CN111765568A - Air conditioning system and control method thereof - Google Patents
Air conditioning system and control method thereof Download PDFInfo
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- CN111765568A CN111765568A CN202010634116.6A CN202010634116A CN111765568A CN 111765568 A CN111765568 A CN 111765568A CN 202010634116 A CN202010634116 A CN 202010634116A CN 111765568 A CN111765568 A CN 111765568A
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 77
- 238000000034 method Methods 0.000 title claims abstract description 28
- 238000007791 dehumidification Methods 0.000 claims abstract description 56
- 238000003303 reheating Methods 0.000 claims abstract description 30
- 238000005057 refrigeration Methods 0.000 claims abstract description 18
- 238000001816 cooling Methods 0.000 claims description 38
- 238000001514 detection method Methods 0.000 claims description 3
- 239000012530 fluid Substances 0.000 claims description 3
- 230000005494 condensation Effects 0.000 abstract description 8
- 238000009833 condensation Methods 0.000 abstract description 8
- 230000007704 transition Effects 0.000 abstract description 6
- 238000004781 supercooling Methods 0.000 abstract description 5
- 239000003507 refrigerant Substances 0.000 description 28
- 238000010586 diagram Methods 0.000 description 14
- 230000006835 compression Effects 0.000 description 9
- 238000007906 compression Methods 0.000 description 9
- 238000001704 evaporation Methods 0.000 description 7
- 230000008020 evaporation Effects 0.000 description 7
- 239000007788 liquid Substances 0.000 description 7
- 230000002427 irreversible effect Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000005516 engineering process Methods 0.000 description 4
- 238000012986 modification Methods 0.000 description 3
- 230000004048 modification Effects 0.000 description 3
- 229920006395 saturated elastomer Polymers 0.000 description 3
- 230000000712 assembly Effects 0.000 description 2
- 238000000429 assembly Methods 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000003247 decreasing effect Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
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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
- F24F5/00—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater
- F24F5/0007—Air-conditioning systems or apparatus not covered by F24F1/00 or F24F3/00, e.g. using solar heat or combined with household units such as an oven or water heater cooling apparatus specially adapted for use in air-conditioning
- F24F5/001—Compression cycle type
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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
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
- F24F11/63—Electronic processing
- F24F11/65—Electronic processing for selecting an operating mode
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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
- F24F11/72—Control systems characterised by their outputs; Constructional details thereof for controlling the supply of treated air, e.g. its pressure
-
- 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
- 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
-
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Signal Processing (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Fuzzy Systems (AREA)
- Mathematical Physics (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention provides an air conditioning system and a control method thereof, wherein the air conditioning system comprises: the indoor heat exchanger comprises a compressor, an indoor first heat exchanger and an indoor second heat exchanger; the valve bank structure can enable the following switching control through the valve bank structure: in the refrigeration mode, the indoor first heat exchanger is communicated to an air suction port of the compressor, and the indoor second heat exchanger is communicated to the air suction port of the compressor; in the reheating dehumidification mode, the indoor first heat exchanger is communicated to an air suction port of the compressor, and the indoor second heat exchanger is communicated to an air exhaust port of the compressor; the indoor first heat exchanger and the indoor second heat exchanger are arranged adjacently, and air flow can sequentially flow through the indoor first heat exchanger and the indoor second heat exchanger to complete heat exchange. According to the invention, when the dehumidification mode in a transition season operates, the leeward side heat exchanger is converted into the reheating heat exchanger through the control of the valve, so that the air supply temperature during the dehumidification mode operates is increased, the condensation temperature is reduced, the supercooling degree of the outlet of the condenser is increased, and the energy efficiency of the system is improved.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system and a control method thereof.
Background
When the conventional refrigeration air-conditioning system shown in fig. 1 is used for refrigeration in summer or dehumidification operation in a transition season, in order to meet the dehumidification requirement, the evaporation temperature is generally required to be reduced to be lower than the dew point temperature of return air, and the temperature difference between the two temperatures is large.
When the conventional air conditioning system is used for dehumidifying operation in plum rain in the middle and lower reaches of Yangtze river in China or in 'south China' in the period of returning to south, the problem that the human body feels uncomfortable due to too low air outlet temperature and indoor temperature can occur.
In addition, the conventional air conditioning system has low evaporation temperature during dehumidification operation, namely, the compressor pressure ratio is high, and the system energy efficiency is low. In order to solve the problem of low energy efficiency of the system during dehumidification operation of the air conditioning system, patent No. CN105115181B proposes a dual-evaporation-temperature system, as shown in fig. 2, that is, two high-temperature evaporators and two low-temperature evaporators are respectively arranged in a single or same air flow channel, indoor return air exchanges heat through the high-temperature evaporators and the low-temperature evaporators respectively, and outlets of the two evaporators are connected with two independent compression cylinders of a compressor respectively, so as to ensure that the evaporation temperature of the high-temperature evaporator is higher than that of a conventional system, and improve the energy efficiency of the system. However, when the system is used for dehumidification, the conditions of too low air outlet temperature and too low indoor temperature exist, and the comfort of a human body is influenced.
The problem of reduced comfort caused by too low air-conditioner outlet air temperature and indoor temperature when an air-conditioning system in the prior art performs dehumidification operation is solved; and the invention also discloses a control method of the air conditioning system.
Disclosure of Invention
Therefore, the technical problem to be solved by the present invention is to overcome the defects of decreased comfort and low system energy efficiency caused by too low air-out temperature and indoor temperature of an air conditioner when the air conditioner system performs dehumidification operation in the prior art, thereby providing an air conditioner system and a control method thereof.
In order to solve the above problems, the present invention provides an air conditioning system including:
the indoor heat exchanger comprises a compressor, an indoor first heat exchanger and an indoor second heat exchanger;
still include valves structure, through valves structure's switching control can make: the indoor first heat exchanger is communicated to an air suction port of the compressor, and the indoor second heat exchanger is communicated to the air suction port of the compressor in a refrigeration mode; the indoor first heat exchanger is communicated to an air suction port of the compressor, and the indoor second heat exchanger is communicated to an air exhaust port of the compressor in the reheating and dehumidifying mode;
the indoor first heat exchanger and the indoor second heat exchanger are arranged adjacently, and air flow can sequentially flow through the indoor first heat exchanger and the indoor second heat exchanger to complete heat exchange.
Preferably, the air conditioning system further comprises an outdoor first heat exchanger, and a first pipeline communicated with one end of the indoor first heat exchanger and a second pipeline communicated with one end of the indoor second heat exchanger are merged and then communicated to the outdoor first heat exchanger through a third pipeline, the first pipeline is provided with a first throttling device, and the second pipeline is provided with a second throttling device.
Preferably, the compressor comprises a first cylinder and a second cylinder, and the exhaust port comprises a first exhaust port; the intake ports include a first intake port on the first cylinder and a second intake port on the second cylinder:
in the cooling mode: the indoor first heat exchanger is communicable to the first suction port, the indoor second heat exchanger is communicable to the second suction port, and the outdoor first heat exchanger is communicable to the first exhaust port;
in the reheat dehumidification mode: the indoor first heat exchanger is connectable to the first intake, the indoor second heat exchanger is connectable to the first exhaust, and the outdoor first heat exchanger is connectable to the first exhaust.
Preferably, the compressor further comprises a third cylinder having a third suction port;
and a flash evaporator is also arranged on the third pipeline, the inlet end of the flash evaporator is communicated with the outdoor first heat exchanger, a main throttling device is also arranged between the flash evaporator and the outdoor first heat exchanger, and the gas outlet end of the flash evaporator is communicated to the third air suction port through a fourth pipeline.
Preferably, the valve set structure includes a four-way valve including a C pipe, a D pipe, an E pipe, and an S pipe, wherein the C pipe is communicated with the first suction port, the D pipe is communicated with the first exhaust port, the E pipe is communicated with the indoor second heat exchanger, and the S pipe is communicated with the second suction port.
Preferably, the first exhaust port is communicated to the outdoor first heat exchanger through a fifth pipeline, and the D pipe is communicated to the fifth pipeline through a sixth pipeline; the indoor first heat exchanger is communicated to the first air suction port through a seventh pipeline, the pipe C is communicated to the seventh pipeline through an eighth pipeline, and a check valve which only allows fluid to flow to the pipe C is arranged on the eighth pipeline; the indoor second heat exchanger is communicated to the E pipe through the ninth pipeline.
Preferably, the first exhaust port is communicated to the outdoor first heat exchanger through a fifth line, and the indoor first heat exchanger is communicated to the first intake port through a seventh line:
the valve group structure comprises a first two-way valve, a second two-way valve and a third two-way valve, one end of the first two-way valve is communicated to the second air suction port through a tenth pipeline, and the other end of the first two-way valve is communicated to the indoor second heat exchanger through an eleventh pipeline; one end of the second two-way valve is communicated to the tenth pipeline, and the other end of the second two-way valve is communicated to the seventh pipeline; one end of the third two-way valve is communicated to the fifth pipeline, and the other end of the third two-way valve is communicated to the eleventh pipeline.
Preferably, the first exhaust port is communicated to the outdoor first heat exchanger through a fifth line, and the indoor first heat exchanger is communicated to the first intake port through a seventh line:
the valve group structure comprises a first three-way valve and a fourth two-way valve, wherein a first end of the first three-way valve is communicated to the second air suction port through a twelfth pipeline, a second end of the first three-way valve is communicated to the indoor second heat exchanger through a thirteenth pipeline, and a third end of the first three-way valve is communicated to the seventh pipeline through a fourteenth pipeline; one end of the fourth two-way valve is communicated to the thirteenth pipeline, and the other end of the fourth two-way valve is communicated to the fifth pipeline.
Preferably, the compressor further comprises a second exhaust port, the air conditioning system further comprises an outdoor second heat exchanger, one end of the outdoor second heat exchanger is communicated with the second exhaust port, one end of the outdoor first heat exchanger is communicated with the first exhaust port, and the other end of the outdoor second heat exchanger is communicated with the third pipeline after being converged with the other end of the outdoor first heat exchanger; the outdoor first heat exchanger and the outdoor second heat exchanger are arranged adjacently, and air flow can sequentially flow through the outdoor first heat exchanger and the outdoor second heat exchanger to complete heat exchange.
Preferably, the air conditioning system further comprises an oil return device, wherein the oil return device is arranged at the second air outlet and can enable oil in the gas exhausted by the second air outlet to flow back to the bottom of the inner cavity of the compressor.
The present invention also provides a control method suitable for the air conditioning system described in any one of the above, including:
a detection step, which is used for detecting the operation mode of the air conditioning system;
judging, wherein the operation modes comprise a refrigeration mode and a reheating dehumidification mode, and the current operation mode of the air conditioner is judged to belong to any one of the modes;
and a control step, when the air conditioning system needs to operate in a reheating and dehumidifying mode: and the indoor first heat exchanger is communicated to an air suction port of the compressor and the indoor second heat exchanger is communicated to an air exhaust port of the compressor through switching control of the valve group structure.
Preferably, when the valve group structure comprises a four-way valve, a pipe C of the four-way valve is controlled to be communicated with a pipe S, and a pipe D of the four-way valve is controlled to be communicated with a pipe E, so that the air conditioning system operates in a reheating and dehumidifying mode;
when the valve group structure comprises a first two-way valve, a second two-way valve and a third two-way valve, controlling the first two-way valve to be closed, and controlling the second two-way valve and the third two-way valve to be opened, so that the air-conditioning system operates in a reheating and dehumidifying mode;
when the valve group structure comprises a first three-way valve and a fourth two-way valve, the first end and the third end of the first three-way valve are controlled to be connected, the second end is disconnected, and the fourth two-way valve is controlled to be opened at the same time, so that the air conditioning system operates in a reheating and dehumidifying mode.
Preferably, the controlling step is further configured to, when the air conditioning system needs to operate in the cooling mode: and the indoor first heat exchanger is communicated to an air suction port of the compressor through switching control of the valve group structure, and the indoor second heat exchanger is communicated to the air suction port of the compressor.
Preferably, when the valve set structure comprises a four-way valve, a pipe C of the four-way valve is controlled to be communicated with a pipe D, and a pipe E of the four-way valve is controlled to be communicated with a pipe S, so that the air-conditioning system operates in a cooling mode;
when the valve group structure comprises a first two-way valve, a second two-way valve and a third two-way valve, controlling the first two-way valve to be opened, and controlling the second two-way valve and the third two-way valve to be closed, so that the air-conditioning system operates in a refrigeration mode;
when the valve group structure comprises a first three-way valve and a fourth two-way valve, the first end and the second end of the first three-way valve are controlled to be connected, the third end is disconnected, and meanwhile, the fourth two-way valve is controlled to be closed, so that the air-conditioning system operates in a cooling mode.
The air conditioning system and the control method thereof provided by the invention have the following beneficial effects:
1. according to the invention, through the special valve group structure, under the condition of high indoor humidity in a transition season, the indoor first heat exchanger can be communicated to the air suction port of the compressor, the indoor second heat exchanger is communicated to the air exhaust port of the compressor, and air flow can sequentially flow through the indoor first heat exchanger and the indoor second heat exchanger to complete heat exchange, so that the first indoor heat exchanger positioned upstream in the air flow direction can cool and dehumidify air, the second indoor heat exchanger positioned downstream in the air flow can reheat the air, and the air outlet temperature and the indoor temperature are controlled while dehumidification is carried out, so that the indoor comfort is improved; meanwhile, the condensation temperature is reduced, the supercooling degree of the outlet of the condenser is increased, and the energy efficiency of the system is improved;
2. in addition, two evaporators are arranged on the evaporator side, and the indoor return air is subjected to gradient cooling or dehumidification treatment during refrigeration or dehumidification operation, so that irreversible loss in the heat exchange process is reduced, and the system energy efficiency is improved;
3. the invention can also adopt a parallel compression technology, reduce the specific enthalpy of the evaporator inlet, improve the refrigerating output per unit mass and further improve the system energy efficiency;
4. the invention realizes the switching of different operation modes by using valve assemblies as few as possible through a reasonable control method.
Drawings
Fig. 1 is a system configuration diagram of a conventional single temperature air conditioning system of the first prior art;
fig. 2 is a system configuration diagram of a conventional single temperature air conditioning system of the second prior art;
FIG. 3 is a system block diagram of the air conditioning system of the present invention in a cooling mode in a primary embodiment;
FIG. 4 is a system diagram of the main embodiment of the air conditioning system of the present invention in a reheat dehumidification mode;
FIG. 5 is a system block diagram of an alternative embodiment of the air conditioning system of the present invention in a cooling mode;
FIG. 6 is a block diagram of an alternative embodiment of a reheat dehumidification mode of an air conditioning system in accordance with the present invention;
FIG. 7 is a system block diagram of an alternative embodiment of the air conditioning system of the present invention in the cooling mode two;
FIG. 8 is a block diagram of an alternative embodiment of a secondary reheat dehumidification mode of an air conditioning system of the present invention;
FIG. 9 is a system block diagram of an alternative embodiment of the air conditioning system of the present invention in a third cooling mode;
FIG. 10 is a block diagram of an alternative embodiment of the air conditioning system of the present invention in a three reheat dehumidification mode;
FIG. 11 is a system block diagram of an alternative embodiment of the air conditioning system of the present invention in a four cooling mode;
fig. 12 is a system configuration diagram of an alternative embodiment of the air conditioning system of the present invention in a four reheat dehumidification mode.
FIG. 13 is a system block diagram of an alternate embodiment of the air conditioning system of the present invention in a five cooling mode;
FIG. 14 is a block diagram of an alternative embodiment of a five reheat dehumidification mode air conditioning system of the present invention
The reference numerals are represented as:
10. a compressor; 11. a third air suction port; 12. a first air intake port; 13. a second air suction port; 14. a first exhaust port; 15. a second exhaust port; 16. an oil return device; 17. an oil return assembly; 20. an outdoor first heat exchanger; 21. an outdoor second heat exchanger; 30. a primary throttling device; 31. a first throttling device; 32. a second throttling device; 4. a flash tank; 50. an indoor first heat exchanger; 51. an indoor second heat exchanger; 60. a four-way valve; 70. a one-way valve; 80. a first two-way valve; 81. a second two-way valve; 82. a third two-way valve; 83. a fourth two-way valve; 90. a first three-way valve; 101. a first pipeline; 102. a second pipeline; 103. a third pipeline; 104. a fifth pipeline; 105. a sixth pipeline; 106. a seventh pipeline; 107. an eighth pipeline; 108. a ninth conduit; 109. a fourth pipeline; 110. a tenth pipeline; 111. an eleventh line; 112. a twelfth pipeline; 113. a thirteenth pipeline; 114. a fourteenth line.
Detailed Description
As shown in fig. 3 to 14, the present invention provides an air conditioning system, which includes:
a compressor 10, an indoor first heat exchanger 50, and an indoor second heat exchanger 51;
still include valves structure, through valves structure's switching control can make: the indoor first heat exchanger 50 is communicated to a suction port of the compressor 10, and the indoor second heat exchanger 51 is communicated to the suction port of the compressor 10 in the cooling mode; the indoor first heat exchanger 50 is communicated to the suction port of the compressor 10, and the indoor second heat exchanger 51 is communicated to the exhaust port of the compressor 10 in the reheating and dehumidifying mode;
the indoor first heat exchanger 50 and the indoor second heat exchanger 51 are arranged adjacently, and air flow can sequentially flow through the indoor first heat exchanger 50 and the indoor second heat exchanger 51 to complete heat exchange.
The two evaporators are arranged on the evaporator side, and the indoor return air is subjected to gradient cooling or dehumidification treatment during refrigeration or dehumidification operation, so that the irreversible loss in the heat exchange process is reduced, and the system energy efficiency is improved; the indoor heat exchanger is communicated with an air suction port of the compressor, the indoor second heat exchanger is communicated with an air exhaust port of the compressor, and air flow can sequentially flow through the indoor first heat exchanger and the indoor second heat exchanger to finish heat exchange, so that the first indoor heat exchanger positioned at the upstream of the air flow direction cools and dehumidifies the air, the second indoor heat exchanger positioned at the downstream of the air flow reheats the air, and the air outlet temperature and the indoor temperature are controlled while dehumidification is performed, so that the indoor comfort is improved;
in the reheating dehumidification mode, the inlet air temperature of the indoor second heat exchanger 51 is far lower than the outdoor environment temperature, so that the condensation temperature is reduced, and the outlet supercooling degree is increased; meanwhile, the indoor second heat exchanger shares part of condensation load, so that the condensation load of the outdoor first heat exchanger 20 is reduced, the condensation temperature of the outdoor first heat exchanger is also reduced, and the energy efficiency of the system is improved.
The invention is characterized in that:
1. two evaporators are arranged on the evaporator side, and the energy efficiency of the system is improved by performing gradient cooling or dehumidification treatment on indoor return air under the condition of ensuring the refrigerating capacity and the dehumidifying capacity of the system;
2. by adopting a parallel compression technology, the specific enthalpy of the inlet of the evaporator is reduced, the refrigerating capacity per unit mass is improved, and the energy efficiency of the system is improved.
3. When dehumidification is performed in a transition season, the reheating dehumidification operation mode is entered through switching control of the valve group structure, so that the dehumidification effect is ensured, the indoor environment comfort is improved, the condensation temperature is reduced, the condenser outlet supercooling degree is increased, and the system energy efficiency is improved;
4. through a reasonable control method, the switching of different operation modes is realized by using valve assemblies as few as possible.
Preferably, the air conditioning system further comprises an outdoor first heat exchanger 20, and a first pipeline 101 communicated with one end of the indoor first heat exchanger 50 and a second pipeline 102 communicated with one end of the indoor second heat exchanger 51 are merged and communicated to the outdoor first heat exchanger 20 through a third pipeline 103, wherein a first throttling device 31 is arranged on the first pipeline 101, and a second throttling device 32 is arranged on the second pipeline 102. The outdoor first heat exchanger can effectively play a role in releasing heat and condensing towards the outside, the first throttling device on the first pipeline can play a role in throttling and reducing pressure for the refrigerant of the pipeline, and the second throttling device on the second pipeline can play a role in throttling and reducing pressure for the refrigerant of the pipeline; the first throttling device arranged on the first pipeline between the outdoor heat exchanger and the first indoor heat exchanger and the second throttling device arranged on the second pipeline between the outdoor heat exchanger and the second indoor heat exchanger can effectively realize double evaporation temperatures, and the irreversible loss in the heat exchange process is reduced and the system energy efficiency is improved by carrying out gradient cooling or dehumidification treatment on indoor return air; meanwhile, under the working condition of high humidity in a transition season, a reheating dehumidification mode is operated, the indoor second heat exchanger is converted into a low-temperature condenser, and the air outlet temperature and the indoor temperature are controlled while dehumidification is performed, so that the indoor comfort is improved; meanwhile, the condensation temperature is reduced, the supercooling degree of the outlet of the condenser is increased, and the energy efficiency of the system is improved.
Preferably, the compressor 10 includes a first cylinder and a second cylinder, and the exhaust port includes a first exhaust port 14; the intake ports include a first intake port 12 on the first cylinder and a second intake port 13 on the second cylinder:
in the cooling mode: the indoor first heat exchanger 50 is connectable to the first suction port 12, the indoor second heat exchanger 51 is connectable to the second suction port 13, and the outdoor first heat exchanger 20 is connectable to the first exhaust port 14;
in the reheat dehumidification mode: the indoor first heat exchanger 50 is connectable to the first intake port 12, the indoor second heat exchanger 51 is connectable to the first exhaust port 14, and the outdoor first heat exchanger 20 is connectable to the first exhaust port 14.
The compressor provided with at least two independent cylinders comprises a first air suction port, a second air suction port and a first exhaust port, and indoor return air can be subjected to step cooling or dehumidification through the communication of an indoor first heat exchanger and the first air suction port and the communication of an indoor second heat exchanger and the second air suction port; through indoor first heat exchanger and the indoor second heat exchanger of first air inlet intercommunication and first exhaust port intercommunication for first indoor heat exchanger cools down the dehumidification to the air, and second indoor heat exchanger carries out reheat to the air, thereby control air-out temperature and indoor temperature when dehumidifying and promote indoor travelling comfort.
As an alternative to the first embodiment, as shown in fig. 5 to 6, it is preferable that the compressor 10 further includes a third cylinder having a third suction port 11;
a flash evaporator 4 is further arranged on the third pipeline 103, the inlet end of the flash evaporator 4 is communicated with the outdoor first heat exchanger 20, a main throttling device 30 is further arranged between the flash evaporator 4 and the outdoor first heat exchanger 20, and the gas outlet end of the flash evaporator 4 is communicated to the third suction port 11 through a fourth pipeline 109. The parallel compression technology adopted by the invention can reduce the specific enthalpy of the evaporator inlet, improve the refrigerating capacity per unit mass and further improve the system energy efficiency. The compressor 10 is provided with three mutually independent compression cylinders which are respectively connected with three air suction ports 11, 12 and 13, wherein the air suction ports 11 are connected with a gas outlet connecting pipeline of the flash tank 4; the displacement of two compression cylinders connected with the two air suction ports 12 and 13 is Va and Vb respectively, and the value of (Va/Vb) is between 0.5 and 2; the exhaust ports of the three compression cylinders are the same exhaust port 14, and exhaust gas is uniformly exhausted after being mixed.
3-6, 11-14, preferably, the valve block structure comprises a four-way valve 60, the four-way valve 60 comprising a C pipe, a D pipe, an E pipe and an S pipe, wherein the C pipe is communicated with the first suction port 12, the D pipe is communicated with the first exhaust port 14, the E pipe is communicated with the indoor second heat exchanger 51, and the S pipe is communicated with the second suction port 13. The preferred structure of the main embodiment, the first alternative embodiment and the fourth alternative embodiment of the present invention is that the effective switching between the cooling mode and the reheat dehumidification mode is accomplished by the four-way valve and the corresponding connection relationship.
Preferably, the first exhaust port 14 is connected to the outdoor first heat exchanger 20 through a fifth line 104, and the D-pipe is connected to the fifth line 104 through a sixth line 105; the indoor first heat exchanger 50 is communicated to the first air suction port 12 through a seventh pipeline 106, the pipe C is communicated to the seventh pipeline 106 through an eighth pipeline 107, and a check valve 70 which only allows fluid to flow to the pipe C is arranged on the eighth pipeline 107; the indoor second heat exchanger 51 is connected to the E-tube via the ninth line 108. The four-way valve structure is a further preferable structure form when the four-way valve structure is provided, namely, especially, the eighth pipeline is arranged, so that the low-temperature refrigerant passing through the indoor first heat exchanger 50 can enter the first air suction port and the second air suction port respectively in two ways in a reheating and dehumidifying mode, the evaporation temperature is reduced, and meanwhile, the mass flow of the refrigerant passing through the indoor first heat exchanger is increased, and the dehumidifying effect is improved; and the refrigerant from the D pipe of the four-way valve flows directly back to the first suction port 12 through the C pipe and the eighth pipe in sequence in the cooling mode can be effectively prevented by the arrangement of the check valve.
The refrigeration system shown in fig. 5 to 6 comprises a compressor 10, an outdoor first heat exchanger 20, a main throttle device 30, a first throttle device 31 and a second throttle device 32, a flash tank 4, an indoor first heat exchanger 50 and an indoor second heat exchanger 51, a four-way valve 60, a check valve 70, and a fan disposed in the vicinity of the heat exchangers, etc.
Wherein the D pipe of the four-way valve 60 is connected with the first exhaust port 14 of the compressor, the E pipe is connected with the outlet of the indoor second heat exchanger 51, the S pipe is connected with the second air inlet 13 of the compressor, and the C pipe is connected with the outlet of the check valve 70; the indoor first heat exchanger 50 and the indoor second heat exchanger 51 are connected with the liquid outlet of the flash evaporator through the first throttling device 31 and the second throttling device 32, the outlet of the indoor first heat exchanger 50 is connected with the first air suction port 12 of the compressor, and the outlet of the indoor second heat exchanger 51 is connected with the E pipe of the four-way valve 60.
During the cooling mode operation, as shown in FIG. 5, the four-way valve is not energized, the tubes S and E of the four-way valve 60 are connected, and the tubes C and D are connected. High-pressure gas compressed by the compressor enters the outdoor first heat exchanger 20, heat is released in an outdoor condenser and condensed into high-pressure refrigerant liquid, the high-pressure refrigerant liquid enters the flash evaporator 4 after being throttled by the main throttling device 30, saturated gaseous refrigerant flashed is sucked into a third air suction port 11 of the compressor through a fourth pipeline and is discharged after being compressed, liquid saturated refrigerant separated by the flash evaporator is divided into two paths and respectively enters the first throttling device 31 and the second throttling device 32, the throttled low-pressure two-phase refrigerant absorbs heat and is gasified in the indoor first heat exchanger 50 and the indoor second heat exchanger 51 respectively, the refrigerant coming out of the indoor first heat exchanger 50 enters a first air suction port 12 of the compressor, and the gaseous refrigerant coming out of the indoor second heat exchanger 51 enters a second air suction port 13 of the compressor through an E pipe and an S pipe of the four-way valve 60 in sequence, the whole refrigeration cycle is completed after the compression of the compressor.
In the refrigeration mode, on one hand, the first heat exchanger 50 and the indoor second heat exchanger 51 sequentially perform step cooling or dehumidification on return air, so that irreversible loss in the heat exchange process is reduced, and the system energy efficiency is improved; on the other hand, the parallel compressor reduces the specific enthalpy of the evaporator inlet, increases the refrigerating capacity per unit mass, and further improves the system energy efficiency.
In the reheat dehumidification mode operation, as shown in fig. 6, the four-way valve is energized, and the tube C and the tube S of the four-way valve are connected, and the tube D and the tube E are connected. The refrigerant is divided into two paths by the high-pressure gas compressed by the compressor, one path of the high-pressure gas sequentially enters the indoor second heat exchanger 51 through the D pipe and the E pipe of the four-way valve 60, the high-pressure gas is throttled and depressurized by the second throttling device 32 after being condensed in the indoor second heat exchanger 51, the other path of the high-temperature high-pressure refrigerant enters the outdoor first heat exchanger 20 to be condensed into high-pressure liquid refrigerant, the high-pressure liquid refrigerant enters the flash tank 4 after being throttled by the main throttling device 30, the liquid saturated refrigerant coming out of the flash tank 4 is converged with the two-phase refrigerant throttled and depressurized by the second throttling device 32, and then the high-temperature high-pressure refrigerant is throttled again by the first throttling device 31 and enters the indoor. The low-temperature refrigerant gas coming out of the indoor first heat exchanger 50 is divided into two paths again, one path directly enters the first suction port 12 of the compressor 10, the other path passes through the check valve 70, sequentially passes through the four-way valve C pipe and the S pipe, and finally enters the second suction port 13 of the compressor 10. Gaseous refrigerant from the flash tank enters the third suction port 11 of compressor 10. The refrigerant introduced into the first, second, and third suction ports of the compressor is compressed and discharged, thereby forming a reheat dehumidification cycle.
At this time, the indoor first heat exchanger 50 serves as an evaporator, the indoor second heat exchanger 51 serves as a condenser, indoor return air is cooled, dehumidified and reheated sequentially through the indoor first heat exchanger and the indoor second heat exchanger, and therefore the air outlet temperature and the indoor temperature are controlled while dehumidification is achieved, and indoor comfort is improved. Meanwhile, a parallel compression technology is adopted, the specific enthalpy of an evaporator inlet is reduced, the refrigerating capacity per unit mass is improved, and the system energy efficiency is improved.
As shown in fig. 3-4, the main embodiment is different from the first alternative embodiment in that the three-cylinder compressor in the first alternative embodiment is replaced by the double cylinder, the flash evaporator is removed, and the system is simplified, the first alternative embodiment is that the flash evaporator is added on the basis of the main embodiment, the double cylinder compressor is changed into the three cylinders, and the refrigeration mode and the reheating dehumidification mode of the first alternative embodiment are operated in the same way as the main embodiment.
7-8, preferably the first exhaust 14 is connected to the outdoor first heat exchanger 20 by a fifth conduit 104 and the indoor first heat exchanger 50 is connected to the first intake 12 by a seventh conduit 106:
the valve group structure comprises a first two-way valve 80, a second two-way valve 81 and a third two-way valve 82, one end of the first two-way valve 80 is communicated to the second air suction port 13 through a tenth pipeline 110, and the other end of the first two-way valve 80 is communicated to the indoor second heat exchanger 51 through an eleventh pipeline 111; one end of the second two-way valve 81 is communicated to the tenth pipeline 110, and the other end is communicated to the seventh pipeline 106; the third two-way valve 82 has one end connected to the fifth pipeline 104 and the other end connected to the eleventh pipeline 111.
This is a further preferable configuration of the present invention having the first, second, and third two-way valve structures, that is, in particular, in the reheat dehumidification mode, the high-temperature and high-pressure refrigerant can be introduced into the indoor second heat exchanger 51 through the third three-way valve to reheat the air cooled and dehumidified by the indoor first heat exchanger, thereby increasing the supply air temperature and the indoor ambient temperature. The pipeline 106 and the pipeline 110 where the second two-way valve is located can divide the low-temperature refrigerant of the indoor first heat exchanger 50 into two paths to respectively enter the first air suction port and the second air suction port, so that the mass flow of the refrigerant flowing through the indoor first heat exchanger is increased while the evaporation temperature is reduced, and the dehumidification effect is improved.
Fig. 7 and 8 show an alternative second embodiment of the present disclosure, which mainly replaces the four-way valve 60 and the check valve 70 in the main embodiment with three two-way valves (preferably solenoid valves), namely, a first two-way valve 80, a second two-way valve 81 and a third two-way valve 82, and the three two-way valves are used to switch the modes, when the cooling mode is operated, the first two-way valve 80 is opened, the second two-way valve 81 and the third two-way valve 82 are closed, when the reheating and dehumidifying mode is operated, the first two-way valve 80 is closed, the second two-way valve 81 and the third two-way valve 82 are opened, and the other operation modes are the same as the main embodiment.
In an alternative embodiment three, as shown in fig. 9-10, preferably the first exhaust 14 is connected to the outdoor first heat exchanger 20 by a fifth conduit 104 and the indoor first heat exchanger 50 is connected to the first intake 12 by a seventh conduit 106:
the valve group structure comprises a first three-way valve 90 and a fourth two-way valve 83, a first end of the first three-way valve 90 is communicated to the second suction port 13 through a twelfth pipeline 112, a second end of the first three-way valve 90 is communicated to the indoor second heat exchanger 51 through a thirteenth pipeline 113, and a third end of the first three-way valve 90 is communicated to the seventh pipeline 106 through a fourteenth pipeline 114; one end of the fourth two-way valve 83 is communicated to the thirteenth pipeline 113, and the other end is communicated to the fifth pipeline 104.
This is a further preferable configuration of the present invention having the first three-way valve and the fourth two-way valve, that is, in particular, in the reheat dehumidification mode, the fourth two-way valve can introduce the high-temperature and high-pressure refrigerant into the indoor second heat exchanger 51 to reheat the air cooled and dehumidified by the indoor first heat exchanger 50, thereby improving the comfort of the indoor environment. The first end and the third end of the first three-way valve are communicated, and the low-temperature refrigerant of the indoor first heat exchanger 50 can be divided into two paths through the pipeline 106 to respectively enter the first air suction port and the second air suction port, so that the mass flow of the refrigerant flowing through the indoor first heat exchanger is increased while the evaporation temperature is reduced, and the dehumidification effect is improved.
Fig. 9 and 10 show an alternative third embodiment of the present disclosure, in which two-way valves (a first two-way valve 80 and a second two-way valve 81) in the second embodiment are replaced with a first three-way valve 90, so as to save cost and simplify the system, and when in cooling operation, a first end and a second end of the first three-way valve 90 are connected, a third end is closed, and a fourth two-way valve 83 is closed; when the reheating and dehumidifying mode is operated, the first end and the third end of the first three-way valve 90 are connected, the second end is closed, and the valve of the fourth two-way valve 83 is also connected, and other operation modes are the same as those of the main embodiment.
In an alternative embodiment, as shown in fig. 11 to 12, preferably, the compressor 10 further includes a second exhaust port 15, the air conditioning system further includes an outdoor second heat exchanger 21, one end of the outdoor second heat exchanger 21 is communicated with the second exhaust port 15, one end of the outdoor first heat exchanger 20 is communicated with the first exhaust port 14, and the other end of the outdoor second heat exchanger 21 is merged with the other end of the outdoor first heat exchanger 20 and then communicated to the third pipeline 103; the outdoor first heat exchanger 20 and the outdoor second heat exchanger 21 are arranged adjacently, and air flow can sequentially pass through the outdoor first heat exchanger 20 and the outdoor second heat exchanger 21 to complete heat exchange.
Fig. 11 and 12 show an alternative fourth embodiment of the present disclosure, which is to add a discharge port to the compressor in the main embodiment, so that the compressor has two discharge ports, a first discharge port 14 and a second discharge port 15, and an oil return device 16, an oil return assembly 17, two heat exchangers (an outdoor first heat exchanger 20 and an outdoor second heat exchanger 21) outside the compressor, the first discharge port 14 is connected to the outdoor first heat exchanger 20, and the second discharge port 15 is connected to the outdoor second heat exchanger 21, and the other operation modes are the same as the main embodiment.
Fig. 13 and 14 show an alternative fifth embodiment of the present disclosure, which is to replace the three-cylinder compressor with two cylinders, eliminate the flash tank, and simplify the system compared with the alternative fourth embodiment. The cooling mode and the reheat dehumidification mode of this alternative embodiment are operated in the same manner as the main embodiment.
Preferably, the air conditioning system further comprises an oil return device disposed at the second exhaust port 15 to enable oil in the gas discharged from the second exhaust port to flow back to the bottom of the inner cavity of the compressor 10.
The present invention also provides a control method applicable to any one of the air conditioning systems described above, characterized in that: the method comprises the following steps:
a detection step, which is used for detecting the operation mode of the air conditioning system;
judging, wherein the operation modes comprise a refrigeration mode and a reheating dehumidification mode, and the current operation mode of the air conditioner is judged to belong to any one of the modes;
and a control step, when the air conditioning system needs to operate in a reheating and dehumidifying mode: the indoor first heat exchanger 50 is communicated to the suction port of the compressor 10 and the indoor second heat exchanger 51 is communicated to the discharge port of the compressor 10 by switching control of the valve block structure.
The optimal control method is characterized in that when the reheating dehumidification mode is operated in a transition season, the indoor first heat exchanger is used for cooling and dehumidifying indoor return air, the indoor second heat exchanger is used for reheating the cooled and dehumidified return air, and the outlet air temperature and the indoor temperature are controlled while dehumidification is performed, so that the comfort of the indoor environment is improved. And when the conventional refrigeration working condition is adopted, the indoor first heat exchanger and the indoor second heat exchanger are controlled to realize the step cooling or dehumidification of indoor return air, so that the irreversible loss in the heat exchange process is reduced. By the effective control means, the conversion of different operation modes is realized, so that an intelligent and effective control effect is formed.
Preferably, when the valve set structure comprises a four-way valve 60, the connection between the C pipe and the S pipe and the connection between the D pipe and the E pipe of the four-way valve 60 are controlled, so that the air conditioning system operates in a reheating and dehumidifying mode;
when the valve group structure comprises a first two-way valve 80, a second two-way valve 81 and a third two-way valve 82, controlling the first two-way valve 80 to be closed, and controlling the second two-way valve 81 and the third two-way valve 82 to be opened, so that the air conditioning system operates in a reheating and dehumidifying mode;
when the valve set structure includes the first three-way valve 90 and the fourth two-way valve 83, the first end and the third end of the first three-way valve 90 are controlled to be connected, the second end is disconnected, and the fourth two-way valve 83 is controlled to be opened, so that the air conditioning system operates in a reheating and dehumidifying mode.
The optimal control method of the invention is to ensure that the indoor first heat exchanger can be connected to the air suction port of the compressor and the indoor second heat exchanger can be connected to the air exhaust port of the compressor during the reheating dehumidification mode, so that the first indoor heat exchanger cools and dehumidifies the indoor return air, and the second indoor heat exchanger reheats the cooled and dehumidified return air, thereby effectively improving the indoor comfort during dehumidification.
Preferably, the controlling step is further configured to, when the air conditioning system needs to operate in the cooling mode: the indoor first heat exchanger 50 is communicated to a suction port of the compressor 10, and the indoor second heat exchanger 51 is communicated to the suction port of the compressor 10 by switching control of the valve block structure. The optimal control method of the invention ensures that the indoor first heat exchanger and the indoor second heat exchanger become evaporators to finish refrigeration by the control of the valve group structure in the refrigeration mode, thereby realizing step cooling or dehumidification.
Preferably, when the valve set structure comprises a four-way valve 60, the connection between the C pipe and the D pipe and the connection between the E pipe and the S pipe of the four-way valve 60 are controlled, so that the air conditioning system operates in a cooling mode;
when the valve group structure comprises a first two-way valve 80, a second two-way valve 81 and a third two-way valve 82, controlling the first two-way valve 80 to be opened, and controlling the second two-way valve 81 and the third two-way valve 82 to be closed, so that the air-conditioning system operates in a cooling mode;
when the valve set structure includes the first three-way valve 90 and the fourth two-way valve 83, the first end and the second end of the first three-way valve 90 are controlled to be connected, the third end is disconnected, and the fourth two-way valve 83 is controlled to be closed, so that the air conditioning system operates in a cooling mode.
The optimal control method of the invention ensures that the indoor first heat exchanger can be connected to the air suction port of the compressor and the indoor second heat exchanger can be connected to the air suction port of the compressor in the refrigeration mode, thereby realizing step cooling or dehumidification, reducing irreversible loss in the heat exchange process and improving energy efficiency.
The above description is only for the purpose of illustrating the preferred embodiments of the present invention and is not to be construed as limiting the invention, and any modifications, equivalents and improvements made within the spirit and principle of the present invention are intended to be included within the scope of the present invention. The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (14)
1. An air conditioning system characterized by: the method comprises the following steps:
a compressor (10), an indoor first heat exchanger (50) and an indoor second heat exchanger (51);
still include valves structure, through valves structure's switching control can make: the indoor first heat exchanger (50) is communicated to a suction port of the compressor (10) in a cooling mode, and the indoor second heat exchanger (51) is communicated to the suction port of the compressor (10); the indoor first heat exchanger (50) is communicated to an air suction port of the compressor (10) in a reheating and dehumidifying mode, and the indoor second heat exchanger (51) is communicated to an air exhaust port of the compressor (10);
the indoor first heat exchanger (50) and the indoor second heat exchanger (51) are arranged adjacently, and air flow can sequentially flow through the indoor first heat exchanger (50) and the indoor second heat exchanger (51) to complete heat exchange.
2. The air conditioning system of claim 1, wherein:
the air conditioning system further comprises an outdoor first heat exchanger (20), a first pipeline (101) communicated with one end of the indoor first heat exchanger (50) and a second pipeline (102) communicated with one end of the indoor second heat exchanger (51) are converged and then communicated to the outdoor first heat exchanger (20) through a third pipeline (103), a first throttling device (31) is arranged on the first pipeline (101), and a second throttling device (32) is arranged on the second pipeline (102).
3. The air conditioning system of claim 2, wherein:
the compressor (10) includes a first cylinder and a second cylinder, the exhaust port includes a first exhaust port (14); the intake ports include a first intake port (12) on the first cylinder and a second intake port (13) on the second cylinder:
in the cooling mode: the indoor first heat exchanger (50) being connectable to the first suction port (12), the indoor second heat exchanger (51) being connectable to the second suction port (13), the outdoor first heat exchanger (20) being connectable to the first exhaust port (14);
in the reheat dehumidification mode: the indoor first heat exchanger (50) is connectable to the first intake (12), the indoor second heat exchanger (51) is connectable to the first exhaust (14), and the outdoor first heat exchanger (20) is connectable to the first exhaust (14).
4. The air conditioning system of claim 3, wherein:
the compressor (10) further comprises a third cylinder having a third suction port (11);
a flash evaporator (4) is further arranged on the third pipeline (103), the inlet end of the flash evaporator (4) is communicated with the outdoor first heat exchanger (20), a main throttling device (30) is further arranged between the flash evaporator (4) and the outdoor first heat exchanger (20), and the gas outlet end of the flash evaporator (4) is communicated to the third suction port (11) through a fourth pipeline (109).
5. The air conditioning system according to claim 3 or 4, characterized in that:
the valve set structure comprises a four-way valve (60), wherein the four-way valve (60) comprises a pipe C, a pipe D, a pipe E and a pipe S, the pipe C is communicated with the first air suction port (12), the pipe D is communicated with the first exhaust port (14), the pipe E is communicated with the indoor second heat exchanger (51), and the pipe S is communicated with the second air suction port (13).
6. The air conditioning system of claim 5, wherein:
the first exhaust port (14) is communicated to the outdoor first heat exchanger (20) through a fifth pipeline (104), and the D pipe is communicated to the fifth pipeline (104) through a sixth pipeline (105); the indoor first heat exchanger (50) is communicated to the first air suction port (12) through a seventh pipeline (106), the pipe C is communicated to the seventh pipeline (106) through an eighth pipeline (107), and a check valve (70) which only allows fluid to flow to the pipe C is arranged on the eighth pipeline (107); the indoor second heat exchanger (51) is communicated to the E pipe through a ninth pipeline (108).
7. The air conditioning system according to claim 3 or 4, characterized in that:
the first exhaust port (14) is connected to the outdoor first heat exchanger (20) by a fifth line (104), and the indoor first heat exchanger (50) is connected to the first intake port (12) by a seventh line (106):
the valve group structure comprises a first two-way valve (80), a second two-way valve (81) and a third two-way valve (82), one end of the first two-way valve (80) is communicated to the second air suction port (13) through a tenth pipeline (110), and the other end of the first two-way valve (80) is communicated to the indoor second heat exchanger (51) through an eleventh pipeline (111); one end of the second two-way valve (81) is communicated to the tenth pipeline (110), and the other end is communicated to the seventh pipeline (106); one end of the third two-way valve (82) is communicated to the fifth pipeline (104), and the other end is communicated to the eleventh pipeline (111).
8. The air conditioning system according to claim 3 or 4, characterized in that:
the first exhaust port (14) is connected to the outdoor first heat exchanger (20) by a fifth line (104), and the indoor first heat exchanger (50) is connected to the first intake port (12) by a seventh line (106):
the valve group structure comprises a first three-way valve (90) and a fourth two-way valve (83), a first end of the first three-way valve (90) is communicated to the second suction port (13) through a twelfth pipeline (112), a second end of the first three-way valve (90) is communicated to the indoor second heat exchanger (51) through a thirteenth pipeline (113), and a third end of the first three-way valve (90) is communicated to the seventh pipeline (106) through a fourteenth pipeline (114); one end of the fourth two-way valve (83) is communicated to the thirteenth pipeline (113), and the other end is communicated to the fifth pipeline (104).
9. The air conditioning system according to any one of claims 3 to 8, characterized in that:
the compressor (10) further comprises a second exhaust port (15), the air conditioning system further comprises an outdoor second heat exchanger (21), one end of the outdoor second heat exchanger (21) is communicated with the second exhaust port (15), one end of the outdoor first heat exchanger (20) is communicated with the first exhaust port (14), and the other end of the outdoor second heat exchanger (21) is communicated with the third pipeline (103) after being converged with the other end of the outdoor first heat exchanger (20); the outdoor first heat exchanger (20) and the outdoor second heat exchanger (21) are arranged adjacently, and air flow can sequentially flow through the outdoor first heat exchanger (20) and the outdoor second heat exchanger (21) to complete heat exchange.
10. The air conditioning system of claim 9, wherein:
the air conditioning system further comprises an oil return device, wherein the oil return device is arranged at the second air outlet (15) and can enable oil in the gas exhausted by the second air outlet to flow back to the bottom of the inner cavity of the compressor (10).
11. A control method applied to the air conditioning system according to any one of claims 1 to 10, characterized in that: the method comprises the following steps:
a detection step, which is used for detecting the operation mode of the air conditioning system;
judging, wherein the operation modes comprise a refrigeration mode and a reheating dehumidification mode, and the current operation mode of the air conditioner is judged to belong to any one of the modes;
and a control step, when the air conditioning system needs to operate in a reheating and dehumidifying mode: the indoor first heat exchanger (50) is communicated to the air suction port of the compressor (10) and the indoor second heat exchanger (51) is communicated to the air discharge port of the compressor (10) through switching control of a valve group structure.
12. The control method according to claim 11, characterized in that:
when the valve group structure comprises a four-way valve (60), controlling a pipe C of the four-way valve (60) to be communicated with a pipe S and a pipe D of the four-way valve to be communicated with a pipe E, and enabling the air conditioning system to operate in a reheating and dehumidifying mode;
when the valve group structure comprises a first two-way valve (80), a second two-way valve (81) and a third two-way valve (82), controlling the first two-way valve (80) to be closed, and controlling the second two-way valve (81) and the third two-way valve (82) to be opened, so that the air conditioning system operates in a reheating and dehumidifying mode;
when the valve group structure comprises a first three-way valve (90) and a fourth two-way valve (83), the first end and the third end of the first three-way valve (90) are controlled to be connected, the second end is disconnected, and the fourth two-way valve (83) is controlled to be opened at the same time, so that the air conditioning system operates in a reheating and dehumidifying mode.
13. The control method according to claim 11, characterized in that:
and the control step is also used for controlling the air conditioning system to run in the cooling mode: the indoor first heat exchanger (50) is communicated to a suction port of the compressor (10) through switching control of a valve group structure, and the indoor second heat exchanger (51) is communicated to the suction port of the compressor (10).
14. The control method according to claim 13, characterized in that:
when the valve group structure comprises a four-way valve (60), controlling a pipe C of the four-way valve (60) to be communicated with a pipe D and a pipe E of the four-way valve to be communicated with a pipe S, and enabling the air-conditioning system to operate in a cooling mode;
when the valve group structure comprises a first two-way valve (80), a second two-way valve (81) and a third two-way valve (82), controlling the first two-way valve (80) to be opened, and controlling the second two-way valve (81) and the third two-way valve (82) to be closed, so that the air-conditioning system operates in a cooling mode;
when the valve group structure comprises a first three-way valve (90) and a fourth two-way valve (83), the first end and the second end of the first three-way valve (90) are controlled to be connected, the third end is disconnected, and the fourth two-way valve (83) is controlled to be closed at the same time, so that the air-conditioning system operates in a cooling mode.
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| CN112228977A (en) * | 2020-11-18 | 2021-01-15 | 珠海格力电器股份有限公司 | Heat pump system, control method and device thereof, air conditioning equipment and storage medium |
| CN112228977B (en) * | 2020-11-18 | 2024-04-30 | 珠海格力电器股份有限公司 | Heat pump system, control method and device thereof, air conditioning equipment and storage medium |
| CN112413738B (en) * | 2020-11-27 | 2022-05-17 | 珠海格力电器股份有限公司 | Fresh air conditioning system and heat recovery method thereof |
| CN112413738A (en) * | 2020-11-27 | 2021-02-26 | 珠海格力电器股份有限公司 | Fresh air conditioning system and heat recovery method thereof |
| WO2022110898A1 (en) * | 2020-11-27 | 2022-06-02 | 珠海格力电器股份有限公司 | Fresh air conditioning system and heat recovery method thereof |
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| 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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