CN114608075A - Temperature-adjusting dehumidifying air-conditioning system and control method thereof - Google Patents
Temperature-adjusting dehumidifying air-conditioning system and control method thereof Download PDFInfo
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- CN114608075A CN114608075A CN202210278448.4A CN202210278448A CN114608075A CN 114608075 A CN114608075 A CN 114608075A CN 202210278448 A CN202210278448 A CN 202210278448A CN 114608075 A CN114608075 A CN 114608075A
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0083—Indoor units, e.g. fan coil units with dehumidification means
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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
- F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
- F24F1/0007—Indoor units, e.g. fan coil units
- F24F1/0059—Indoor units, e.g. fan coil units characterised by heat exchangers
- F24F1/0063—Indoor units, e.g. fan coil units characterised by heat exchangers by the mounting or arrangement of the heat exchangers
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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
- F24F11/62—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/87—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
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- 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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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- 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
- F25B31/00—Compressor arrangements
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- 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
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
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- 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
- F25B39/00—Evaporators; Condensers
- F25B39/04—Condensers
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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- 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
- F25B41/00—Fluid-circulation arrangements
- F25B41/30—Expansion means; Dispositions thereof
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- 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
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/04—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases
- F25B43/043—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for withdrawing non-condensible gases for compression type systems
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/10—Temperature
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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
- F24F2110/00—Control inputs relating to air properties
- F24F2110/20—Humidity
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Abstract
The invention provides a temperature-regulating dehumidifying air-conditioning system and a control method thereof, wherein the temperature-regulating dehumidifying air-conditioning system comprises an indoor side heat exchange set, an indoor first heat exchanger and an indoor second heat exchanger of the indoor side heat exchange set, a first throttling element is arranged on a first trunk between the indoor side heat exchange set and an outdoor heat exchanger, a second throttling element is arranged on a second trunk, and when in a refrigeration mode, a refrigerant flows out of the outdoor heat exchanger and then flows back into a compressor through the indoor first heat exchanger and the indoor second heat exchanger in parallel; in the heating mode, the refrigerant flows out of the indoor first heat exchanger and the indoor second heat exchanger in parallel and then flows back into the compressor through the outdoor heat exchanger; in the reheating and dehumidifying mode, the refrigerant flows out through the outdoor heat exchanger and the indoor second heat exchanger in parallel and then flows back into the compressor through the indoor first heat exchanger. According to the invention, when dehumidification is needed in transitional seasons, the distribution of condensation load and the regulation of indoor outlet air temperature can be realized, the comfort is obviously improved, and the energy consumption is reduced.
Description
Technical Field
The invention belongs to the technical field of air conditioning, and particularly relates to a temperature-adjusting and dehumidifying air-conditioning system and a control method thereof.
Background
The household variable frequency air conditioner is popularized in China and is used for refrigerating and dehumidifying in summer. In order to meet the dehumidification requirement, the evaporation temperature of the air conditioner is usually lower than the dew point temperature of return air; in order to meet the requirement of comfort, the return air temperature is not too low. When the household variable frequency air conditioner operates in low-load refrigeration, the evaporation temperature is usually higher, in order to realize dehumidification, the air quantity of the indoor unit needs to be reduced, so that the evaporation temperature is reduced to achieve the purpose of dehumidification, and at the moment, the refrigeration energy efficiency ratio and the unit energy consumption dehumidification amount are both reduced.
In the middle and lower reaches of Yangtze river and areas in south of China, the relative humidity is high in transitional seasons (without air conditioning and refrigeration), and particularly in the 'plum rain season' and 'return south' period, dehumidification is needed to solve the comfort and health problems caused by humidity. When the conventional household variable frequency air conditioner performs refrigeration and dehumidification in a transition season, the indoor return air temperature and the return air dew point are gradually reduced, and the indoor relative humidity is not reduced or even increased after being reduced to a certain degree, so that the indoor cooling is realized and the indoor cooling is not dry; on the other hand, the reduction in the evaporating temperature and the return air dew point leads to a significant reduction in the unit energy consumption dehumidification capacity of the air conditioner. Therefore, in humid weather in transition seasons, the conventional household variable frequency air conditioner cannot meet the dehumidification comfort requirement, and is usually in an idle state.
Disclosure of Invention
Therefore, the invention provides a temperature-adjusting dehumidifying air-conditioning system and a control method thereof, which can overcome the defects of high energy consumption of refrigeration and dehumidification in low-load operation in summer and low comfort and high energy consumption brought by refrigeration and dehumidification in humid weather in transitional seasons of the prior art in the conventional household variable-frequency air conditioner.
In order to solve the above problems, the present invention provides a temperature-adjusting dehumidifying air-conditioning system, which includes a compressor, an outdoor heat exchanger, a first throttling element, an indoor side heat exchange set, an indoor first heat exchanger and an indoor second heat exchanger of the indoor side heat exchange set, wherein the indoor first heat exchanger and the indoor second heat exchanger are respectively located at the upstream and downstream of indoor return air, the first throttling element is disposed on a first trunk between the indoor side heat exchange set and the outdoor heat exchanger, the indoor second heat exchanger is communicated with the first trunk through a second branch, and the second branch is provided with a second throttling element, and further includes a flow path control valve set, the flow path control valve set is configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in a refrigeration mode, the refrigerant discharged by the compressor flows out through the outdoor heat exchanger and then can flow back into the compressor through the indoor first heat exchanger and the indoor second heat exchanger in parallel; when the temperature-adjusting dehumidifying air-conditioning system operates in a heating mode, the refrigerant discharged by the compressor flows out through the indoor first heat exchanger and the indoor second heat exchanger in parallel and then flows back into the compressor through the outdoor heat exchanger; when the temperature-adjusting dehumidifying air-conditioning system operates in a reheating dehumidifying mode, the refrigerant discharged by the compressor flows out through the outdoor heat exchanger and the indoor second heat exchanger in parallel and then flows back into the compressor through the indoor first heat exchanger.
In some embodiments, the compressor has a first cylinder and a second cylinder in parallel, wherein the first cylinder has a first suction port, the second cylinder has a second suction port, and the first cylinder and the second cylinder exhausts are summed at an exhaust port of the compressor.
In some embodiments, the flow path control valve set comprises a four-way reversing valve, a three-way reversing valve and a solenoid valve, wherein a first port of the three-way reversing valve and a side of the indoor second heat exchanger away from the second throttling element are communicated, a second port of the three-way reversing valve is communicated with a second air suction port and a first end of the solenoid valve in a gathering manner, a third port of the three-way reversing valve is communicated with the air exhaust port and a D pipe of the four-way reversing valve, a C pipe of the four-way reversing valve is communicated with a side of the outdoor heat exchanger away from the first throttling element, an S pipe of the four-way reversing valve is communicated with the first air suction port and a second end of the solenoid valve, an E pipe of the four-way reversing valve is communicated with a side of the indoor first heat exchanger away from the first throttling element, and in the refrigeration mode, the first port is communicated with the second port, The electromagnetic valve is cut off, a D pipe and a C pipe of the four-way reversing valve and an E pipe and an S pipe of the four-way reversing valve are respectively communicated, in the heating mode, the first port is communicated with the third port, the electromagnetic valve is communicated, the D pipe and the E pipe of the four-way reversing valve and the C pipe and the S pipe of the four-way reversing valve are respectively communicated, in the reheating and dehumidifying mode, the first port is communicated with the third port, the electromagnetic valve is communicated, and the D pipe and the C pipe of the four-way reversing valve and the E pipe and the S pipe of the four-way reversing valve are respectively communicated.
In some embodiments, the three-way reversing valve is formed by a four-way reversing valve having one port plugged.
In some embodiments, the first indoor heat exchanger is in communication with the first main line through a first branch line, and a third throttling element is provided on the first branch line.
In some embodiments, the compressor further includes a third cylinder parallel to the first cylinder and the second cylinder, the first trunk further includes a flash evaporation device, and a third suction port of the third cylinder is communicated with the flash evaporation device so as to introduce the gaseous refrigerant in the flash evaporation device into the third cylinder.
In some embodiments, the indoor heat exchange groups are provided in at least two groups, and at least two groups of the indoor heat exchange groups are provided in parallel.
The invention also provides a control method of the temperature-regulating dehumidifying air-conditioning system, which is used for controlling the temperature-regulating dehumidifying air-conditioning system, and the control method comprises the following steps:
acquiring an operation mode of the temperature-adjusting dehumidifying air-conditioning system;
and controlling the on-off of the flow paths of the four-way reversing valve, the three-way reversing valve and the electromagnetic valve according to the acquired running mode.
In some embodiments of the present invention, the substrate is,
when the operation mode is a refrigeration mode, controlling the first port to be communicated with the second port, controlling the electromagnetic valve to be cut off, and controlling a D pipe and a C pipe and an E pipe and an S pipe of the four-way reversing valve to be communicated respectively;
when the operation mode is a heating mode, controlling the first port to be communicated with the third port, the electromagnetic valve to be communicated, and the D pipe and the E pipe and the C pipe and the S pipe of the four-way reversing valve to be communicated respectively;
and when the operation mode is a reheating dehumidification mode, controlling the first port to be communicated with the third port, controlling the electromagnetic valve to be communicated, and controlling a pipe D and a pipe C and a pipe E and a pipe S of the four-way reversing valve to be communicated respectively.
In some embodiments of the present invention, the substrate is,
when the operation mode is a reheating dehumidification mode, the relative humidity of return air is higher than a humidity set value, and the temperature of the return air is lower than a temperature set value, the opening degree of the first throttling element is controlled to be reduced, the opening degree of the second throttling element is controlled to be increased, and the rotating speed of the outdoor fan is reduced.
On one hand, two heat exchangers are arranged in parallel on the indoor side, so that the system has two different evaporation temperatures when running in a refrigeration mode, and indoor return air sequentially flows through the two heat exchangers with high and low evaporation temperatures, so that the return air is subjected to stepped cooling and dehumidification, the irreversible loss in the heat exchange process is reduced, and the refrigeration energy efficiency ratio and the unit energy consumption dehumidification capacity are improved; on the other hand, when dehumidification is needed in transition seasons, the indoor windward side evaporator can realize dehumidification and cooling of return air through switching of the functional valves, the indoor leeward side heat exchanger becomes a condenser and is connected with an outdoor condenser in parallel, and the flow distribution of the refrigerant is adjusted through the electronic expansion valves which are connected on respective outlet pipelines in series, so that the distribution of condensation load and the adjustment of indoor outlet air temperature are realized, the comfort is obviously improved, the energy consumption is reduced, and the system is relatively simple, reliable and low in cost.
Drawings
FIG. 1 is a schematic diagram of a temperature and humidity conditioning system in a cooling mode according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of a temperature and humidity controlled air conditioning system in a heating mode according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a temperature and humidity controlled and dehumidifying air conditioning system in a reheat dehumidification mode according to an embodiment of the present invention;
FIG. 4 is a schematic view of a temperature conditioned and dehumidified air conditioning system of another embodiment of the present invention in a cooling mode;
FIG. 5 is a schematic view of a temperature and humidity conditioning system according to another embodiment of the present invention in a heating mode;
FIG. 6 is a schematic diagram of a temperature and humidity controlled and dehumidifying air conditioning system according to another embodiment of the present invention in a reheat dehumidification mode;
FIG. 7 is a schematic diagram of a temperature and humidity conditioning system in a cooling mode according to yet another embodiment of the present invention;
FIG. 8 is a schematic view of a temperature and humidity controlled air conditioning system in a heating mode according to yet another embodiment of the present invention;
fig. 9 is a schematic view of a temperature-regulating dehumidifying air-conditioning system in a reheating dehumidifying mode according to still another embodiment of the present invention.
The reference numerals are represented as:
10. a compressor; 11. an exhaust port; 12. a first air intake port; 13. a second air suction port; 14. a third air suction port; 20. an outdoor heat exchanger; 31. a first throttling element; 32. a second throttling element; 33. a third throttling element; 41. an indoor first heat exchanger; 42. an indoor second heat exchanger; 51. a four-way reversing valve; 52. a three-way reversing valve; 61. an outdoor side fan; 62. an indoor side fan; 70. an electromagnetic valve; 80. a flash device.
Detailed Description
Referring to fig. 1 to 9 in combination, according to an embodiment of the present invention, there is provided a temperature-adjusting and dehumidifying air-conditioning system, which includes a compressor 10, an outdoor heat exchanger 20, a first throttling element 31 (such as an electronic expansion valve, a thermal expansion valve, a throttling short pipe or a capillary pipe, etc., the same applies below), an indoor heat exchange set, the indoor first heat exchanger 41 and the indoor second heat exchanger 42 of the indoor side heat exchange group are respectively positioned at the upstream and the downstream of the indoor return air, the first throttling element 31 is arranged on a first trunk line between the indoor side heat exchange group and the outdoor heat exchanger 20, the indoor second heat exchanger 42 is communicated with the first trunk line through a second branch line, and a second throttling element 32 is provided on the second branch, and a flow control valve group configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in the cooling mode, the refrigerant discharged from the compressor 10 flows out through the outdoor heat exchanger 20 and then can flow back into the compressor 10 through the indoor first heat exchanger 41 and the indoor second heat exchanger 42 in parallel; when the temperature-adjusting dehumidifying air-conditioning system operates in the heating mode, the refrigerant discharged from the compressor 10 flows out through the indoor first heat exchanger 41 and the indoor second heat exchanger 42 in parallel and then flows back into the compressor 10 through the outdoor heat exchanger 20; when the temperature-adjusting dehumidifying air-conditioning system operates in the reheat dehumidifying mode, the refrigerant discharged from the compressor 10 flows out through the outdoor heat exchanger 20 and the indoor second heat exchanger 42 in parallel, and then flows back into the compressor 10 through the indoor first heat exchanger 41.
In the technical scheme, on one hand, two heat exchangers are arranged on the indoor side in parallel, so that two different evaporation temperatures are achieved when the system operates in a refrigeration mode, indoor return air sequentially flows through the two heat exchangers with high and low evaporation temperatures, and therefore stepped cooling and dehumidification of the return air are achieved, irreversible loss in the heat exchange process is reduced, and the refrigeration energy efficiency ratio and the unit energy consumption dehumidification capacity are improved; on the other hand, when dehumidification is needed in transitional seasons, the indoor windward side evaporator (i.e., the indoor first heat exchanger 41) is enabled to achieve dehumidification and cooling of return air through switching of the functional valve (i.e., the flow path control valve group), the indoor leeward side heat exchanger is changed into a condenser (i.e., the indoor second heat exchanger 42) and is connected with the outdoor condenser (i.e., the outdoor heat exchanger 20) in parallel, and the refrigerant flow distribution is adjusted through the electronic expansion valves (i.e., the first throttling element 31 and the second throttling element 32) connected in series on respective outlet pipelines, so that distribution of condensation load and adjustment of indoor outlet air temperature are achieved, comfort is remarkably improved, energy consumption is reduced, and the system is relatively simple, reliable and low in cost.
In some embodiments, the compressor 10 has a first cylinder and a second cylinder in parallel, wherein the first cylinder has a first suction port 12, the second cylinder has a second suction port 13, and the exhaust of the first cylinder and the second cylinder is collected at the exhaust port 11 of the compressor 10, i.e. the compressor 10 is a double-suction single-row double-cylinder compressor, and is compact.
Referring specifically to fig. 1 to 3, in some embodiments, the flow path control valve assembly includes a four-way reversing valve 51, a three-way reversing valve 52 and a solenoid valve 70, wherein a first port of the three-way reversing valve 52 and a side of the indoor second heat exchanger 42 away from the second throttling element 32 communicate with each other, a second port of the three-way reversing valve 52 communicates with the second suction port 13 and a first end of the solenoid valve 70 in a collective manner, a third port of the three-way reversing valve 52 communicates with the discharge port 11 and a D-pipe of the four-way reversing valve 51, a C-pipe of the four-way reversing valve 51 communicates with a side of the outdoor heat exchanger 20 away from the first throttling element 31, an S-pipe of the four-way reversing valve 51 communicates with the first suction port 12 and a second end of the solenoid valve 70, and an E-pipe of the four-way reversing valve 51 communicates with a side of the indoor first heat exchanger 41 away from the first throttling element 31, and in the cooling mode, the first port is communicated with the second port, the solenoid valve 70 is blocked, the D-tube and C-tube and the E-tube and S-tube of the four-way valve 51 are respectively communicated, in the heating mode, the first port is communicated with the third port, the solenoid valve 70 is communicated, the D-tube and E-tube and C-tube and S-tube of the four-way valve 51 are respectively communicated, in the reheating and dehumidifying mode, the first port is communicated with the third port, the solenoid valve 70 is communicated, the D-tube and C-tube and E-tube and S-tube of the four-way valve 51 are respectively communicated, in some embodiments, the three-way valve 52 is formed by a four-way valve having one port blocked, specifically, as shown in fig. 1, the four-way valve in the figure comprises an S-tube, an E-tube, a D-tube and a C-tube, wherein the S-tube corresponds to the second port, and the E-tube corresponds to the first port, the D pipe corresponds to the third port, and the C pipe is blocked, because the four-way reversing valve is common in an air conditioning system and has a price advantage, the function of the three-way reversing valve 52 is realized by welding and blocking one port of the four-way reversing valve, and the system cost is lower.
Referring specifically to fig. 1, at this time, when the temperature adjusting and dehumidifying air-conditioning system operates in the cooling mode: the four-way reversing valve 51 and the three-way reversing valve 52 are both powered off, the electromagnetic valve 70 is closed, the four-way reversing valve 51 and the three-way reversing valve 52 are both communicated by a D pipe and a C pipe, and are communicated by an S pipe and an E pipe, high-temperature and high-pressure refrigerant gas discharged by the compressor enters the outdoor heat exchanger 20 through the D pipe and the C pipe of the four-way reversing valve 51, releases heat in the outdoor heat exchanger 20 and is condensed into high-pressure liquid refrigerant, and then is throttled and depressurized by the first throttling element 31 to be divided into two paths: one path of the refrigerant passes through the indoor first heat exchanger 41 to evaporate and absorb heat and then enters the first air suction port 12 of the compressor through the E end and the S end of the four-way reversing valve 51; the other path of refrigerant enters the indoor second heat exchanger 42 after being further throttled and depressurized by the second throttling element 32, enters the second air suction port 13 of the compressor through an E, S pipe of the three-way reversing valve 52 after heat exchange is finished, and is exhausted, mixed and discharged after the refrigerant entering the first air suction port and the second air suction port of the compressor are compressed in respective compression cylinders, so that the whole refrigeration cycle is finished. In this mode, the indoor first heat exchanger 41 and the indoor second heat exchanger 42 are respectively used as a high-temperature evaporator and a low-temperature evaporator, the high-temperature evaporator is mainly responsible for sensible heat load, the low-temperature evaporator is mainly responsible for latent heat load, return air is cooled and dehumidified by the high-temperature evaporator and the low-temperature evaporator in a stepped manner, irreversible loss in a heat exchange process is reduced, and the energy efficiency ratio of the system is improved.
Referring specifically to fig. 2, when the temperature-adjusting and dehumidifying air-conditioning system operates in the heating mode: at this time, the four-way reversing valve 51 and the three-way reversing valve 52 are both electrified, the electromagnetic valve 70 is opened, the four-way reversing valve 51 and the three-way reversing valve 52 are both communicated through a D pipe and an E pipe, and a C pipe and an S pipe. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 10 is divided into two paths, one path of the gaseous refrigerant enters the indoor first heat exchanger 41 through an D, E pipe of the four-way reversing valve 51 to be condensed and released into liquid; the other path of the refrigerant enters the indoor second heat exchanger 42 through a D, E pipe of the three-way reversing valve 52 to be condensed and released into liquid, then is throttled and depressurized by the second throttling element 32 (at the moment, the second throttling element 32 mainly plays a role in flow distribution), is mixed with the refrigerant coming out of the indoor first heat exchanger 41, and is throttled and depressurized by the first throttling element 31 to enter the outdoor heat exchanger 20 to be evaporated and absorbed into gas. The gaseous refrigerant passes through the C, S tube of the four-way reversing valve 51 and then is divided into two paths, one path directly enters the first suction port 12 of the compressor 10, and the other path enters the second suction port 13 of the compressor through the electromagnetic valve 70. After the refrigerant entering the first and second air suction ports of the compressor is compressed in the respective compression cylinders, the refrigerant is exhausted, mixed and discharged, thereby completing the whole heating cycle.
Referring specifically to fig. 3, when the temperature-adjusting dehumidifying air-conditioning system operates in the reheat dehumidification mode: at this time, the four-way reversing valve 51 is powered off, the three-way reversing valve 52 is powered on, the electromagnetic valve 70 is opened, the pipe D of the three-way reversing valve 52 is communicated with the pipe E, the pipe C of the three-way reversing valve 52 is communicated with the pipe S, the pipe D of the four-way reversing valve 51 is communicated with the pipe C, and the pipe E of the four-way reversing valve 51 is communicated with the pipe S. The high-temperature and high-pressure gaseous refrigerant discharged by the compressor is divided into two paths, one path of the high-temperature and high-pressure gaseous refrigerant enters the outdoor heat exchanger 20 through an D, C pipe of the four-way reversing valve 51 for heat exchange, is condensed to release heat to be liquid refrigerant, and then is throttled and depressurized through the first throttling element 31; the other path of refrigerant discharged by the compressor enters the indoor second heat exchanger 42 through an D, E pipe of the three-way reversing valve 52 for heat exchange, is condensed to release heat to be liquid refrigerant, is throttled and depressurized by the second throttling element 32, is finally mixed with the refrigerant coming out of the first throttling element 31, enters the indoor first heat exchanger 41, and is evaporated, absorbed and changed into a gas state. The gaseous refrigerant passes through the E, S tube of the four-way reversing valve 51 and is then split into two paths, one path being drawn directly into the first suction port 12 of the compressor and the other path passing through the solenoid valve 70 into the second suction port 13 of the compressor. After the refrigerants entering the first and second air suction ports of the compressor are compressed in the respective compression cylinders, the refrigerants are exhausted, mixed and discharged, thereby completing the whole reheating and dehumidifying cycle. In this mode, the indoor first heat exchanger 41 serves as a separate evaporator to cool and dehumidify the indoor air, and the indoor second heat exchanger 42 serves as a condenser to reheat the cooled and dehumidified air, thereby increasing the supply air temperature and improving the comfort of the indoor environment.
Referring to fig. 4 to 6 in particular, in some embodiments, the indoor first heat exchanger 41 is communicated with the first main line through a first branch line, a third throttling element 33 is disposed on the first branch line, and the setting of the third throttling element 33 can control the flow rate of the refrigerant in the indoor first heat exchanger 41, so that the temperature adjustment or the evaporation temperature control is more accurate.
Specifically, referring to fig. 4 and 6, in some embodiments, the compressor 10 further includes a third cylinder parallel to the first cylinder and the second cylinder, a flash device 80 is further disposed on the first trunk line, and the third suction port 14 of the third cylinder is communicated with the flash device 80 so as to introduce the gaseous refrigerant in the flash device 80 into the third cylinder, so that the flash device 80 is disposed in the system to reduce the specific enthalpy of the evaporator inlet and improve the energy efficiency ratio of the system.
Specifically, referring to fig. 4, when the system is operating in the cooling mode: the four-way reversing valve 51 and the three-way reversing valve 52 are both powered off, the electromagnetic valve 70 is closed, and the four-way reversing valve 51 and the three-way reversing valve 52 are both communicated through a D pipe and a C pipe and are communicated through an S pipe and an E pipe. The high-temperature high-pressure refrigerant gas discharged by the compressor enters the outdoor heat exchanger 20 through the pipe D and the pipe C of the four-way reversing valve 51, releases heat in the outdoor heat exchanger 20 and is condensed into high-pressure liquid refrigerant, then the high-pressure liquid refrigerant is throttled and decompressed into a two-phase state through the first throttling element 31 and enters the flash device 80, in the flash device 80, the gaseous saturated refrigerant is sucked into the third suction port 14 of the compressor, and the liquid saturated refrigerant separated by the flash device is divided into two paths: one path of the refrigerant enters the indoor first heat exchanger 41 for evaporation and heat absorption after being throttled and depressurized by the third throttling element 33, and then enters the first air suction port 12 of the compressor through the E end and the S end of the four-way reversing valve 51; the other path of refrigerant enters the indoor second heat exchanger 42 after being throttled and depressurized by the second throttling element 32, enters the second air suction port 13 of the compressor through an E, S pipe of the three-way reversing valve 52 after heat exchange is finished, and is discharged, mixed and discharged after the refrigerant entering the first air suction port, the second air suction port and the third air suction port of the compressor are compressed in respective compression cylinders, so that the whole refrigeration cycle is finished. In this mode, the specific enthalpy of the evaporator inlet is reduced by adopting a parallel compression flash extraction mode, the refrigerating capacity and the system energy efficiency ratio are improved, the indoor first heat exchanger 41 and the indoor second heat exchanger 42 are respectively used as a high-temperature evaporator and a low-temperature evaporator, the high-temperature evaporator is mainly responsible for sensible heat load, the low-temperature evaporator is mainly responsible for latent heat load, return air is subjected to gradient cooling and dehumidification by the high-temperature evaporator and the low-temperature evaporator, the irreversible loss in the heat exchange process is reduced, and the system energy efficiency ratio is improved.
Referring to fig. 5, when the system is operating in heating mode: at this time, the four-way reversing valve 51 and the three-way reversing valve 52 are both electrified, the electromagnetic valve 70 is opened, the four-way reversing valve 51 and the three-way reversing valve 52 are both communicated through a D pipe and an E pipe, and a C pipe and an S pipe. The high-temperature high-pressure gaseous refrigerant discharged from the compressor 10 is divided into two paths, one path of the high-temperature high-pressure gaseous refrigerant enters the indoor first heat exchanger 41 through an D, E pipe of the four-way reversing valve 51 to be condensed and released into liquid, and then is throttled and depressurized through the third throttling element 33; the other path of the refrigerant enters the indoor second heat exchanger 42 through a D, E pipe of the three-way reversing valve 52 to be condensed and released into liquid, then is throttled and depressurized by the second throttling element 32 and is mixed with the refrigerant coming out of the third throttling element 33, the mixed refrigerant enters the flash device 80, the gaseous saturated refrigerant flashed by the flash device 80 is sucked into the third suction port 14 of the compressor, and the liquid saturated refrigerant separated from the flash device 80 is throttled and depressurized by the first throttling element 31 and then enters the outdoor heat exchanger 20 to be evaporated and absorbed into gas. The gaseous refrigerant passes through the C, S tube of the four-way reversing valve 51 and then is divided into two paths, one path directly enters the first suction port 12 of the compressor 10, and the other path enters the second suction port 13 of the compressor through the electromagnetic valve 70. After the refrigerants entering the first, second and third air suction ports of the compressor are compressed in the respective compression cylinders, the refrigerants are exhausted, mixed and discharged, and therefore the whole heating cycle is completed. In this mode, a parallel compression flash pumping mode is adopted, the system heating performance coefficient is improved, the system heating capacity is obviously improved, and the heating operation working condition of the system is widened.
Referring to fig. 6, when the system is operating in the reheat dehumidification mode: at this time, the four-way reversing valve 51 is powered off, the three-way reversing valve 52 is powered on, the electromagnetic valve 70 is opened, the pipe D of the three-way reversing valve 52 is communicated with the pipe E, the pipe C is communicated with the pipe S, the pipe D of the four-way reversing valve 51 is communicated with the pipe C, and the pipe E is communicated with the pipe S. The high-temperature high-pressure gaseous refrigerant discharged by the compressor is divided into two paths, one path of the high-temperature high-pressure gaseous refrigerant enters the outdoor heat exchanger 20 through an D, C pipe of the four-way reversing valve 51 for heat exchange, the condensed heat is released into a liquid refrigerant, the liquid refrigerant is throttled and reduced in pressure by the first throttling element 31 and enters the flash device 80, and the gaseous saturated refrigerant flashed by the flash device 80 is sucked into a third air suction port 14 of the compressor; the other path of refrigerant discharged by the compressor enters the indoor second heat exchanger 42 through an D, E pipe of the three-way reversing valve 52 for heat exchange, is condensed to release heat to be liquid refrigerant, is throttled and depressurized by the second throttling element 32, is finally mixed with the liquid saturated refrigerant separated from the flash device 80, is further throttled and depressurized by the third throttling element 33, enters the indoor first heat exchanger 41, and is evaporated, absorbed and changed into gas state. The gaseous refrigerant passes through the E, S tube of the four-way reversing valve 51 and is then split into two paths, one path being drawn directly into the first suction port 12 of the compressor and the other path passing through the solenoid valve 70 into the second suction port 13 of the compressor. After the refrigerants entering the first, second and third air suction ports of the compressor are compressed in the respective compression cylinders, the exhaust gas is mixed and discharged, thereby completing the whole reheating and dehumidifying cycle.
Specifically, referring to fig. 7 and 9, in some embodiments, the indoor heat exchange sets are provided with at least two sets, and at least two sets of the indoor heat exchange sets are arranged in parallel (two sets are shown in fig. 7 and 9), so that the temperature-adjusting and dehumidifying air-conditioning system forms a multi-connected mode, and can adjust and dehumidify multiple spaces.
According to an embodiment of the present invention, there is also provided a control method of a temperature-regulating and dehumidifying air-conditioning system, for controlling the temperature-regulating and dehumidifying air-conditioning system, the control method including:
acquiring an operation mode of the temperature-adjusting dehumidifying air-conditioning system;
and controlling the on-off of the flow paths of the four-way reversing valve 51, the three-way reversing valve 52 and the electromagnetic valve 70 according to the acquired running mode. Specifically, when the operation mode is a refrigeration mode, the first port is controlled to be communicated with the second port, the electromagnetic valve 70 is controlled to be blocked, and a pipe D and a pipe C of the four-way reversing valve 51 and a pipe E and a pipe S of the four-way reversing valve are controlled to be communicated respectively; when the operation mode is a heating mode, controlling the first port to be communicated with the third port, the electromagnetic valve 70 to be communicated, and the D pipe and the E pipe and the C pipe and the S pipe of the four-way reversing valve 51 to be communicated respectively; and when the operation mode is a reheating and dehumidifying mode, controlling the first port to be communicated with the third port, the electromagnetic valve 70 to be communicated, and the D pipe and the C pipe and the E pipe and the S pipe of the four-way reversing valve 51 to be communicated respectively.
In some embodiments, when the operation mode is the reheat dehumidification mode, the relative humidity of the return air is higher than a humidity set value, and the temperature of the return air is lower than a temperature set value, the opening degree of the first throttling element 31 is controlled to be decreased, the opening degree of the second throttling element 32 is controlled to be increased, and the rotating speed of the outdoor fan 61 is controlled to be decreased, and the humidity set value and the temperature set value can be obtained through experiments. In practical application, the second throttling element 32 is an electronic expansion valve, when the first throttling element 31 is an electronic expansion valve, the reheating and dehumidifying mode temperature regulation range is the largest, when the first throttling element 31 is a capillary tube or a throttling short tube (cost reduction), the temperature regulation range is relatively reduced, the rotating speed of the outdoor side fan 61 is reduced, the outlet air temperature of the second indoor side heat exchanger 42 can be improved, and the rotating speed of the outdoor side fan 61 is reduced to be generally matched with the opening reduction of the first throttling element 31 for regulation.
It is readily understood by a person skilled in the art that the advantageous ways described above can be freely combined, superimposed without conflict.
The present invention is not limited to the above preferred embodiments, and any modifications, equivalent substitutions and improvements made within the spirit and principle of the present invention should be included in the protection scope of the present invention. The above is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several improvements and modifications can be made without departing from the technical principle of the present invention, and these improvements and modifications should also be regarded as the protection scope of the present invention.
Claims (10)
1. The utility model provides a temperature regulation and dehumidification air conditioning system, includes compressor (10), outdoor heat exchanger (20), first throttling element (31), indoor side heat transfer group, its characterized in that, indoor first heat exchanger (41), indoor second heat exchanger (42) of indoor side heat transfer group, indoor first heat exchanger (41) reach indoor second heat exchanger (42) are in the upper reaches and the low reaches of indoor return air respectively, first throttling element (31) are located indoor side heat transfer group with on the first trunk between outdoor heat exchanger (20), indoor second heat exchanger (42) through the second branch road with first trunk intercommunication, just be equipped with second throttling element (32) on the second branch road, still include flow path control valves, flow path control valves is configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in a refrigeration mode, the refrigerant discharged by the compressor (10) flows out through the outdoor heat exchanger (20) and then can parallelly flow back into the compressor (10) through the indoor first heat exchanger (41) and the indoor second heat exchanger (42); when the temperature-adjusting dehumidifying air-conditioning system operates in a heating mode, the refrigerant discharged by the compressor (10) flows out through the indoor first heat exchanger (41) and the indoor second heat exchanger (42) in parallel and then flows back into the compressor (10) through the outdoor heat exchanger (20); when the temperature-adjusting dehumidifying air-conditioning system operates in a reheating dehumidifying mode, the refrigerant discharged by the compressor (10) flows out through the outdoor heat exchanger (20) and the indoor second heat exchanger (42) in parallel and then flows back into the compressor (10) through the indoor first heat exchanger (41).
2. Tempering and dehumidifying air conditioning system according to claim 1, characterized in that the compressor (10) has a first cylinder and a second cylinder in parallel, wherein the first cylinder has a first suction opening (12), the second cylinder has a second suction opening (13), and the exhausts of the first and second cylinders are combined at an exhaust opening (11) of the compressor (10).
3. The temperature-adjusting dehumidifying air-conditioning system according to claim 2, wherein the flow path control valve group comprises a four-way reversing valve (51), a three-way reversing valve (52) and a solenoid valve (70), wherein a first port of the three-way reversing valve (52) communicates with a side of the indoor second heat exchanger (42) away from the second throttling element (32), a second port of the three-way reversing valve (52) communicates with a second suction port (13) and a first end of the solenoid valve (70) in a collective manner, a third port of the three-way reversing valve (52) communicates with the discharge port (11) and a D pipe of the four-way reversing valve (51), a C pipe of the four-way reversing valve (51) communicates with a side of the outdoor heat exchanger (20) away from the first throttling element (31), and an S pipe of the four-way reversing valve (51) communicates with the first suction port (12) and a second end of the solenoid valve (70), the four-way reversing valve is characterized in that an E pipe of the four-way reversing valve (51) is communicated with one side, far away from the first throttling element (31), of the indoor first heat exchanger (41), in the refrigerating mode, a first port is communicated with a second port, the electromagnetic valve (70) is cut off, a D pipe and a C pipe of the four-way reversing valve (51) and the E pipe and the S pipe are respectively communicated, in the heating mode, the first port is communicated with the third port, the electromagnetic valve (70) is communicated, the D pipe and the E pipe of the four-way reversing valve (51) and the C pipe and the S pipe are respectively communicated, and in the reheating and dehumidifying mode, the first port is communicated with the third port, the electromagnetic valve (70) is communicated, and the D pipe and the C pipe of the four-way reversing valve (51) and the E pipe and the S pipe are respectively communicated.
4. The system according to claim 3, wherein the three-way reversing valve (52) is formed by a four-way reversing valve having one port blocked.
5. Tempering and dehumidifying air conditioning system according to claim 3, wherein said indoor first heat exchanger (41) communicates with said first main circuit through a first branch circuit, on which a third throttling element (33) is provided.
6. The temperature-regulating dehumidifying air-conditioning system according to any one of claims 3 to 5, wherein the compressor (10) further has a third cylinder connected in parallel with the first cylinder and the second cylinder, a flash device (80) is further provided on the first trunk line, and a third suction port (14) of the third cylinder is communicated with the flash device (80) so as to be able to introduce the gaseous refrigerant in the flash device (80) into the third cylinder.
7. The system of claim 1, wherein at least two of said indoor side heat exchange sets are arranged, and at least two of said indoor side heat exchange sets are arranged in parallel.
8. A control method of a temperature-adjusting and dehumidifying air-conditioning system, for controlling the temperature-adjusting and dehumidifying air-conditioning system according to any one of claims 3 to 7, the control method comprising:
acquiring an operation mode of the temperature-adjusting dehumidifying air-conditioning system;
and controlling the on-off of the flow paths of the four-way reversing valve (51), the three-way reversing valve (52) and the electromagnetic valve (70) according to the acquired running mode.
9. The control method according to claim 8,
when the operation mode is a refrigeration mode, controlling the first port to be communicated with the second port, the electromagnetic valve (70) to be cut off, and the D pipe and the C pipe and the E pipe and the S pipe of the four-way reversing valve (51) to be respectively communicated;
when the operation mode is a heating mode, the first port is controlled to be communicated with the third port, the electromagnetic valve (70) is controlled to be communicated, and a pipe D and a pipe E of the four-way reversing valve (51) and a pipe C and a pipe S of the four-way reversing valve are respectively controlled to be communicated;
and when the operation mode is a reheating dehumidification mode, the first port is communicated with the third port, the electromagnetic valve (70) is communicated, and a pipe D and a pipe C of the four-way reversing valve (51) are respectively communicated with a pipe E and a pipe S.
10. The control method according to claim 9,
when the operation mode is a reheating dehumidification mode, the relative humidity of return air is higher than a humidity set value, and the temperature of the return air is lower than a temperature set value, the opening degree of the first throttling element (31) is reduced, the opening degree of the second throttling element (32) is increased, and the rotating speed of the outdoor fan (61) is reduced.
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115218434A (en) * | 2022-07-06 | 2022-10-21 | 青岛海尔空调器有限总公司 | Air conditioner and air conditioner control method |
| CN115751517A (en) * | 2022-09-08 | 2023-03-07 | 珠海格力电器股份有限公司 | Heat pump type air conditioner control method, heat pump type air conditioner control device, heat pump type air conditioner, and storage medium |
| WO2024140367A1 (en) * | 2022-12-30 | 2024-07-04 | 广东美的白色家电技术创新中心有限公司 | Air conditioner and air conditioner operating method |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105526672A (en) * | 2015-12-11 | 2016-04-27 | 珠海格力电器股份有限公司 | Temperature and humidity control method for reheating and dehumidifying system |
| JP2019052817A (en) * | 2017-09-19 | 2019-04-04 | ダイキン工業株式会社 | Air conditioner |
| CN110345659A (en) * | 2019-07-29 | 2019-10-18 | 珠海格力电器股份有限公司 | Reheating and dehumidifying integrated refrigeration system and control method |
| CN111396993A (en) * | 2020-03-30 | 2020-07-10 | 广东美的制冷设备有限公司 | Three-pipe air conditioning system, reheating and dehumidifying method and computer readable storage medium |
| CN111780254A (en) * | 2020-07-02 | 2020-10-16 | 珠海格力电器股份有限公司 | Air conditioning system and control method thereof |
-
2022
- 2022-03-21 CN CN202210278448.4A patent/CN114608075A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105526672A (en) * | 2015-12-11 | 2016-04-27 | 珠海格力电器股份有限公司 | Temperature and humidity control method for reheating and dehumidifying system |
| JP2019052817A (en) * | 2017-09-19 | 2019-04-04 | ダイキン工業株式会社 | Air conditioner |
| CN110345659A (en) * | 2019-07-29 | 2019-10-18 | 珠海格力电器股份有限公司 | Reheating and dehumidifying integrated refrigeration system and control method |
| CN111396993A (en) * | 2020-03-30 | 2020-07-10 | 广东美的制冷设备有限公司 | Three-pipe air conditioning system, reheating and dehumidifying method and computer readable storage medium |
| CN111780254A (en) * | 2020-07-02 | 2020-10-16 | 珠海格力电器股份有限公司 | Air conditioning system and control method thereof |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115218434A (en) * | 2022-07-06 | 2022-10-21 | 青岛海尔空调器有限总公司 | Air conditioner and air conditioner control method |
| CN115751517A (en) * | 2022-09-08 | 2023-03-07 | 珠海格力电器股份有限公司 | Heat pump type air conditioner control method, heat pump type air conditioner control device, heat pump type air conditioner, and storage medium |
| CN115751517B (en) * | 2022-09-08 | 2024-07-05 | 珠海格力电器股份有限公司 | Heat pump type air conditioner control method and device, heat pump type air conditioner and storage medium |
| WO2024140367A1 (en) * | 2022-12-30 | 2024-07-04 | 广东美的白色家电技术创新中心有限公司 | Air conditioner and air conditioner operating method |
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