CN114484623A - 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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- CN114484623A CN114484623A CN202210277869.5A CN202210277869A CN114484623A CN 114484623 A CN114484623 A CN 114484623A CN 202210277869 A CN202210277869 A CN 202210277869A CN 114484623 A CN114484623 A CN 114484623A
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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, a first indoor side heat exchanger and a second indoor side 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 the outdoor side heat exchanger, a second throttling element is arranged on a second branch, and during a refrigeration mode, a refrigerant discharged by a compressor flows out of the outdoor side heat exchanger and then flows back into the compressor through the first indoor side heat exchanger and the second indoor side heat exchanger; and in the reheating dehumidification mode, the refrigerant discharged by the compressor flows out through the outdoor heat exchanger and the second indoor heat exchanger and then flows back into the compressor through the first indoor heat exchanger, and the flow path control valve group comprises a one-way valve which is cut off in the refrigeration mode and communicated in the reheating dehumidification mode. 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-regulating 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, and an indoor heat exchange set, wherein the indoor heat exchange set includes a first indoor heat exchanger and a second indoor heat exchanger, the first indoor heat exchanger and the second indoor 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 heat exchange set and the outdoor heat exchanger, the second indoor 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 control valve set, the flow 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 first indoor heat exchanger and the second indoor heat exchanger in parallel; when the temperature adjusting and dehumidifying air-conditioning system operates in a reheating and dehumidifying mode, the refrigerant discharged by the compressor flows back into the compressor through the first indoor heat exchanger after flowing out through the outdoor heat exchanger and the second indoor heat exchanger in parallel, the flow path control valve group comprises a one-way valve, and the one-way valve is cut off in the refrigerating mode and is communicated in the reheating and dehumidifying mode.
In some embodiments, the flow path control valve block is further configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in a heating mode, the refrigerant discharged by the compressor flows out through the first indoor side heat exchanger and the second indoor side heat exchanger in parallel and then flows back into the compressor through the outdoor side heat exchanger, the flow path control valve group comprises a one-way valve, and the one-way valve is communicated in the heating mode.
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 further comprises a first four-way reversing valve and a second four-way reversing valve, wherein a first port of the first four-way reversing valve is communicated with a side of the first indoor heat exchanger away from the first throttling element, a second port of the first four-way reversing valve is communicated with a second port of the second four-way reversing valve and the exhaust port in a summing manner, a third port of the first four-way reversing valve is communicated with a side of the outdoor heat exchanger away from the first throttling element, and a fourth port of the first four-way reversing valve is communicated with a first end of the one-way valve and the first suction port in a summing manner; the first port of the second four-way reversing valve is communicated with one side, far away from the second throttling element, of the second indoor heat exchanger, the third port of the second four-way reversing valve is communicated with the second end of the one-way valve, the fourth port of the second four-way reversing valve is communicated with the second air suction port, the first port of the first four-way reversing valve is communicated with the fourth port, the second port of the first four-way reversing valve is communicated with the third port, the first port of the second four-way reversing valve is communicated with the fourth port, the second port of the second four-way reversing valve is communicated with the third port, the first port of the first four-way reversing valve is communicated with the second port, the third port of the first four-way reversing valve is communicated with the fourth port, the second port of the first four-way reversing valve is communicated with the third port, the first port of the second four-way reversing valve is communicated with the second port, the third port of the second four-way reversing valve is communicated with the second port, and the second port of the first four-way reversing valve is communicated with the second port of the second four-way reversing valve in a reheating dehumidification mode, The third port communicates with the fourth port.
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 disposed on the first branch line.
In some embodiments, the compressor further includes a third cylinder parallel to the first cylinder and the second cylinder, a flash device is further disposed on the first trunk line, and a third suction port of the third cylinder is communicated with the flash device so as to be able to introduce the gaseous refrigerant in the flash 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 flow paths of the first four-way reversing valve and the second four-way reversing valve to be switched according to the acquired operation mode.
In some embodiments, when the operation mode is a cooling mode, the first port of the first four-way reversing valve is controlled to be communicated with the fourth port, the second port of the first four-way reversing valve is controlled to be communicated with the third port, and the first port of the second four-way reversing valve is controlled to be communicated with the fourth port, and the second port of the second four-way reversing valve is controlled to be communicated with the third port;
when the operation mode is a heating mode, controlling the first port of the first four-way reversing valve to be communicated with the second port and the third port of the first four-way reversing valve to be communicated with the fourth port, and controlling the first port of the second four-way reversing valve to be communicated with the second port and the third port of the second four-way reversing valve to be communicated with the fourth port;
and when the operation mode is a reheating and dehumidifying mode, controlling the first port and the fourth port of the first four-way reversing valve to be communicated, controlling the second port and the third port of the first four-way reversing valve to be communicated, and controlling the first port and the second port of the second four-way reversing valve to be communicated, and controlling the third port and the fourth port to be communicated.
In some embodiments, when the operation mode is a reheat 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 control unit decreases the opening degree of the first throttling element, increases the opening degree of the second throttling element, and decreases the rotation speed of the outdoor fan.
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 diagram of a temperature and humidity conditioning system in a cooling mode according to another embodiment of the present invention;
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 side heat exchanger; 31. a first throttling element; 32. a second throttling element; 33. a third throttling element; 41. a first indoor-side heat exchanger; 42. a second indoor-side heat exchanger; 51. a first four-way reversing valve; 52. a second four-way reversing valve; 61. an outdoor side fan; 62. an indoor side fan; 70. a one-way 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 side heat exchange group comprises a first indoor side heat exchanger 41 and a second indoor side heat exchanger 42, the first indoor side heat exchanger 41 and the second indoor side heat exchanger 42 are respectively positioned at the upstream and the downstream of indoor return air, the first throttling element 31 is arranged on a first trunk between the indoor side heat exchange set and the outdoor side heat exchanger 20, the second indoor side heat exchanger 42 is communicated with the first trunk through a second branch, 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 first indoor heat exchanger 41 and the second indoor heat exchanger 42 in parallel; when the temperature adjusting and dehumidifying air-conditioning system operates in a reheating and dehumidifying mode, the refrigerant discharged from the compressor 10 flows out through the outdoor heat exchanger 20 and the second indoor heat exchanger 42 in parallel and then flows back into the compressor 10 through the first indoor heat exchanger 41, the flow path control valve set includes a check valve 70, and the check valve 70 is cut off in the cooling mode and is communicated in the reheating and dehumidifying mode.
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 first indoor side heat exchanger 41) is enabled to achieve dehumidification and cooling of return air through switching of the functional valves (i.e., the flow path control valve group), the indoor leeward side heat exchanger is changed into a condenser (i.e., the second indoor side heat exchanger 42) and is connected in parallel with the outdoor condenser (i.e., the outdoor side heat exchanger 20), 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) which are 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 addition, in the technical scheme, the check valve 70 is arranged, so that the on-off of the check valve can be formed in different system operation modes only through the pressure difference of the refrigerants at two ends without controlling the check valve, the control is simplified, and the design cost of the system is reduced.
In some embodiments, the flow path control valve block is further configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in the heating mode, the refrigerant discharged from the compressor 10 flows back into the compressor 10 through the outdoor heat exchanger 20 after flowing out through the first indoor heat exchanger 41 and the second indoor heat exchanger 42, the flow path control valve group comprises a check valve 70, and the check valve 70 is communicated in the heating mode, so that the temperature-adjusting dehumidifying system has the heating mode, different temperature-adjusting requirements of users are met, and the comfort of the users is improved.
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 set further includes a first four-way reversing valve 51 and a second four-way reversing valve 52, wherein a first port of the first four-way reversing valve 51 communicates with a side of the first indoor heat exchanger 41 away from the first throttling element 31, a second port communicates with a second port of the second four-way reversing valve 52 and the exhaust port 11 in a collective manner, a third port communicates with a side of the outdoor heat exchanger 20 away from the first throttling element 31, and a fourth port communicates with a first end of the check valve 70 and the first intake port 12 in a collective manner; the first port of the second four-way reversing valve 52 is communicated with the side of the second indoor heat exchanger 42 away from the second throttling element 32, the third port is communicated with the second end of the one-way valve 70, the fourth port is communicated with the second suction port 13, in the cooling mode, the first port of the first four-way reversing valve 51 is communicated with the fourth port, the second port is communicated with the third port, the first port of the second four-way reversing valve 52 is communicated with the fourth port, the second port is communicated with the third port, in the heating mode, the first port of the first four-way reversing valve 51 is communicated with the second port, the third port is communicated with the fourth port, the first port of the second four-way reversing valve 52 is communicated with the second port, the third port is communicated with the fourth port, in the reheating and dehumidifying mode, the first port of the first four-way reversing valve 51 is communicated with the fourth port, the second port is communicated with the third port, and the first port of the second four-way reversing valve 52 is communicated with the second port, The third port communicates with the fourth port.
Referring specifically to fig. 1, when the temperature-adjusting dehumidifying air-conditioning system operates in the cooling mode: the first four-way selector valve 51 and the second four-way selector valve 52 are both de-energized, and the first four-way selector valve 51 and the second four-way selector valve 52 are both D-tube (i.e., the second port, the same below) and C-tube (i.e., the third port, the same below) energized, and S-tube (i.e., the fourth port, the same below) and E-tube (i.e., the first port, the same below) energized. 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 first four-way reversing valve 51, releases heat in the outdoor heat exchanger 20 and is condensed into high-pressure liquid refrigerant, and then the high-pressure liquid refrigerant is throttled and depressurized by the first throttling element 31 and then divided into two paths: one path of the refrigerant passes through the first indoor heat exchanger 41 to evaporate and absorb heat and then enters the first air suction port 12 of the compressor through the end E and the end S of the first four-way reversing valve 51 (at this time, the end D and the end C of the second four-way reversing valve 52 are communicated, and the check valve 70 is closed under the action of reverse pressure difference, as shown by a dotted line in fig. 1); the other path of refrigerant is further throttled and depressurized by the second throttling element 32 and then enters the second indoor heat exchanger 42, after heat exchange is completed, the refrigerant enters the second air suction port 13 of the compressor through the E, S pipe of the second four-way reversing valve 52, and the refrigerant entering the first air suction port 12 and the second air suction port 13 of the compressor is compressed in respective compression cylinders, then is exhausted, mixed and discharged, thereby completing the whole refrigeration cycle. In this mode, the first indoor heat exchanger 41 and the second indoor 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 stepped cooled and dehumidified by the high temperature evaporator and the low temperature evaporator, irreversible loss in the 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 first four-way selector valve 51 and the second four-way selector valve 52 are both energized, the first four-way selector valve 51 and the second four-way selector valve 52 are both in communication with the D pipe and the E pipe, and the C pipe and the S pipe. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 10 is divided into two paths, one path of the high-temperature and high-pressure gaseous refrigerant enters the first indoor side heat exchanger 41 through the D, E pipe of the first four-way reversing valve 51 to be condensed and release heat into a liquid state; the other path of the refrigerant enters the second indoor heat exchanger 42 through an D, E pipe of the second four-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 first indoor heat exchanger 41, is throttled and depressurized by the first throttling element 31, and then enters the outdoor heat exchanger 20 to be evaporated and absorb heat into gas. The gaseous refrigerant passes through C, S tube of the first 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 sequentially passes through the check valve 70 and C, S tube of the second four-way reversing valve 52 and enters the second suction port 13 of the compressor. After the refrigerants entering the first suction port 12 and the second suction port 13 of the compressor are compressed in the respective compression cylinders, the refrigerants are exhausted, mixed and discharged, and thus the whole heating cycle is completed
Referring specifically to fig. 3, when the temperature-adjusting dehumidifying air-conditioning system operates in the reheat dehumidification mode: at this time, the first four-way reversing valve 51 is de-energized, the second four-way reversing valve 52 is energized, the tube D of the first four-way reversing valve 51 is communicated with the tube C, the tube E is communicated with the tube S, and the tube D of the second four-way reversing valve 52 is communicated with the tube E and the tube S is communicated with the tube C. 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 the D, C pipe of the first four-way reversing valve 51 to exchange heat, 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 second indoor heat exchanger 42 through an D, E pipe of the second four-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 first indoor heat exchanger 41, and is evaporated to absorb heat to be gaseous. The gaseous refrigerant passes through E, S tube of the first four-way reversing valve 51 and then is divided into two paths, one path is directly sucked into the first suction port 12 of the compressor, and the other path sequentially passes through the check valve 70 and C, S tube of the second four-way reversing valve 52 and enters the second suction port 13 of the compressor. After the refrigerants having entered the first suction port 12 and the second suction port 13 of the compressor are compressed in the respective compression cylinders, the exhaust gases are mixed and discharged, thereby completing the entire reheat dehumidification cycle. In this mode, the first indoor heat exchanger 41 serves as a separate evaporator to cool and dehumidify the indoor air, and the second indoor 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 some embodiments, the first indoor heat exchanger 41 is communicated with the first main line through a first branch, a third throttling element 33 is disposed on the first branch, and the setting of the third throttling element 33 can control the flow rate of the refrigerant in the first indoor heat exchanger 41, so as to control the temperature or the evaporation temperature more accurately.
Referring to fig. 4 to 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, and a 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: at this time, the first four-way selector valve 51 and the second four-way selector valve 52 are both de-energized, and the first four-way selector valve 51 and the second four-way selector valve 52 are both D-tube and C-tube conductive, and S-tube and E-tube conductive. The high-temperature high-pressure refrigerant gas discharged by the compressor enters the outdoor heat exchanger 20 through the tube D and the tube C of the first four-way reversing valve 51, is condensed and released into high-pressure liquid refrigerant in the outdoor heat exchanger 20, and then is throttled and depressurized into a two-phase state through the first throttling element 31 to enter 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 80 is divided into two paths: one path of the refrigerant is throttled and depressurized by a third throttling element 33, enters a first indoor heat exchanger 41 to be evaporated and absorb heat, and then enters a first air suction port 12 of the compressor through an E end and an S end of a first four-way reversing valve 51; the other path of refrigerant enters the second indoor 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 the E, S pipe of the second four-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 first indoor side heat exchanger 41 and the second indoor side 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 first four-way selector valve 51 and the second four-way selector valve 52 are both energized, the first four-way selector valve 51 and the second four-way selector valve 52 are both in communication with the D pipe and the E pipe, and the C pipe and the S pipe. The high-temperature and high-pressure gaseous refrigerant discharged from the compressor 10 is divided into two paths, one path of the high-temperature and high-pressure gaseous refrigerant enters the first indoor side heat exchanger 41 through the D, E pipe of the first 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 second indoor heat exchanger 42 through a D, E pipe of the second four-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 by 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 C, S tubes of the first 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 sequentially passes through the check valve 70 and C, S tubes of the second four-way reversing valve 52 and enters 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 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 first four-way reversing valve 51 is de-energized, the second four-way reversing valve 52 is energized, the tube D of the first four-way reversing valve 51 is communicated with the tube C, the tube E is communicated with the tube S, the tube D of the second four-way reversing valve 52 is communicated with the tube E, and the tube C is communicated with the tube S. The high-temperature high-pressure gaseous refrigerant discharged by the compressor 10 is divided into two paths, one path of the high-temperature high-pressure gaseous refrigerant enters the outdoor heat exchanger 20 through the D, C pipe of the first four-way reversing valve 51 for heat exchange, is condensed to release heat to form liquid refrigerant, then is throttled and depressurized by the first throttling element 31 to enter the flash device 80, and gaseous saturated refrigerant flashed by the flash device 80 is sucked into the third suction port 14 of the compressor; the other path of refrigerant discharged by the compressor enters the second indoor side heat exchanger 42 through an D, E pipe of the second four-way reversing valve 52 for heat exchange, the condensed heat is released to be liquid refrigerant, then the liquid refrigerant is throttled and depressurized by the second throttling element 32, and finally the liquid refrigerant is mixed with the liquid saturated refrigerant separated from the flash device 80, and the mixed refrigerant enters the first indoor side heat exchanger 41 after being further throttled and depressurized by the third throttling element 33, and is evaporated, absorbed and changed into gas state. The gaseous refrigerant passes through E, S tube of the first four-way reversing valve 51 and then is divided into two paths, one path is directly sucked into the first suction port 12 of the compressor, and the other path sequentially passes through the check valve 70 and C, S tube of the second four-way reversing valve 52 and enters 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 to 9, in some embodiments, at least two groups of indoor side heat exchange sets are provided, and at least two groups of indoor side heat exchange sets are arranged in parallel (two groups are shown in fig. 7 to 9), and at this time, the temperature-adjusting and dehumidifying air-conditioning system forms a multi-connected mode, so that temperature adjustment and dehumidification of multiple spaces can be achieved.
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 flow paths of the first four-way reversing valve 51 and the second four-way reversing valve 52 to be switched on and off according to the acquired operation mode. Specifically, when the operation mode is a cooling mode, the first port and the fourth port of the first four-way reversing valve 51 are controlled to be communicated, the second port and the third port of the first four-way reversing valve are controlled to be communicated, and the first port and the fourth port of the second four-way reversing valve 52 are controlled to be communicated, and the second port and the third port of the second four-way reversing valve are controlled to be communicated;
when the operation mode is a heating mode, controlling the first port of the first four-way reversing valve 51 to be communicated with the second port and the third port to be communicated with the fourth port, and controlling the first port of the second four-way reversing valve 52 to be communicated with the second port and the third port to be communicated with the fourth port;
and when the operation mode is a reheating and dehumidifying mode, controlling the first port and the fourth port of the first four-way reversing valve 51 to be communicated, controlling the second port and the third port to be communicated, and controlling the first port and the second port of the second four-way reversing valve 52 to be communicated, and controlling the third port and the fourth port to be communicated.
In some embodiments, when the operation mode is the reheat dehumidification mode, the return air relative humidity is higher than the humidity set value, and the return air temperature is lower than the 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 rotation speed of the outdoor fan 61 is reduced, 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 dehumidification air conditioning system adjusts temperature, includes compressor (10), outdoor side heat exchanger (20), first throttling element (31), indoor side heat exchanger group, its characterized in that, the first indoor side heat exchanger (41) of indoor side heat exchanger group, second indoor side heat exchanger (42), first indoor side heat exchanger (41) reach second indoor side 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 exchanger group with on the first trunk between outdoor side heat exchanger (20), second indoor side heat exchanger (42) through the second branch road with first trunk road 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 flow back into the compressor (10) through the first indoor heat exchanger (41) and the second indoor heat exchanger (42) in parallel; when the temperature-adjusting dehumidifying air-conditioning system operates in a reheating dehumidifying mode, refrigerant discharged by the compressor (10) flows back into the compressor (10) through the first indoor heat exchanger (41) after flowing out of the outdoor heat exchanger (20) and the second indoor heat exchanger (42) in parallel, the flow path control valve group comprises a one-way valve (70), and the one-way valve (70) is cut off in the refrigerating mode and is communicated in the reheating dehumidifying mode.
2. The temperature conditioning, dehumidification and air conditioning system of claim 1, wherein the flow control valve block is further configured to: when the temperature-adjusting dehumidifying air-conditioning system operates in a heating mode, the refrigerant discharged by the compressor (10) flows back into the compressor (10) through the outdoor heat exchanger (20) after flowing out through the first indoor heat exchanger (41) and the second indoor heat exchanger (42) in parallel, the flow path control valve group comprises a one-way valve (70), and the one-way valve (70) is communicated in the heating mode.
3. The hvac system of claim 2, wherein 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 first cylinder and the second cylinder exhausts are combined at an exhaust port (11) of the compressor (10).
4. The temperature-regulating dehumidifying air-conditioning system according to claim 3, wherein the flow path control valve group further comprises a first four-way reversing valve (51) and a second four-way reversing valve (52), wherein a first port of the first four-way reversing valve (51) communicates with a side of the first indoor-side heat exchanger (41) away from the first throttling element (31), a second port communicates with a second port of the second four-way reversing valve (52) and the exhaust port (11) in a collective manner, a third port communicates with a side of the outdoor-side heat exchanger (20) away from the first throttling element (31), and a fourth port communicates with a first end of the check valve (70) and the first intake port (12) in a collective manner; the first port of the second four-way reversing valve (52) is communicated with one side, far away from the second throttling element (32), of the second indoor-side heat exchanger (42), the third port of the second four-way reversing valve is communicated with the second end of the one-way valve (70), the fourth port of the second four-way reversing valve is communicated with the second suction port (13), in the refrigerating mode, the first port of the first four-way reversing valve (51) is communicated with the fourth port, the second port of the first four-way reversing valve is communicated with the third port, the first port of the second four-way reversing valve (52) is communicated with the fourth port, the second port of the second four-way reversing valve (52) is communicated with the third port, in the heating mode, the first port of the first four-way reversing valve (51) is communicated with the second port, the third port of the second four-way reversing valve is communicated with the fourth port, in the reheating mode, the first port of the first four-way reversing valve (51) is communicated with the fourth port, The second port is communicated with the third port, the first port of the second four-way reversing valve (52) is communicated with the second port, and the third port is communicated with the fourth port.
5. The system according to claim 3, wherein the first indoor heat exchanger (41) communicates with the first main circuit via a first branch, 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 flow path switching of the first four-way reversing valve (51) and the second four-way reversing valve (52) according to the acquired operation mode.
9. The control method according to claim 8,
when the operation mode is a refrigeration mode, controlling the first port and the fourth port of the first four-way reversing valve (51) to be communicated, controlling the second port and the third port to be communicated, and controlling the first port and the fourth port of the second four-way reversing valve (52) to be communicated, and controlling the second port and the third port to be communicated;
when the operation mode is a heating mode, controlling the first port of the first four-way reversing valve (51) to be communicated with the second port and the third port to be communicated with the fourth port, and controlling the first port of the second four-way reversing valve (52) to be communicated with the second port and the third port to be communicated with the fourth port;
and when the operation mode is a reheating and dehumidifying mode, controlling the first port and the fourth port of the first four-way reversing valve (51) to be communicated, controlling the second port and the third port to be communicated, and controlling the first port and the second port of the second four-way reversing valve (52) to be communicated, and controlling the third port and the fourth port to be communicated.
10. The control method according to claim 9,
when the operation mode is a reheating 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 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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| CN202210277869.5A CN114484623A (en) | 2022-03-21 | 2022-03-21 | Temperature-adjusting dehumidifying air-conditioning system and control method thereof |
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Cited By (1)
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| 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 |
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