. The indoor side transmission unit 30b transmits control data and the like to and from the outdoor side control unit 20. The indoor-side storage unit 30b stores control data and the like. The indoor-side communication unit 30c transmits and receives control data and the like to and from the remote controller 60. The indoor CPU 30a performs transmission, reading, writing, and transmission/reception of control data and the like via the indoor transmission unit 30b, the indoor storage unit 30c, and the indoor communication unit 30d, and performs operation control of the constituent devices 32 and 49 and the like provided in the indoor unit 3.
< remote controller >
The remote controller 60 is installed indoors as described above, and mainly includes a remote controller CPU 61, a remote controller storage unit 62, a remote controller communication unit 63, a remote controller operation unit 64, and a remote controller display unit 65.
The remote controller CPU 61 is connected to a remote controller communication unit 62, a remote controller storage unit 63, a remote controller operation unit 64, and a remote controller display unit 65. The remote controller communication unit 62 transmits and receives control data and the like to and from the indoor side communication unit 30 c. The remote controller storage 63 stores control data and the like. The remote controller operation unit 64 receives an input of a control command or the like from a user. The remote controller display unit 65 displays operation. The remote control CPU 61 receives an input of an operation command, a control command, and the like via the remote control operation unit 64, reads and writes control data and the like in the remote control storage unit 63, displays an operation state, a control state, and the like in the remote control display unit 65, and performs a control command and the like to the indoor side control unit 30 via the remote control communication unit 62.
In this way, the air conditioner 1 as a refrigeration apparatus includes the control unit 6 that controls the operation of the constituent devices. The control unit 6 controls the constituent devices 21, 23, 25, 26, 32, 49 and the like based on detection signals of the suction pressure sensor 28, the indoor temperature sensor 34, the indoor humidity sensor 35 and the like, and can perform air conditioning operations such as a cooling operation, a dehumidifying operation, a heating operation and the like, and various controls.
(3) Basic motion
Next, basic operations (heating operation, cooling operation, and dehumidifying operation) of the air conditioner 1 will be described.
< heating operation >
In the air conditioning apparatus 1, a heating operation as an air conditioning operation can be performed. The heating operation is performed by the control unit 6, which has received the command for the heating operation via the remote controller operation unit 64, performing operation control on the constituent devices 21, 23, 25, 26, 32, 49 and the like of the outdoor unit 2 and the outdoor unit 3.
During the heating operation, the four-way switching valve 23 is switched to a state in which the outdoor heat exchanger 24 functions as an evaporator of the refrigerant and the indoor heat exchanger 31 functions as a radiator of the refrigerant (i.e., a state indicated by a broken line in the four-way switching valve 23 in fig. 1).
In the refrigerant circuit 10 in this state, the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21, compressed to a high pressure in the refrigeration cycle, and then discharged. The high-pressure refrigerant discharged from the compressor 21 is sent to the indoor heat exchanger 31 through the four-way switching valve 23 and the gas-refrigerant communication tube 5. The high-pressure refrigerant sent to the indoor heat exchanger 31 exchanges heat with the indoor air supplied by the indoor fan 32 in the indoor heat exchanger 31, and dissipates heat. Thereby, the indoor air is heated and blown into the room. The high-pressure refrigerant having radiated heat in the indoor heat exchanger 31 is sent to the expansion valve 25 through the liquid refrigerant communication tube 4, and is depressurized to a low pressure in the refrigeration cycle. The low-pressure refrigerant decompressed by the expansion valve 25 is sent to the outdoor heat exchanger 24. The low-pressure refrigerant sent to the outdoor heat exchanger 24 is evaporated in the outdoor heat exchanger 24 by heat exchange with outdoor air supplied by the outdoor fan 26. The low-pressure refrigerant evaporated in the outdoor heat exchanger 24 passes through the four-way switching valve 23 and is again sucked into the compressor 21. In this way, during the heating operation, the control unit 6 performs an operation of circulating the refrigerant sealed in the refrigerant circuit 10 in the order of the compressor 21, the indoor heat exchanger 31, the expansion valve 25, and the outdoor heat exchanger 24.
< cooling operation >
In the air conditioning apparatus 1, a cooling operation, which is an air conditioning operation, can be performed. The cooling operation is performed by the control unit 6, which has received an instruction for the cooling operation via the remote controller operation unit 64, performing operation control on the constituent devices 21, 23, 25, 26, 32, 49 and the like of the outdoor unit 2 and the outdoor unit 3.
During the cooling operation, the four-way switching valve 23 is switched to a state in which the outdoor heat exchanger 24 functions as a radiator of the refrigerant and the indoor heat exchanger 31 functions as an evaporator of the refrigerant (i.e., a state indicated by a solid line of the four-way switching valve 23 in fig. 1).
In the refrigerant circuit 10 in such a state, the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21, compressed to a high pressure in the refrigeration cycle, and then discharged. The high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 24 through the four-way switching valve 23. The high-pressure refrigerant sent to the outdoor heat exchanger 24 exchanges heat with outdoor air supplied by the outdoor fan 26 in the outdoor heat exchanger 24, and dissipates heat. The high-pressure refrigerant having radiated heat in the outdoor heat exchanger 24 is sent to the expansion valve 25, and is decompressed to a low pressure in the refrigeration cycle. The low-pressure refrigerant decompressed by the expansion valve 25 is sent to the indoor heat exchanger 31 through the liquid refrigerant communication tube 4. The low-pressure refrigerant sent to the indoor heat exchanger 31 is evaporated in the indoor heat exchanger 31 by heat exchange with the indoor air supplied by the indoor fan 32. Thereby, the indoor air is cooled and blown out into the room. The low-pressure refrigerant evaporated in the indoor heat exchanger 31 passes through the gas refrigerant communication tube 5 and the four-way switching valve 23, and is again sucked into the compressor 21. In this way, during the cooling operation, the control unit 6 performs an operation of circulating the refrigerant sealed in the refrigerant circuit 10 in the order of the compressor 21, the outdoor heat exchanger 24, the expansion valve 25, and the indoor heat exchanger 31.
< dehumidification operation >
In the air conditioning apparatus 1, a dehumidification operation as an air conditioning operation can be performed. The dehumidification operation is performed by the control unit 6, which has received the instruction of the dehumidification operation via the remote controller operation unit 64, performing operation control on the constituent devices 21, 23, 25, 26, 32, 49 and the like of the outdoor unit 2 and the outdoor unit 3.
In the dehumidification operation, as in the cooling operation, the four-way switching valve 23 is switched to a state in which the outdoor heat exchanger 24 functions as a radiator of the refrigerant and the indoor heat exchanger 31 functions as an evaporator of the refrigerant (i.e., a state indicated by a solid line of the four-way switching valve 23 in fig. 1).
In the refrigerant circuit 10 in such a state, the low-pressure refrigerant in the refrigeration cycle is sucked into the compressor 21, compressed to a high pressure in the refrigeration cycle, and then discharged. The high-pressure refrigerant discharged from the compressor 21 is sent to the outdoor heat exchanger 24 through the four-way switching valve 23. The high-pressure refrigerant sent to the outdoor heat exchanger 24 exchanges heat with outdoor air supplied by the outdoor fan 26 in the outdoor heat exchanger 24, and dissipates heat. The high-pressure refrigerant having radiated heat in the outdoor heat exchanger 24 is sent to the expansion valve 25, and is decompressed to a low pressure in the refrigeration cycle. The low-pressure refrigerant decompressed by the expansion valve 25 is sent to the indoor heat exchanger 31 through the liquid refrigerant communication tube 4. The low-pressure refrigerant sent to the indoor heat exchanger 31 is evaporated in the indoor heat exchanger 31 by heat exchange with the indoor air supplied by the indoor fan 32. Thereby, the indoor air is dehumidified and blown out into the room. The low-pressure refrigerant evaporated in the indoor heat exchanger 31 passes through the gas refrigerant communication tube 5 and the four-way switching valve 23, and is again sucked into the compressor 21. In this way, during the dehumidification operation, the control unit 6 performs an operation of circulating the refrigerant sealed in the refrigerant circuit 10 in the order of the compressor 21, the outdoor heat exchanger 24, the expansion valve 25, and the indoor heat exchanger 31.
(4) Control during cooling operation
In the cooling operation described above, the following control is performed. Fig. 5 is a flowchart of the cooling operation.
< step ST1 (Heat on) >
The control unit 6 performs capacity control for controlling the capacity of the compressor 21 so that the evaporation temperature Te of the refrigerant in the refrigerant circuit 10 becomes the target evaporation temperature Tecs, at the time of the cooling operation (the operation of operating the compressor 21 to circulate the refrigerant, i.e., the heat on period) in step ST 1. During the heat conduction period in step ST1, the control unit 6 controls the air volume of the indoor fan 32 to the set air volume (here, any one of the air volume L, the air volume M, and the air volume H) selected by the indoor person input from the remote controller operation unit 64 of the remote controller 60.
The capacity control of the compressor 21 is as follows: the capacity of the compressor 21 is increased by increasing the rotation speed (frequency) of the compressor 21 in the case where the evaporation temperature Te of the refrigerant is higher than the target evaporation temperature Tecs, and the capacity of the compressor 21 is decreased by decreasing the rotation speed (frequency) of the compressor 21 in the case where the evaporation temperature Te of the refrigerant is lower than the target evaporation temperature Tecs.
Here, the control unit 6 determines the target evaporation temperature Tecs based on the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr. Specifically, the control unit 6 determines that the target evaporation temperature Tecs is lower as the temperature difference Δ Tr is larger. The target indoor temperature Trs is set by an indoor person inputting it from the remote controller operation unit 64 of the remote controller 60. The evaporation temperature Te of the refrigerant can be obtained by converting the suction pressure Ps into the saturation temperature of the refrigerant. The evaporation temperature Te of the refrigerant is a temperature obtained by converting a pressure (evaporation pressure Pe of the refrigerant in the refrigerant circuit 10) representing a low-pressure refrigerant in the refrigeration cycle flowing during a period from the outlet of the expansion valve 25 to the suction side of the compressor 21 via the indoor heat exchanger 31 during the cooling operation into a refrigerant saturation temperature, or a refrigerant saturation temperature in the indoor heat exchanger 31 functioning as an evaporator of the refrigerant. Therefore, when a temperature sensor is provided in the indoor heat exchanger 31, the temperature of the refrigerant detected by the temperature sensor may be set to the evaporation temperature Te of the refrigerant.
Here, the state quantity of the control target in the capacity control is set to the evaporation temperature Te, but may be the evaporation pressure Pe. In this case, the control target value may be a target evaporation pressure Pecs corresponding to the target evaporation temperature Tecs. The case where the evaporation pressure Pe and the target evaporation pressure Pecs are used in this capacity control is also the same as the case where the evaporation temperature Te and the target evaporation temperature Tecs are used.
< step ST2 (determination of whether or not thermal shutdown condition is satisfied) >
During the heat on at step ST1, the control portion 6 makes a determination whether or not the heat off condition is satisfied at step ST 2.
The control unit 6 has a thermal shutdown temperature condition based on the indoor temperature Tr as a determination element for determining whether or not the thermal shutdown condition is satisfied. When the thermal shutdown temperature condition is satisfied, the control unit 6 determines that the thermal shutdown condition is satisfied, and when the thermal shutdown temperature condition is not satisfied, the control unit 6 determines that the thermal shutdown condition is not satisfied. Specifically, during the heat conduction, the indoor temperature Tr becomes low, and the controller 6 determines that the heat shutdown temperature condition is satisfied when the indoor temperature Tr is equal to or lower than the heat shutdown temperature Trcf, and determines that the heat shutdown temperature condition is not satisfied when the indoor temperature Tr is higher than the heat shutdown temperature Trcf. Here, the thermal shutdown temperature Trcf is a value obtained by adding the thermal shutdown temperature difference Δ Trcf to the target indoor temperature Trs. The thermal shutdown temperature difference Δ Trcf is set to a value of about-1 to +1 degrees.
Here, whether or not the thermal shutdown condition is satisfied is determined according to whether or not the indoor temperature Tr reaches the thermal shutdown temperature Trcf, but is not limited thereto. For example, the determination may be made based on whether or not the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr reaches the thermal shutdown temperature difference Δ Trcf, and the determination based on the temperature difference Δ Tr may be the same as the case where the determination is made based on whether or not the indoor temperature Tr reaches the thermal shutdown temperature Trcf.
< step ST3 (thermal shutdown) >
When it is determined in step ST2 that the thermal shutdown condition is satisfied because the indoor temperature Tr has become equal to or lower than the thermal shutdown temperature Trcf, the controller 6 stops the compressor 21 to stop the circulation of the refrigerant and stop the operation of the cooling operation (thermal shutdown) in step ST 3.
< step ST4 (determination of whether or not the hot-key condition is satisfied) >
During the heat-off period in step ST3, in step ST4, the controller 6 determines whether or not the heat-on condition is satisfied.
The control portion 6 has a thermal on temperature condition based on the room temperature Tr as a determination element for determining whether or not the thermal on condition is satisfied. Further, the control portion 6 determines that the heat-on condition is satisfied when the heat-on temperature condition is satisfied, and determines that the heat-on condition is not satisfied when the heat-on temperature condition is not satisfied. Specifically, during the thermal shutdown period, the indoor temperature Tr becomes high, and the controller 6 determines that the thermal conduction temperature condition is satisfied when the indoor temperature Tr becomes equal to or higher than the thermal conduction temperature Trcn, and determines that the thermal conduction temperature condition is not satisfied when the indoor temperature Tr is lower than the thermal conduction temperature Trcn. Here, the thermal conduction temperature Trcn is a value obtained by adding the thermal conduction temperature difference Δ Trcn to the target indoor temperature Trs. The thermal conduction temperature difference Δ Trcn is set to a value of about 0 degrees to +2 degrees.
Here, whether or not the heat-on condition is satisfied is determined according to whether or not the room temperature Tr reaches the heat-on temperature Trcn, but is not limited thereto. For example, the determination may be made based on whether or not the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr reaches the heat conduction temperature difference Δ Trcn, and the determination based on the temperature difference Δ Tr may be the same as the determination made based on whether or not the indoor temperature Tr reaches the heat conduction temperature Trcn.
When it is determined at step ST4 that the heat-on condition is satisfied, the process returns to step ST1, and controller 6 starts compressor 21 to perform the cooling operation (heat-on).
(5) Control during dehumidification operation
In the dehumidification operation described above, the following control is performed. Fig. 6 is a flowchart of the dehumidification operation (mode selection), and fig. 7 is a flowchart of the dehumidification operation (dehumidification operation mode L, M, H).
< step ST11 (mode selection) >
Here, in order to meet the demand of the dehumidification level of the indoor person, a plurality of dehumidification operation modes having different dehumidification levels are prepared as the dehumidification operation. Here, the dehumidification level is a level of the indoor humidity Hr desired to be obtained by the dehumidification operation, and the lower the indoor humidity Hr desired to be obtained by the dehumidification operation, the higher the dehumidification level. Specifically, as the dehumidification operation mode, 3 modes of the dehumidification operation mode L having the lowest dehumidification level, the dehumidification operation mode M having an intermediate dehumidification level higher than the dehumidification operation mode L, and the dehumidification operation mode H having a higher dehumidification level than the dehumidification operation mode M are prepared in the control unit 6. Here, the selection of the dehumidification operation mode is performed by the indoor person inputting from the remote controller operation unit 64 of the remote controller 60 in step ST 11.
< step ST12 (dehumidification operation mode L) >
When the dehumidification operation mode L is selected in step ST11, the control unit 6 performs the control of step ST12 (i.e., steps ST21 to ST 27).
Step ST21 (thermal switch-on)
In the operation of the dehumidification operation (the operation of operating the compressor 21 to circulate the refrigerant, i.e., the heat on period) in step ST21, the controller 6 performs capacity control to control the capacity of the compressor 21 so that the evaporation temperature Te of the refrigerant in the refrigerant circuit 10 becomes the target evaporation temperature Teds. In the heat conduction period in step ST21, the controller 6 performs air volume control for limiting the air volume of the indoor fan 32 to the air volume L or the air volume LL, unlike in step ST1 during the cooling operation.
The capacity control of the compressor 21 is similar to step ST1 in the cooling operation except that the target evaporation temperature Tecs is set to the target evaporation temperature Teds. Therefore, here, the description of the capacity control of the compressor 21 is omitted. Here, the target evaporation temperature Teds is set to a value equal to or lower than the target evaporation temperature Tecs.
Step ST22 (determination 1 of whether the thermal shutdown condition is satisfied)
During the heat on at step ST21, the control portion 6 makes a determination whether or not the heat off condition is satisfied at step ST 22.
The control unit 6 has a 1 st thermal shutdown temperature condition based on the indoor temperature Tr and a thermal shutdown humidity condition based on the indoor humidity Hr as determination elements for determining whether or not the thermal shutdown condition is satisfied. The control unit 6 determines that the thermal shutdown condition is satisfied when both the 1 st thermal shutdown temperature condition and the thermal shutdown humidity condition are satisfied, and determines that the thermal shutdown condition is not satisfied when one or both of the 1 st thermal shutdown temperature condition and the thermal shutdown humidity condition are not satisfied. That is, in the dehumidification operation mode L, unlike step ST2 during the cooling operation, whether or not the heat shutdown condition is satisfied is determined in consideration of not only the heat shutdown temperature condition but also the heat shutdown humidity condition.
Specifically, during the heat conduction, the indoor temperature Tr becomes low, and the controller 6 determines that the 1 st heat-off temperature condition is satisfied when the state where the indoor temperature Tr reaches the 1 st heat-off temperature TrdfL1 or less continues for the predetermined time tL, and determines that the 1 st heat-off temperature condition is not satisfied when the indoor temperature Tr is higher than the 1 st heat-off temperature TrdfL1 or when the state where the indoor temperature Tr reaches the 1 st heat-off temperature TrdfL1 or less does not continue for the predetermined time tL. Here, the 1 st heat shut-off temperature TrdfL1 is a value obtained by adding the 1 st heat shut-off temperature difference Δ TrdfL1 to the target indoor temperature Trs. The 1 st heat-off temperature difference Δ TrdfL1 is set to a value of about-1 degree to +1 degree, and the prescribed time tL is set to a value of about several tens of seconds to several minutes. The 1 st heat shutdown temperature TrdfL1 (the target indoor temperature Trs + the 1 st heat shutdown temperature difference Δ TrdfL1) may be the same as or lower than the heat shutdown temperature Trcf during the cooling operation.
During the heat on period, the indoor humidity Hr becomes low, and the control unit 6 determines that the heat off humidity condition is satisfied when the indoor humidity Hr reaches the target indoor humidity HrsL, and determines that the heat off humidity condition is not satisfied when the indoor humidity Hr is higher than the target indoor humidity HrsL. Here, when the dehumidification operation mode L is selected in step ST11, the target indoor humidity HrsL is set to a low dehumidification level value (i.e., a high relative humidity value) of about 60% to 70%.
Here, whether or not the thermal shutdown condition is satisfied is determined based on whether or not the indoor temperature Tr reaches the 1 st thermal shutdown temperature TrdfL1 and whether or not the indoor humidity Hr reaches the target indoor humidity HrsL, but the present invention is not limited thereto. For example, the determination may be made based on whether or not the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr reaches the 1 st heat-off temperature difference Δ TrdfL1 and whether or not the humidity difference Δ Hr obtained by subtracting the target indoor humidity Hrs from the indoor humidity Hr reaches 0 (zero). The determination based on the temperature difference Δ Tr and the humidity difference Δ Hr is also the same as the case where the determination is made based on whether the indoor temperature Tr reaches the 1 st heat shutdown temperature TrdfL1 and whether the indoor humidity Hr reaches the target indoor humidity HrsL.
Step ST23 (thermal shutdown) -
When the indoor humidity Hr reaches the target indoor humidity HrsL and it is determined that the thermal shutdown condition is satisfied when the state in which the indoor temperature Tr has reached the 1 ST thermal shutdown temperature TrdfL1 or less continues for the predetermined time tL in step ST22, the controller 6 stops the compressor 21 to stop the circulation of the refrigerant and stop the operation of the dehumidifying operation (thermal shutdown) in step ST 23. In step ST27 (described later), the controller 6 also performs thermal shutdown when it is determined that the thermal shutdown condition is satisfied because the indoor temperature Tr has reached the 2 nd thermal shutdown temperature TrdfL2 or less.
Step ST24 (determination of whether the heat-on condition is satisfied)
During the heat-off period in step ST23, in step ST24, the controller 6 determines whether or not the heat-on condition is satisfied.
As a determination element for determining whether or not the heat-on condition is satisfied, the controller 6 has a heat-on temperature condition based on the indoor temperature Tr, as in step ST4 during the cooling operation. Further, the control portion 6 determines that the heat-on condition is satisfied when the heat-on temperature condition is satisfied, and determines that the heat-on condition is not satisfied when the heat-on temperature condition is not satisfied. Specifically, during the thermal shutdown period, the indoor temperature Tr becomes high, and the controller 6 determines that the thermal conduction temperature condition is satisfied when the indoor temperature Tr becomes equal to or higher than the thermal conduction temperature TrdnL, and determines that the thermal conduction temperature condition is not satisfied when the indoor temperature Tr is lower than the thermal conduction temperature TrdnL. Further, the heat conduction temperature TrdnL is a value obtained by adding the heat conduction temperature difference Δ TrdnL to the target indoor temperature Trs. The heat conduction temperature difference Δ TrdnL may be the same as the heat conduction temperature Trcn during the cooling operation (target indoor temperature Trs + heat conduction temperature difference Δ Trcn), or may be a value lower than the heat conduction temperature Trcn during the cooling operation.
Here, whether or not the heat-on condition is satisfied is determined according to whether or not the room temperature Tr reaches the heat-on temperature TrdnL, but is not limited thereto. For example, the determination may be made based on whether or not the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr reaches the heat conduction temperature difference Δ TrdnL, and the determination based on the temperature difference Δ Tr may be the same as the determination made based on whether or not the indoor temperature Tr reaches the heat conduction temperature TrdnL.
When it is determined at step ST24 that the heat-on condition is satisfied, the process returns to step ST21, and the controller 6 starts the compressor 21 to perform the dehumidifying operation (heat-on).
Step ST25 (determination 2 of whether the thermal shutdown condition is satisfied)
In the case where the thermal shutdown condition (both the 1 ST thermal shutdown temperature condition and the thermal shutdown humidity condition) of step ST22 is not satisfied during the thermal turn-on of step ST21, the control portion 6 determines whether or not the 1 ST thermal shutdown temperature condition is satisfied but the thermal shutdown humidity condition is not satisfied in step ST 25. That is, the control unit 6 determines whether or not the thermal shutdown humidity condition is not satisfied when the 1 st thermal shutdown temperature condition is satisfied. When the 1 ST thermal shutdown temperature condition is satisfied but the thermal shutdown humidity condition is not satisfied, the control unit 6 does not perform thermal shutdown and performs the dehumidification continuation control of step ST 26.
Step ST26 (Heat-on, dehumidification continuation control) -
In step ST26, the control unit 6 continues the capacity control for controlling the capacity of the compressor 21 and the air volume control of the indoor fan 32 so that the evaporation temperature Te of the refrigerant in the refrigerant circuit 10 becomes the target evaporation temperature Teds. However, unlike the capacity control and the air volume control in step ST21, the control unit 6 controls the capacity of the compressor 21 and the air volume of the indoor fan 32 such that the evaporation temperature Te of the refrigerant in the indoor heat exchanger 31 is lower than the dew-point temperature Trw of the indoor air. Here, the air volume of the indoor fan 32 is controlled to the minimum air volume LL, and control is performed to reduce the capacity of the compressor 21 in a range where the evaporation temperature Te is lower than the dew-point temperature Trw.
Here, the control unit 6 determines the target evaporation temperature Teds based on the dew-point temperature Trw. Specifically, the controller 6 calculates the dew point temperature Trw from the indoor temperature Tr and the indoor humidity Hr. Then, the control unit 6 determines the target evaporation temperature Teds by subtracting the predetermined temperature difference Δ Trw from the calculated dew point temperature Trw. That is, the control unit 6 determines the target evaporation temperature Teds to be lower than the dew point temperature Trw.
Then, the dehumidification in the room is continued by the dehumidification continuation control, and when the room humidity Hr reaches the target room humidity HrsL, the controller 6 determines that the thermal shutdown condition is satisfied because both the 1 ST thermal shutdown temperature condition and the thermal shutdown humidity condition are satisfied in step ST22, and performs the thermal shutdown in step ST 23.
Step ST27 (determination 3 of whether the thermal shutdown condition is satisfied)
If the thermal shutdown condition (both the 1 ST thermal shutdown temperature condition and the thermal shutdown humidity condition) of step ST22 is not satisfied during the dehumidification continuation control of step ST26, the control unit 6 determines whether or not the thermal shutdown condition is satisfied because the 2 nd thermal shutdown temperature condition is satisfied even if the thermal shutdown humidity condition is not satisfied in step ST 27.
The control unit 6 further has a 2 nd thermal shutdown temperature condition on the lower temperature side than the 1 st thermal shutdown temperature condition as a determination element for determining whether or not the thermal shutdown condition is satisfied. Then, when the 2 nd thermal shutdown temperature condition is satisfied even if the thermal shutdown humidity condition is not satisfied, the control unit 6 determines that the thermal shutdown condition is satisfied, and when the thermal shutdown humidity condition and the 2 nd thermal shutdown temperature condition are not satisfied, the control unit 6 determines that the thermal shutdown condition is not satisfied. That is, during the dehumidification continuation control at step ST26, it is determined at step ST22 whether not only both the 1 ST thermal shutdown temperature condition and the thermal shutdown humidity condition are satisfied, but also whether the 2 nd thermal shutdown temperature condition is satisfied.
Specifically, during the dehumidification continuation control, the indoor temperature Tr further decreases, and the controller 6 determines that the 2 nd heat-off temperature condition is satisfied when the indoor temperature Tr reaches the 2 nd heat-off temperature TrdfL2 or less, and determines that the 2 nd heat-off temperature condition is not satisfied when the indoor temperature Tr is higher than the 2 nd heat-off temperature TrdfL 2. Here, the 2 nd heat off temperature TrdfL2 is a value obtained by adding the 2 nd heat off temperature difference Δ TrdfL2 to the target indoor temperature Trs. Also, the 2 nd thermal shutdown temperature difference Δ TrdfL2 is set to a value lower than the 1 st thermal shutdown temperature TrdfL1 (for example, a value of about-3 degrees to-2 degrees).
Here, whether or not the thermal shutdown condition is satisfied is determined based on whether or not the indoor temperature Tr reaches the 2 nd thermal shutdown temperature TrdfL2, but the present invention is not limited to this. For example, the determination may be made based on whether or not the temperature difference Δ Tr obtained by subtracting the target indoor temperature Trs from the indoor temperature Tr reaches the 2 nd heat-off temperature difference Δ TrdfL 2. The determination based on the temperature difference Δ Tr is also the same as the case where the determination is made based on whether or not the indoor temperature Tr reaches the 2 nd heat shutdown temperature TrdfL 2.
< step ST13 (dehumidification operation mode M) >
When the dehumidification operation mode M is selected in step ST11, the control unit 6 performs the control of step ST13 (i.e., steps ST31 to ST 37).
Here, the processing in steps ST31 to ST37 in the dehumidification operation mode M is the same as the processing in steps ST21 to ST27 in the dehumidification operation mode L. Therefore, the explanation of steps ST31 to ST37 is omitted here by replacing the character "L" in the explanation of steps ST21 to ST27 in the dehumidification operation mode L with "M" and replacing steps ST21 to ST27 with steps ST31 to ST 37.
However, when the dehumidification operation mode M is selected in step ST11, the target indoor humidity HrsM is set to a value lower than the target indoor humidity HrsL in the dehumidification operation mode L (for example, a moderate relative humidity value of about 50% to 60%).
In the dehumidification operation mode M, the 1 st heat shutdown temperature TrdfM1 (the 1 st heat shutdown temperature difference Δ TrdfM1) may be set to the same value as the 1 st heat shutdown temperature TrdfL1 (the 1 st heat shutdown temperature difference Δ TrdfL1) in the dehumidification operation mode L, but may be set to a value lower than the 1 st heat shutdown temperature TrdfL1 in the dehumidification operation mode L (for example, the 1 st heat shutdown temperature difference Δ TrdfM1 may be set to a value of about-1.5 degrees to +0.5 degrees). The predetermined time tM may be the same as the predetermined time tL in the dehumidification operation mode L, but may be longer than the predetermined time tL in the dehumidification operation mode L. The heat conduction temperature TrdnM (the target indoor temperature Trs + the heat conduction temperature difference Δ TrdnM) may be set to the same value as the heat conduction temperature TrdnL in the dehumidification operation mode L (the target indoor temperature Trs + the heat conduction temperature difference Δ TrdnL), but may be set to a value lower than the heat conduction temperature TrdnL in the dehumidification operation mode L. The 2 nd heat shut-off temperature TrdfM2 (i.e., the target indoor temperature Trs + the 2 nd heat shut-off temperature difference Δ TrdfM2) may be set to the same value as the 2 nd heat shut-off temperature TrdfL2 in the dehumidification operation mode L (i.e., the target indoor temperature Trs + the 2 nd heat shut-off temperature difference Δ TrdfL2), but may be set to a value lower than the 2 nd heat shut-off temperature TrdfL2 in the dehumidification operation mode L (e.g., the 2 nd heat shut-off temperature difference Δ TrdfM2 may be set to a value of about-3.5 degrees to-2.5 degrees).
< step ST14 (dehumidification operation mode H) >
When the dehumidification operation mode H is selected in step ST11, the control unit 6 performs the control of step ST14 (i.e., steps ST41 to ST 47).
Here, the processing in steps ST41 to ST47 in the dehumidification operation mode H is the same as the processing in steps ST21 to ST27 in the dehumidification operation mode L. Therefore, the explanation of steps ST41 to ST47 is omitted here by replacing the character "L" in the explanation of steps ST21 to ST27 in the dehumidification operation mode L with "H" and replacing steps ST21 to ST27 with steps ST41 to ST 47.
However, when the dehumidification operation mode H is selected in step ST11, the target indoor humidity HrsH is set to a value lower than the target indoor humidities HrsL and HrsM in the dehumidification operation mode L, M (for example, a relatively low relative humidity value of about 40% to 50%).
In the dehumidification operation mode H, the 1 st heat shutdown temperature TrdfH1 (the 1 st heat shutdown temperature difference Δ TrdfH1) may be set to the same value as the 1 st heat shutdown temperatures TrdfL1 and TrdfM1 (the 1 st heat shutdown temperature differences Δ TrdfL1 and Δ TrdfM1) in the dehumidification operation mode L, M, but may be set to a value lower than the 1 st heat shutdown temperatures TrdfL1 and TrdfM1 in the dehumidification operation mode L, M (for example, the 1 st heat shutdown temperature difference Δ TrdfH1 is a value of about-2 degrees to 0 degrees). The predetermined time tH may be set to the same value as the predetermined times tL and tM in the dehumidification operation mode L, M, but may be set to a value longer than the predetermined times tL and tM in the dehumidification operation mode L, M. The heat conduction temperature TrdnH (the target indoor temperature Trs + the heat conduction temperature difference Δ TrdnH) may be set to the same value as the heat conduction temperatures TrdnL and TrdnM (the target indoor temperature Trs + the heat conduction temperature difference Δ TrdnL and Δ TrdnM) in the dehumidification operation mode L, M, but may be set to a value lower than the heat conduction temperatures TrdnL and TrdnM in the dehumidification operation mode L, M. The 2 nd hot off temperature TrdfH2 (the target indoor temperature Trs + the 2 nd hot off temperature difference Δ TrdfH2) may be set to the same values as the 2 nd hot off temperatures TrdfL2 and TrdfM2 (the target indoor temperature Trs + the 2 nd hot off temperature difference Δ TrdfL2 and Δ TrdfM2) in the dehumidification operation mode L, M, but may be set to a value lower than the 2 nd hot off temperatures TrdfL2 and TrdfM2 in the dehumidification operation mode L, M (for example, the 2 nd hot off temperature difference Δ TrdfH2 may be a value of about-4 degrees to-3 degrees).
(6) Feature(s)
Next, the features of the air conditioner 1 will be described.
＜A＞
In the air conditioner 1 performing the dehumidification operation, even during the dehumidification operation, if the heat shutdown is performed at the time when the indoor temperature Tr approaches the target indoor temperature Trs and the indoor temperature Tr reaches the heat shutdown temperature, as in the cooling operation (the processing of steps ST1 to ST 4), the dehumidification in the room becomes insufficient, and the dehumidification in the room may be insufficient, which may cause discomfort to the indoor person. In particular, in a transient operation state in which the target indoor temperature Trs is set high and the dehumidification operation is started, the heat shut-down is performed immediately after the start of the dehumidification operation, and thus insufficient dehumidification in the room tends to occur. Further, since the temperature of the indoor heat exchanger 31 increases during the hot-off period, the dew condensation water may evaporate again, and the indoor humidity Hr may increase.
Therefore, as described above, when the 1 ST thermal shutdown temperature condition (thermal shutdown temperature condition) is satisfied but the thermal shutdown humidity condition is not satisfied, the controller 6 controls the capacity of the compressor 21 and the air volume of the indoor fan 32 so that the evaporation temperature Te of the refrigerant in the indoor heat exchanger 31 is lower than the dew point temperature Trw of the indoor air, without stopping the compressor 21 (see the dehumidification continuation control, steps ST26, ST36, and ST 46).
Thus, in this state, the indoor dehumidification can be continued with condensation of the indoor air reliably occurring in the indoor heat exchanger 31. Therefore, compared to the case where the thermal shutdown is performed when the thermal shutdown temperature condition is satisfied, the dehumidification amount can be increased, and the possibility that the indoor person feels uncomfortable due to insufficient dehumidification in the room can be reduced.
In particular, here, the control unit 6 controls the air volume of the indoor fan 32 to the minimum air volume LL and performs control to reduce the capacity of the compressor 21 in a range where the evaporation temperature Te is lower than the dew-point temperature Trw.
Thus, since the flow rate of the refrigerant and the air volume of the indoor air that are heat-exchanged in the indoor heat exchanger 31 are reduced, the heat exchange between the refrigerant and the indoor air can be suppressed. Therefore, it is possible to suppress a decrease in the indoor temperature Tr and reduce the possibility that the indoor temperature Tr is too low and causes discomfort to the indoor person.
＜B＞
Here, as described above, the controller 6 is configured to be able to select a plurality of dehumidification operation modes having different dehumidification levels as the dehumidification operation (see steps ST11 to ST 14).
Thus, the dehumidification operation can be performed in accordance with the demand of the dehumidification level of the indoor person.
＜C＞
Here, as described above, the control unit 6 changes the 1 ST thermal shutdown temperature condition (thermal shutdown temperature condition) to the low temperature side as the dehumidification level of the selected dehumidification operation mode is higher (see steps ST22, ST32, ST42, ST25, ST35, and ST 45). Specifically, the heat shut-off temperature difference is set to a low value in the order of the dehumidification operation mode L, M, H (i.e., Δ TrdfL1 > Δ TrdfM1 > Δ TrdfH1), and thus the heat shut-off temperature is set to a low value in the order of the dehumidification operation mode L, M, H (i.e., TrdfL1 > TrdfM1 > TrdfH 1).
Accordingly, here, the higher the dehumidification level is, the more difficult the thermal shutdown temperature condition is satisfied, and therefore, the dehumidification amount can be increased until the thermal shutdown temperature condition is satisfied.
Here, the control unit 6 may change the heat shutdown temperature condition during the dehumidification operation to a lower temperature side than the heat shutdown temperature condition during the cooling operation. Specifically, the heat shut-off temperature differences Δ TrdfL1, Δ TrdfM1, and Δ TrdfH1 during the dehumidification operation are set to values lower than the heat shut-off temperature difference Δ Trcf during the cooling operation. This can facilitate dehumidification of the room as compared with the cooling operation.
＜D＞
However, since the dehumidification is continued after the 1 st heat shutdown temperature condition (heat shutdown temperature condition) described above is satisfied, there is a possibility that the indoor temperature Tr may be excessively low. For example, the heat shutdown humidity condition is not satisfied even if the dehumidification is continued after the heat shutdown temperature condition is satisfied. In such a case, the indoor temperature Tr is too low, and therefore, the indoor person may feel uncomfortable.
Therefore, here, as described above, the control unit 6 further has the 2 nd thermal shutdown temperature condition on the lower temperature side than the 1 st thermal shutdown temperature condition (thermal shutdown temperature condition) as a determination element for determining whether or not the thermal shutdown condition is satisfied. Even if the thermal shutdown humidity condition is not satisfied, the controller 6 determines that the thermal shutdown condition is satisfied when the 2 nd thermal shutdown temperature condition on the low temperature side is satisfied (see steps ST27, ST37, and ST 47).
Thus, by continuing the dehumidification after the 1 ST thermal shutdown temperature condition is satisfied, the thermal shutdown can be performed before the indoor temperature Tr becomes too low (see steps ST23, ST33, and ST 43). Therefore, by continuing to perform dehumidification after the 1 st heat shutdown temperature condition is satisfied to increase the amount of dehumidification, it is possible to reduce the possibility that the indoor person feels uncomfortable due to insufficient dehumidification in the room, and it is possible to suppress excessive continuous dehumidification after the 1 st heat shutdown temperature condition is satisfied, thereby reducing the possibility that the indoor person feels uncomfortable due to too low indoor temperature Tr.
＜E＞
Here, as described above, the controller 6 determines that the 2 nd thermal shutdown temperature condition is satisfied at the time when the indoor temperature Tr reaches the 2 nd thermal shutdown temperatures TrdfL2, TrdfM2, and TrdfH2 that are lower than the 1 ST thermal shutdown temperatures TrdfL1, TrdfM1, and TrdfH1 (see steps ST27, ST37, and ST 47).
Thus, since the thermal shutdown is performed at the time when the indoor temperature Tr reaches the 2 nd thermal shutdown temperature TrdfL2, TrdfM2, TrdfH2, the possibility that the indoor temperature Tr becomes too low can be reduced.
＜F＞
As described above, the control unit 6 changes the 2 nd hot off temperature condition to the low temperature side as the dehumidification level of the selected dehumidification operation mode is higher (see steps ST27, ST37, and ST 47). Specifically, the 2 nd hot off temperature difference is set to a low value in the order of the dehumidification operation mode L, M, H (i.e., Δ TrdfL2 > Δ TrdfM2 > Δ TrdfH2), whereby the 2 nd hot off temperature is set to a low value in the order of the dehumidification operation mode L, M, H (i.e., TrdfL2 > TrdfM2 > TrdfH 2).
Accordingly, here, the higher the dehumidification level is, the less likely the 2 nd heat shutdown temperature condition is satisfied, and therefore, the dehumidification amount can be increased until the 2 nd heat shutdown temperature condition is satisfied.
＜G＞
Here, as described above, the controller 6 determines that the 1 ST thermal shutdown temperature condition is satisfied when the indoor temperature Tr reaches the 1 ST thermal shutdown temperatures TrdfL1, TrdfM1, and TrdfH1 continuously continue for the predetermined times tL, tM, and tH (see steps ST22, ST32, ST42, ST25, ST35, and ST 45).
Here, the dehumidification amount can be increased even until the 1 st thermal shutdown temperature condition is satisfied, as compared with a case where the 1 st thermal shutdown temperature condition is determined to be satisfied at the time when the indoor temperature Tr reaches the 1 st thermal shutdown temperature TrdfL1, TrdfM1, TrdfH 1. In addition, it is possible to prevent erroneous determination as to whether or not the 1 st thermal shutdown temperature condition is satisfied.
Here, the control unit 6 may extend the predetermined time as the dehumidification level of the selected dehumidification operation mode is higher (see steps ST22, ST32, ST42, ST25, ST35, and ST 45). Specifically, the predetermined time is set to a longer value (tL < tM < tH) in the order of the dehumidification operation mode L, M, H.
Accordingly, here, the higher the dehumidification level is, the less likely the 1 st heat shutdown temperature condition is satisfied, and therefore, the dehumidification amount can be increased until the 1 st heat shutdown temperature condition is satisfied.
(7) Modification example
＜A＞
In the above embodiment, in the dehumidification continuation control in steps ST26, ST36, and ST46, the controller 6 performs control to reduce the capacity of the compressor 21 in the range in which the evaporation temperature Te is lower than the dew point temperature Trw. Specifically, the control unit 6 determines the target evaporation temperature Teds by subtracting the predetermined temperature difference Δ Trw from the dew-point temperature Trw, and controls the capacity of the compressor 21 so that the evaporation temperature Te becomes the target evaporation temperature Teds.
However, in the capacity control of the compressor 21, when the target evaporation temperature Teds is set to be low, the capacity of the compressor 21 is controlled to be large, and not only does dehumidification in the room be promoted, but the room temperature Tr is also easily lowered.
Therefore, in the dehumidification continuation control at steps ST26, ST36, and ST46, the control of reducing the capacity of the compressor 21 is performed until it is determined that the indoor temperature Tr has increased.
Specifically, as shown in fig. 8, the control unit 6 changes the predetermined temperature difference Δ Trw to be smaller in step ST52 until it is determined in step ST51 that the room temperature Tr has increased, thereby increasing the target evaporation temperature Teds to a level lower than the dew point temperature Trw and controlling the capacity of the compressor 21.
Thus, the flow rate of the refrigerant that exchanges heat in the indoor heat exchanger 31 can be reduced to a flow rate at which dehumidification is performed without lowering the indoor temperature Tr, and the possibility that the indoor person feels uncomfortable can be further reduced. Also, the frequency of thermal shutdown can be reduced.
＜B＞
In the above-described embodiment and modification a, in the dehumidification continuation control in steps ST26, ST36, and ST46, the controller 6 performs control to reduce the capacity of the compressor 21 in the range in which the evaporation temperature Te is lower than the dew-point temperature Trw. Specifically, the control unit 6 determines the target evaporation temperature Teds by subtracting the predetermined temperature difference Δ Trw from the dew-point temperature Trw, and controls the capacity of the compressor 21 so that the evaporation temperature Te becomes the target evaporation temperature Teds.
However, if the target evaporation temperature Teds is set low, there is a possibility that the indoor air is excessively cooled in the indoor heat exchanger 31, and condensation may occur near the air outlet 46 of the indoor unit 3 housing the indoor heat exchanger 31.
Therefore, in the dehumidification continuation control in steps ST26, ST36, and ST46, the controller 6 performs control to reduce the capacity of the compressor 21 in a range of the lower limit Tem of the evaporation temperature Te or more.
Specifically, as shown in fig. 9, first, in step ST53, the controller 6 determines the lower limit Tem based on the indoor temperature Tr and the indoor humidity Hr. Here, the lower limit Tem is determined from the viewpoint of not causing condensation in the vicinity of the air outlet 46 of the indoor unit 3 regardless of the degree to which the evaporation temperature Te is lowered, from the viewpoint of the indoor temperature Tr and the indoor humidity Hr. Therefore, the lower limit Tem is determined to be low because condensation is less likely to occur when the indoor temperature Tr is low or the indoor humidity Hr is low, and is determined to be high because condensation is likely to occur when the indoor temperature Tr is high or the indoor humidity Hr is high. Next, the control unit 6 determines whether or not the target evaporation temperature Teds is equal to or greater than the lower limit Tem in step ST 54. When it is determined at step ST54 that the target evaporation temperature Teds is not lower than the lower limit value Tem or more, the controller 6 changes the predetermined temperature difference Δ Trw to be small at step ST55, increases the target evaporation temperature Teds within a range lower than the dew-point temperature Trw, and controls the capacity of the compressor 21.
Thus, by performing control to reduce the capacity of the compressor 21 in the range of the lower limit value Tem of the evaporation temperature Te or more, it is possible to reduce the possibility of condensation occurring near the outlet 46 of the indoor unit 3 due to excessive cooling of the indoor air in the indoor heat exchanger 31.
When the dehumidification operation is performed, since the indoor humidity Hr is gradually decreased by performing the indoor dehumidification, the possibility of the occurrence of dew condensation near the air outlet 46 of the indoor unit 3 tends to be gradually reduced. Here, in step ST53, the control unit 6 determines the lower limit Tem based on the indoor temperature Tr and the indoor humidity Hr, and therefore, the lower limit Tem decreases while the dehumidification continuation control is being performed. That is, here, the control unit 6 lowers the lower limit Tem of the evaporation temperature Te during the dehumidification operation.
Thus, the range in which the evaporation temperature Te is reduced can be expanded, and the evaporation temperature Te can be reliably lowered below the dew-point temperature Trw. In particular, since the range in which the evaporation temperature Te is reduced can be expanded in consideration of the indoor temperature Tr and the indoor humidity Hr, the occurrence of dew condensation can be suppressed as much as possible.
＜C＞
In the above-described embodiment and modification A, B, 3 dehumidification operation modes L, M, H can be selected as the plurality of dehumidification operation modes having different dehumidification levels, but the present invention is not limited to this, and 2 dehumidification operation modes may be used, or 4 or more dehumidification operation modes may be used.
＜D＞
In the above-described embodiment and modifications a to C, the example in which the ceiling-embedded type is adopted as the indoor unit 3 housing the indoor heat exchanger 31 has been described, but the present invention is not limited thereto, and may be an indoor unit of another type such as a wall-mounted type.
While the embodiments of the present disclosure have been described above, it is to be understood that various changes in the form and details may be made therein without departing from the spirit and scope of the present disclosure as set forth in the appended claims.
Industrial applicability
The present disclosure can be widely applied to an air conditioner that performs a dehumidification operation.
Description of the reference symbols
1: an air conditioning device; 6: a control unit; 10: a refrigerant circuit; 21: a compressor; 24: an outdoor heat exchanger;
25: an expansion valve (expansion mechanism); 31: an indoor heat exchanger; 32: an indoor fan.
Documents of the prior art
Patent document
Patent document 1: japanese laid-open patent publication No. 2004-76973

Claims (6)

1. An air conditioning device (1), the air conditioning device (1) comprising:
a refrigerant circuit (10) configured by connecting a compressor (21), an outdoor heat exchanger (24), an expansion mechanism (25), and an indoor heat exchanger (31);
an indoor fan (32) that sends indoor air to the indoor heat exchanger; and
a control unit (6) that performs a dehumidification operation in which the refrigerant sealed in the refrigerant circuit is circulated in the order of the compressor, the outdoor heat exchanger, the expansion mechanism, and the indoor heat exchanger,
the control unit stops the compressor when a predetermined thermal shutdown condition is satisfied during the dehumidification operation,
the control unit has a thermal shutdown temperature condition based on an indoor temperature and a thermal shutdown humidity condition based on an indoor humidity as determination elements for determining whether or not the thermal shutdown condition is satisfied,
in the dehumidification operation, the control unit controls the capacity of the compressor and the air volume of the indoor fan so that the evaporation temperature of the refrigerant in the indoor heat exchanger is lower than the dew point temperature of the indoor air without stopping the compressor when the hot-off temperature condition is satisfied but the hot-off humidity condition is not satisfied,
the control unit is configured to be able to select a plurality of dehumidification operation modes having different dehumidification levels as the dehumidification operation,
the control unit changes the heat shut-off temperature condition to a lower temperature side as the dehumidification level of the selected dehumidification operation mode is higher.
2. The air conditioner according to claim 1,
the control unit performs the following control: controlling an air volume of the indoor fan to a minimum air volume, and reducing a capacity of the compressor in a range where the evaporation temperature is lower than the dew point temperature.
3. The air conditioner according to claim 2,
the control unit performs the following control: reducing a capacity of the compressor until the indoor temperature rises.
4. The air conditioner according to claim 2 or 3,
the control unit performs the following control: and reducing the capacity of the compressor in a range of the lower limit value of the evaporation temperature or more.
5. The air conditioner apparatus according to claim 4,
the control unit reduces the lower limit value of the evaporation temperature during the dehumidification operation.
6. The air conditioner apparatus according to claim 5,
the control unit determines a lower limit value of the evaporation temperature based on the indoor temperature and the indoor humidity.
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