CN111878891A - Air conditioning system and control method thereof - Google Patents
Air conditioning system and control method thereof Download PDFInfo
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- CN111878891A CN111878891A CN202010548456.7A CN202010548456A CN111878891A CN 111878891 A CN111878891 A CN 111878891A CN 202010548456 A CN202010548456 A CN 202010548456A CN 111878891 A CN111878891 A CN 111878891A
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- 238000004378 air conditioning Methods 0.000 title claims abstract description 105
- 238000000034 method Methods 0.000 title claims abstract description 27
- 239000003507 refrigerant Substances 0.000 claims abstract description 279
- 239000007788 liquid Substances 0.000 claims abstract description 179
- 238000001179 sorption measurement Methods 0.000 claims abstract description 170
- 238000010257 thawing Methods 0.000 claims abstract description 90
- 238000010438 heat treatment Methods 0.000 claims abstract description 71
- 230000007246 mechanism Effects 0.000 claims abstract description 11
- 238000011144 upstream manufacturing Methods 0.000 claims abstract description 9
- 239000003463 adsorbent Substances 0.000 claims description 23
- 239000011248 coating agent Substances 0.000 claims description 15
- 238000000576 coating method Methods 0.000 claims description 15
- 230000008929 regeneration Effects 0.000 claims description 13
- 238000011069 regeneration method Methods 0.000 claims description 13
- 238000003795 desorption Methods 0.000 claims description 8
- 230000000274 adsorptive effect Effects 0.000 claims 2
- 239000003570 air Substances 0.000 description 45
- 238000001816 cooling Methods 0.000 description 21
- 238000004891 communication Methods 0.000 description 9
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Chemical compound O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 9
- 239000012080 ambient air Substances 0.000 description 8
- VYPSYNLAJGMNEJ-UHFFFAOYSA-N Silicium dioxide Chemical compound O=[Si]=O VYPSYNLAJGMNEJ-UHFFFAOYSA-N 0.000 description 7
- 239000012621 metal-organic framework Substances 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 5
- 230000008020 evaporation Effects 0.000 description 5
- 239000007787 solid Substances 0.000 description 5
- 230000008569 process Effects 0.000 description 4
- 229920006395 saturated elastomer Polymers 0.000 description 4
- 230000015572 biosynthetic process Effects 0.000 description 3
- 238000007791 dehumidification Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 3
- 239000000314 lubricant Substances 0.000 description 3
- 239000000741 silica gel Substances 0.000 description 3
- 229910002027 silica gel Inorganic materials 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 239000000499 gel Substances 0.000 description 2
- 238000012423 maintenance Methods 0.000 description 2
- 239000000377 silicon dioxide Substances 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 230000009471 action Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000001143 conditioned effect Effects 0.000 description 1
- 239000002826 coolant Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 238000005057 refrigeration Methods 0.000 description 1
- 230000001172 regenerating effect Effects 0.000 description 1
- 239000002594 sorbent Substances 0.000 description 1
- 238000004781 supercooling Methods 0.000 description 1
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Classifications
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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
- F24F1/0003—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station characterised by a split arrangement, wherein parts of the air-conditioning system, e.g. evaporator and condenser, are in separately located units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/42—Defrosting; Preventing freezing of outdoor units
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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
-
- 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
- F24F11/88—Electrical aspects, e.g. circuits
-
- 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
-
- 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
- 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
- F24F2110/12—Temperature of the outside air
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F2140/00—Control inputs relating to system states
- F24F2140/20—Heat-exchange fluid temperature
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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)
- Mathematical Physics (AREA)
- Fuzzy Systems (AREA)
- Thermal Sciences (AREA)
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- Life Sciences & Earth Sciences (AREA)
- Air Conditioning Control Device (AREA)
Abstract
The invention relates to an air conditioning system and a control method thereof. The air conditioning system is configured as a circuit in which a refrigerant circulates and which has a compressor, a main four-way valve, an indoor heat exchanger, and a throttle mechanism, and further includes in the circuit: a first adsorption outdoor heat exchanger and a second outdoor heat exchanger connected in parallel, the former being located upstream of the latter in the air flow direction; a high-temperature gas refrigerant bypass or a high-temperature liquid refrigerant bypass; and a first bypass four-way valve disposed in the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant bypass and configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the first outdoor adsorption heat exchanger to perform forward defrosting and desorb and regenerate the first outdoor adsorption heat exchanger when the air conditioning system operates in the heating mode. The air conditioning system can obviously reduce the defrosting frequency of the outdoor heat exchanger through the configuration, and does not need to interrupt heating when the defrosting is carried out in the forward direction.
Description
Technical Field
The invention relates to the field of air conditioners, in particular to an air conditioning system and a control method thereof.
Background
The air conditioning system having a heating mode includes, but is not limited to, a heat pump type air conditioner, a multi-split air conditioning system, and the like. When the air conditioning system operates in a heating mode, a high-temperature and high-pressure gas refrigerant discharged from a compressor generally flows into an indoor heat exchanger through two intercommunicating ports in a four-way valve (four different ports in total); in the indoor heat exchanger (acting as a condenser), the gas refrigerant is condensed into high-temperature and high-pressure liquid by transferring heat to the indoor air, and the indoor air is heated and heated; the high-temperature and high-pressure liquid refrigerant leaves the indoor heat exchanger, flows to the expansion valve and is throttled into a low-temperature and low-pressure liquid refrigerant in the expansion valve; the liquid refrigerant of low temperature and low pressure flows into the outdoor heat exchanger (serving as an evaporator) and is evaporated therein into a gas refrigerant of low temperature and low pressure by absorbing heat of ambient air; the low-temperature low-pressure gas refrigerant then flows back to the air suction end of the compressor through the other two intercommunicating ports in the four-way valve, so that a heating cycle is formed; the compressor compresses the sucked low-temperature and low-pressure refrigerant into high-temperature and high-pressure gas refrigerant and discharges the high-temperature and high-pressure gas refrigerant to start a new heating cycle. The heating operation required for an air conditioning system usually occurs in winter, and the temperature of the ambient air is often very low, for example, may be lower than 0 ℃. Therefore, the outer surface of the outdoor heat exchanger is easily frosted. If the frost layer of the outdoor heat exchanger is not removed in time, the heating performance of the air conditioning system is greatly affected, and even the air conditioning system is in failure. Air conditioning systems of the prior art have developed two different ways of reverse defrosting and forward defrosting.
The reverse defrosting generally refers to that, during defrosting, a high-temperature and high-pressure gas refrigerant discharged from a compressor is first introduced into an outdoor heat exchanger by switching the mutually communicated ports of the four-way valve, and the frost layer on the outer surface of the outdoor heat exchanger is melted by the high-temperature and high-pressure gas refrigerant. The flow direction of the refrigerant in the air conditioning system during defrosting is exactly opposite to the flow direction of the refrigerant in the air conditioning system during heating, and therefore, the defrosting is called "reverse defrosting". Due to this reverse defrosting, the air conditioning system must suspend heating, and thus the reverse defrosting affects the comfort of the user.
In order to overcome or mitigate the adverse effects of "reverse defrost," a forward defrost mode has also been developed. The "forward defrosting" means that a part of a high-temperature and high-pressure gas refrigerant or a liquid refrigerant is introduced into an outdoor heat exchanger to be defrosted through a bypass to remove a frost layer on the outdoor heat exchanger during defrosting, but the flow direction of a main refrigerant in the air conditioning system does not need to be changed, so that the air conditioning system is still operated in a heating mode through another outdoor heat exchanger without interrupting heating. For example, chinese patent application publication CN109237725A discloses such a forward defrosting mode. In the air conditioner disclosed in CN109237725A, two outdoor heat exchangers are provided, each of which is connected to one high-temperature and high-pressure gas refrigerant bypass or one high-temperature and high-pressure liquid refrigerant bypass. A defrosting electromagnetic valve is arranged on a high-temperature high-pressure gas refrigerant bypass or a high-temperature high-pressure liquid refrigerant bypass. When the forward defrosting is needed, the control system of the air conditioner opens the corresponding defrosting electromagnetic valve to introduce the high-temperature gas refrigerant or the high-temperature liquid refrigerant into the corresponding outdoor heat exchanger, so that the defrosting of the outdoor heat exchanger is realized under the condition of not interrupting the heating of the air conditioner. The air conditioner may also perform reverse defrosting when necessary. Compared with the pipe diameter of a high-pressure liquid refrigerant bypass or a high-pressure gas refrigerant bypass, especially compared with the pipe diameter of the high-pressure gas refrigerant bypass, the pipe diameter in the defrosting electromagnetic valve is much smaller, so that the electromagnetic valve pipeline necking is formed. When the defrosting solenoid valve is opened, the pipeline necking of the solenoid valve causes a larger position pressure difference between the upstream and the downstream of the defrosting solenoid valve, and further causes the problem that the refrigerant flow deviation cannot be adjusted.
Accordingly, there is a need in the art for a new solution to the above problems.
Disclosure of Invention
In order to solve the above-mentioned problems in the prior art, that is, to solve the technical problem that the forward defrosting configuration of the conventional air conditioning system causes the refrigerant flow deviation to be unable to be adjusted, the present invention provides an air conditioning system configured as a loop in which the refrigerant can circulate and flow and which has a compressor, a main four-way valve, an indoor heat exchanger, and a throttling mechanism, wherein the loop further comprises: a first adsorption outdoor heat exchanger and a second outdoor heat exchanger connected in parallel, the first adsorption outdoor heat exchanger being located upstream of the second outdoor heat exchanger in an air flow direction; a high-temperature gas refrigerant bypass or a high-temperature liquid refrigerant bypass; and a first bypass four-way valve disposed in the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant bypass and configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the first adsorption outdoor heat exchanger to perform forward defrosting and desorb and regenerate the first adsorption outdoor heat exchanger when the air conditioning system operates in a heating mode.
In a preferred embodiment of the air conditioning system, the first outdoor heat exchanger and the second outdoor heat exchanger are stacked together, or the first outdoor heat exchanger and the second outdoor heat exchanger are located at a predetermined distance.
In a preferred embodiment of the air conditioning system, the second outdoor heat exchanger is also configured as a second adsorption outdoor heat exchanger, and a second bypass four-way valve is disposed in the loop, the second bypass four-way valve and the first bypass four-way valve are disposed in parallel in the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant bypass, and the second bypass four-way valve is configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the second adsorption outdoor heat exchanger to perform the forward defrosting and desorb and regenerate the second adsorption outdoor heat exchanger when the air conditioning system operates in the heating mode.
In a preferred embodiment of the air conditioning system, each of the first adsorption outdoor heat exchanger and the second adsorption outdoor heat exchanger is connected to a corresponding first solenoid valve and a corresponding second solenoid valve, the first solenoid valves are positioned in liquid pipelines upstream of the corresponding first adsorption outdoor heat exchanger and the corresponding second adsorption outdoor heat exchanger in the loop along the flow direction of the refrigerant in the heating mode, the second solenoid valves are respectively positioned in low-temperature refrigerant bypasses of the corresponding first adsorption outdoor heat exchanger and the corresponding second adsorption outdoor heat exchanger, and the low-temperature refrigerant bypasses are respectively communicated to a suction side pipeline of the compressor from positions between the corresponding first adsorption outdoor heat exchanger and the corresponding second adsorption outdoor heat exchanger in the loop.
In a preferred embodiment of the air conditioning system, the first adsorption outdoor heat exchanger and the second adsorption outdoor heat exchanger are both composed of fin-tube heat exchangers having an adsorbent coating on the outer surface thereof.
In a preferred embodiment of the air conditioning system, the second outdoor heat exchanger is configured as a non-adsorption outdoor heat exchanger, and the second outdoor heat exchanger and the first bypass four-way valve are disposed on two parallel branches of the circuit, respectively.
In a preferred embodiment of the air conditioning system, the high-temperature gas refrigerant bypass may be communicated with an exhaust pipe in the loop, and the high-temperature liquid refrigerant bypass may be communicated with a high-pressure liquid pipe in the loop.
As can be understood by those skilled in the art, in the loop of the air conditioning system of the present invention, a first adsorption outdoor heat exchanger and a second outdoor heat exchanger connected in parallel, a high-temperature gas refrigerant bypass or a high-temperature liquid refrigerant bypass, and a first bypass four-way valve are provided. The first adsorption outdoor heat exchanger is disposed upstream of the second outdoor heat exchanger in the air flow direction. In the heating mode, the low-temperature liquid refrigerant flows into the first adsorption outdoor heat exchanger and the second adsorption outdoor heat exchanger, and is evaporated into a low-temperature gas refrigerant by absorbing heat of air flowing over the heat exchange surfaces. Meanwhile, the first outdoor heat exchanger removes moisture or water vapor in the air by the adsorption principle, so that the relative humidity of the air is greatly reduced. The dew point temperature of the air subjected to adsorption treatment is far lower than the temperature of the refrigerant in the first adsorption outdoor heat exchanger and the second outdoor heat exchanger, so that a frost layer is not formed on the outer surfaces of the first adsorption outdoor heat exchanger and the second outdoor heat exchanger for a period of time. This can significantly extend the time for the formation of frost layers on the outer surfaces of the first and second outdoor heat exchangers, thereby reducing the frequency of defrosting of the air conditioning system and improving thermal comfort of the conditioned space (e.g., room) while heating. When the adsorption capacity of the first outdoor-adsorption heat exchanger is saturated, the air conditioning system may control the first bypass four-way valve to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the first outdoor-adsorption heat exchanger to heat the first outdoor-adsorption heat exchanger, thereby desorbing and regenerating the adsorbent on the outer surface of the first outdoor-adsorption heat exchanger while removing the frost layer existing on the outer surface of the first outdoor-adsorption heat exchanger (i.e., "forward defrosting"). When the first adsorption outdoor heat exchanger performs desorption regeneration and defrosting, the air conditioning system continues heating through the second outdoor heat exchanger, and thus the heating mode is not interrupted. The first bypass four-way valve does not cause a large position pressure difference when it is opened because its inner diameter of the pipe is relatively large. In addition, the air conditioning system can also implement reverse defrosting by controlling the main four-way valve when necessary.
Preferably, the second outdoor heat exchanger is a second adsorption outdoor heat exchanger, and a second bypass four-way valve is provided in the circuit, the second bypass four-way valve being disposed in the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant bypass in parallel with the first bypass four-way valve, the second bypass four-way valve being configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the second adsorption outdoor heat exchanger to perform forward defrosting and desorb and regenerate the second adsorption outdoor heat exchanger when the air conditioning system is operating in the heating mode. This arrangement enhances the removal of water vapor from the air flowing over its surface, reducing the relative humidity of the air, and thus further reducing the frequency of defrosting.
Preferably, the adsorbent coating of the first and second adsorption outdoor heat exchangers may be formed of Metal Organic Framework (MOF) or silica gel.
The present invention also provides a control method of an air conditioning system, when any one of the above air conditioning systems operates in a heating mode, the control method comprising: measuring the outdoor ambient temperature and the outdoor relative humidity to obtain an outdoor dew point temperature; measuring the outlet temperature of each heat exchanger outside the adsorption chamber; comparing the outlet temperature to the outdoor dew point temperature; and when the difference between the outlet temperature and the outdoor dew point temperature is lower than a first preset temperature value, controlling a corresponding bypass four-way valve to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the outdoor adsorption heat exchanger to perform forward defrosting and enable the outdoor adsorption heat exchanger to perform desorption regeneration.
In a preferred technical solution of the control method of the air conditioning system, when the outdoor ambient temperature is less than or equal to 5 ℃, the interval time of the forward defrosting is a first predetermined time period, when the outdoor ambient temperature is less than or equal to 5 ℃, the interval time of the forward defrosting is a second predetermined time period, and the second predetermined time period is longer than the first predetermined time period.
In a preferable embodiment of the control method of the air conditioning system, the control method further includes: determining outlet pressures of the first and second outdoor heat exchangers; determining a corresponding refrigerant saturation temperature based on each of the outlet pressures; and controlling the lowest refrigerant saturation temperature to be higher than a second preset temperature value.
Drawings
Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:
FIG. 1 is a system schematic of a first embodiment of an air conditioning system of the present invention;
FIG. 2 is a schematic diagram showing the change in dew point temperature over time as air is dehumidified by an adsorption outdoor heat exchanger;
FIG. 3 is a system diagram of a second embodiment of the air conditioning system of the present invention;
FIG. 4 is a system diagram of a third embodiment of the air conditioning system of the present invention;
FIG. 5 is a system schematic of a fourth embodiment of the air conditioning system of the present invention;
fig. 6 is a flowchart of a control method of the air conditioning system of the present invention.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.
In order to solve the technical problem that the forward defrosting configuration of the prior air conditioning system can cause the deviation of the flow rate of the refrigerant to be incapable of being adjusted, the invention provides an air conditioning system 1, the air conditioning system 1 is configured into a loop which can enable the refrigerant to circularly flow in the loop and is provided with a compressor 11, a main four-way valve 14, an indoor heat exchanger 31 and a throttling mechanism, and the loop further comprises: a first adsorption outdoor heat exchanger 21a and a second outdoor heat exchanger 21b connected in parallel, the first adsorption outdoor heat exchanger 21a being located upstream of the second outdoor heat exchanger 21b in the air flow direction; a high-temperature gas refrigerant bypass 41a or a high-temperature liquid refrigerant bypass 41 b; and a first bypass four-way valve 42, the first bypass four-way valve 42 being disposed in the high-temperature gas refrigerant bypass 41a or the high-temperature liquid refrigerant bypass 41b, and configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass 41a or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass 41b into the first adsorption outdoor heat exchanger 21a to perform forward defrosting and desorb regeneration of the first adsorption outdoor heat exchanger 21a when the air conditioning system 1 is operating in the heating mode.
The "air conditioning system" referred to herein includes, but is not limited to, a central air conditioner having a heating mode, a split type air conditioner, a multi-split air conditioner, and the like. Reference herein to "coolant" includes, but is not limited to, R134a, R407C, R410A. References herein to a "throttle mechanism" include, but are not limited to, capillary tubes, thermostatic expansion valves, and electronic expansion valves.
As referred to herein, a "sorption outdoor heat exchanger" refers to a heat exchanger having an outer surface coated with a solid sorbent coating, including but not limited to a finned tube heat exchanger. Solid adsorbents include, but are not limited to, MOFs and silica gels.
Fig. 1 is a system schematic of a first embodiment of the air conditioning system of the present invention. As shown in fig. 1, the air conditioning system 1 forms a loop 1a in which a refrigerant (not shown) can circulate. In this embodiment, the circuit 1a mainly includes a compressor 11, a main four-way valve 14, an indoor heat exchanger 31, a throttle mechanism, a first adsorption outdoor heat exchanger 21a and a second outdoor heat exchanger 21b connected in parallel, a high-temperature gas refrigerant bypass 41a, and a first bypass four-way valve 42. In the air conditioning system of the present invention, the throttle mechanism includes an indoor throttle mechanism and an outdoor throttle mechanism, and both the indoor throttle mechanism and the outdoor throttle mechanism include, but are not limited to, an expansion valve, such as an electronic expansion valve or a thermostatic expansion valve.
As shown in fig. 1, the compressor 11 in circuit 1a may be any suitable compressor including, but not limited to, a centrifugal compressor, a scroll compressor, a screw compressor. The compressors can be variable frequency compressors or fixed frequency compressors according to requirements. The compressor 11 has a discharge end 111 and a suction end 112. The discharge end 111 of the compressor is connected to the d-port of the main four-way valve 14 by a discharge line 141, while the suction end 112 of the compressor 11 is connected to the s-port of the main four-way valve 14 by a suction line 144. In one or more embodiments, an oil separator 12 and a vent check valve 13 are provided on the vent line 141. The refrigerant is compressed to a high-temperature and high-pressure refrigerant in the compressor 11, and then discharged from the discharge end 111, and passes through the oil separator 12 to separate the compressor lubricant oil carried by the refrigerant. The separated compressor lubricant oil is returned to the suction side 112 of the compressor via an oil return line 121. In order to gasify the compressor lubricant and the refrigerant therein, a throttle capillary (not shown) is further provided on the oil return line 121. The high-temperature and high-pressure refrigerant leaving the oil separator 12 flows through the discharge check valve 13 to the main four-way valve 14. Alternatively, depending on the actual requirements, the oil separator 12 and/or the non-return valve 13 may not be provided in the exhaust line 141. In one or more embodiments, a gas-liquid separator 15 is disposed on the suction pipeline 144, and the suction end 112 of the compressor 11 is connected to a gas pipeline connection end of the gas-liquid separator 15, so as to prevent the liquid impact phenomenon caused by the liquid refrigerant sucked by the compressor 11. Alternatively, the gas-liquid separator 15 may be eliminated, depending on the actual requirements.
As shown in FIG. 1, main four-way valve 14 has four ports, an e-port and a c-port, in addition to the d-port and s-port mentioned above. The e-port of the main four-way valve 14 is connected to one end of an indoor gas line 311 through a first four-way valve gas line 142, and the other end of the indoor gas line 311 is connected to one side of the indoor heat exchanger 31. Optionally, a gas shut-off valve 33 is disposed between the first four-way valve gas line 142 and the indoor gas line 311. When the air conditioning system 1 is operating, the gas shutoff valve 33 is in a normally open state. The gas shut-off valve 33 can be closed as required, for example, when the air conditioning system 1 is not in operation for a long time or needs maintenance. As shown in fig. 1, the c-port of the main four-way valve 14 is connected to the s-port of the first bypass four-way valve 42 and the second outdoor gas line 211b of the second outdoor heat exchanger 21b, respectively, through a second four-way valve gas line 143.
As shown in fig. 1, in one or more embodiments, the indoor heat exchanger 31 includes four indoor heat exchanger units connected in parallel with each other: a first indoor heat exchanger 31a, a second indoor heat exchanger 31b, a third indoor heat exchanger 31c, and a fourth indoor heat exchanger 31 d. Alternatively, the indoor heat exchanger 31 may comprise more or fewer indoor heat exchanger units, as the actual need arises. The indoor heat exchanger 31 may take the form of a heat exchanger including, but not limited to, a fin-and-tube heat exchanger and a plate heat exchanger. As shown in fig. 1, first sides of the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31d are respectively communicated to the indoor gas piping 311. On the second side, the first indoor heat exchanger 31a is connected to the first indoor expansion valve 32a, the second indoor heat exchanger 31b is communicated to the second indoor expansion valve 32b, the third indoor heat exchanger 31c is communicated to the third indoor expansion valve 32c, and the fourth indoor heat exchanger 31d is communicated to the fourth indoor expansion valve 32 d. The first, second, third, and fourth indoor expansion valves 32a, 32b, 32c, and 32d are connected in parallel to the indoor liquid line 312. The first, second, third, and fourth indoor expansion valves 32a, 32b, 32c, and 32d may be, but are not limited to, electronic expansion valves and thermostatic expansion valves.
As shown in fig. 1, in one or more embodiments, the indoor liquid line 312 is connected to the second outdoor liquid line 232 through the liquid shut-off valve 34. The liquid shutoff valve 34 is also in a normally open state when the air conditioning system 1 is operating. The liquid shut-off valve 34 may cooperate with the gas shut-off valve 33 to facilitate maintenance of the air conditioning system 1. Optionally, a subcooler 24 may be provided in the second outdoor liquid line 232. One side of the subcooler 24 is connected to the indoor liquid line 312 and the other side thereof is connected to the suction line 144 of the continuous gas-liquid separator 15 through a gas branch 241. The subcooler 24 may utilize a small portion of the refrigerant to throttle and cool the rest of the refrigerant, and the small portion of the refrigerant cools the refrigerant in the main flow path to obtain heat and enter the gas-liquid separator 15. For example, in the cooling mode, the main flow path refrigerant from the second outdoor liquid line 232 may be branched into a small portion of refrigerant, and the small portion of refrigerant is throttled by the expansion valve 25 to cool the main flow path refrigerant, and the main flow path cooled by the small portion of refrigerant and super-cooled enters the indoor liquid line 312.
As shown in fig. 1, in one or more embodiments, the second outdoor liquid line 232 communicates with the first outdoor liquid line 231 through the high pressure accumulator 23. Alternatively, the high pressure reservoir 23 may be eliminated, as desired. As shown in fig. 1, the first outdoor liquid piping 231 is connected to the first adsorption outdoor heat exchanger 21a through the first outdoor heat exchanger liquid branch 212a, and is connected to the second outdoor heat exchanger 21b through the second outdoor heat exchanger liquid branch 212 b. A first outdoor expansion valve 22a, such as an electronic expansion valve or a thermostatic expansion valve, is disposed in the first outdoor heat exchanger liquid branch 212 a. A second outdoor expansion valve 22b, such as an electronic expansion valve or a thermostatic expansion valve, is disposed in the second outdoor heat exchanger liquid branch 212 b. The first adsorption outdoor heat exchanger 21a is connected to the e port of the first bypass four-way valve 42 through the first outdoor heat exchanger gas branch 211 a. The second outdoor heat exchanger 21b is directly connected to a second four-way valve gas line 143 by a second outdoor heat exchanger gas branch 211 b. Therefore, the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b are connected in parallel.
In one or more embodiments, the first adsorption outdoor heat exchanger 21a may be a finned tube heat exchanger coated with a solid adsorbent coating on its outer surface, while the second outdoor heat exchanger 21b is a non-adsorption outdoor heat exchanger, e.g., also a finned tube heat exchanger. Solid adsorbents include, but are not limited to, MOFs and silica gels. The first adsorption outdoor heat exchanger 21a is located upstream of the second outdoor heat exchanger 21b in the direction in which air flows, so that the ambient air first flows through the first adsorption outdoor heat exchanger 21a and then flows over the outer surface of the second outdoor heat exchanger 21 b. In one or more embodiments, the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b are stacked together, and thus may share a fan (not shown), such as an axial fan or a centrifugal fan. Alternatively, the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b are positioned to be spaced apart from each other by a predetermined distance. In this case, the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b may be each provided with a fan; and the fan of the second outdoor heat exchanger 21b may not be stopped while the forward defrosting is performed on the first adsorption outdoor heat exchanger 21a, and vice versa.
As shown in fig. 1, one end of the high temperature gas refrigerant bypass 41a is connected to the high pressure exhaust line 141, and the other end thereof is connected to the d port of the first bypass four-way valve 42. As shown in FIG. 1, the first bypass four-way valve 42 has an e-port, an s-port, and a c-port in addition to the d-port. In this embodiment, the c-port is closed and not connected to any tubing. As mentioned above, the e-port of the first bypass four-way valve 42 is connected to the first outdoor heat exchanger gas branch 211a, and the s-port of the first bypass four-way valve 42 is connected to the second four-way valve gas line 143.
The air conditioning system 1 described above can realize different functions such as cooling, heating, forward defrosting, and reverse defrosting by controlling the main four-way valve 14 and the first bypass four-way valve 42.
In the cooling mode, the main four-way valve 14 is powered off, and four ports of the main four-way valve are switched into a mode that a port d is directly communicated with a port c, and a port e is directly communicated with a port s; the first bypass four way valve 42 is de-energized so its d port is not in communication with both the e and s ports, but the e and s ports are in communication. When the air conditioning system 1 operates in the cooling mode, the compressor 11 compresses the low-temperature and low-pressure gas refrigerant sucked from the suction end 112 into a high-temperature and high-pressure gas refrigerant and discharges the gas refrigerant from the discharge end 111. The high-temperature and high-pressure gas refrigerant flows through the oil separator 12 and the check valve 13 in this order along the exhaust line 141, and then enters the main four-way valve 14. The high-temperature and high-pressure gas refrigerant entering the main four-way valve 14 from the d port exits from the c port and flows along the second four-way valve gas line 143. The high temperature and high pressure gas refrigerant from the second four-way valve gas line 143 is then divided into two portions: a first part of the high-temperature and high-pressure gas refrigerant flows into the first bypass four-way valve 42 from the s port of the first bypass four-way valve 42, leaves from the e port of the first bypass four-way valve 42, and flows into the first adsorption outdoor heat exchanger 21 a; the second portion of the high-temperature and high-pressure gas refrigerant directly flows into the second exterior heat exchanger 21 b. The high-temperature and high-pressure gas refrigerant then transfers heat to the air flowing over the outer surfaces of the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b in the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b, respectively, and is cooled to a high-temperature and high-pressure liquid refrigerant. Therefore, in the cooling mode, both the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b function as condensers, and since the refrigerant temperature in the first adsorption outdoor heat exchanger 21a is relatively high, adsorption of the adsorption coating on the outer surface of the first adsorption outdoor heat exchanger 21a does not occur. The high-temperature and high-pressure liquid refrigerant leaving the first and second adsorption outdoor heat exchangers 21a and 21b are merged together after passing through the first and second outdoor expansion valves 22a and 22b, respectively (which do not perform the throttling expansion function in the cooling mode), and flow into the high-pressure accumulator 23 along the first outdoor liquid pipe 231. After passing through the high-pressure accumulator 23, the high-temperature and high-pressure liquid refrigerant enters the subcooler 24 along the second outdoor liquid line 232. The liquid refrigerant, the supercooling degree of which is increased in the subcooler 24, then flows along the indoor liquid pipe 312 and through the liquid stop valve 34, and then is divided into four parts to flow toward the first indoor expansion valve 32a, the second indoor expansion valve 32b, the third indoor expansion valve 32c, and the fourth indoor expansion valve 32d, respectively. The high-temperature and high-pressure liquid refrigerant is throttled and expanded into a low-temperature and low-pressure liquid refrigerant by the first indoor expansion valve 32a, the second indoor expansion valve 32b, the third indoor expansion valve 32c, and the fourth indoor expansion valve 32d, and flows into the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d, respectively. In the cooling mode, the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31d all function as evaporators. Therefore, the low-temperature and low-pressure liquid refrigerant is evaporated into a low-temperature and low-pressure gas refrigerant by absorbing heat of the indoor air in the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31d, respectively, and the indoor air is cooled. The low-temperature and low-pressure gas refrigerant is then merged in the indoor gas line 311 and flows toward the e-port of the main four-way valve 14 via the gas shutoff valve 33 and the first four-way valve gas line 142. Since the e port is communicated with the s port in the cooling mode, the low-temperature and low-pressure gas refrigerant enters the suction line 144 from the s port. The low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started.
In the heating mode, the flow direction of the refrigerant in the air conditioning system 1 is opposite to the flow direction in the refrigeration cycle. In the heating mode, the main four-way valve 14 is in a power-on state, the d port thereof is directly communicated with the e port, and the c port thereof is directly communicated with the s port; the first bypass four way valve 42 is de-energized so its d port is not in communication with both the e and s ports, but the e and s ports are in communication. When the heating cycle starts, the compressor 11 also compresses the low-temperature and low-pressure gas refrigerant sucked from the suction end 112 into a high-temperature and high-pressure gas refrigerant, and discharges the gas refrigerant from the discharge end 111. The high-temperature and high-pressure gas refrigerant flows through the oil separator 12 and the check valve 13 in this order along the exhaust line 141, and then enters the main four-way valve 14 from the d port. The high-temperature and high-pressure gas refrigerant is separated from the e port of the main four-way valve 14 and flows through the first four-way valve gas line 142, the gas shutoff valve 33, and the indoor gas line 311 in this order. The high-temperature and high-pressure gas refrigerant is divided into four portions, and flows into the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d, respectively. In the heating mode, the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d all function as condensers. The high-temperature and high-pressure gas refrigerant is cooled to a high-temperature and high-pressure liquid refrigerant by transferring heat to the indoor air in the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31d, and the indoor air is heated (which usually occurs when the outdoor air temperature is relatively low, for example, in winter). The high-temperature and high-pressure liquid refrigerant then flows through the first, second, third, and fourth indoor expansion valves 32a, 32b, 32c, and 32d (which do not perform a throttling expansion function in the heating mode) and joins in the indoor liquid line 312. The high-temperature and high-pressure liquid refrigerant then flows through the liquid stop valve 34, the subcooler 24, the second outdoor liquid line 232, the high-pressure accumulator 23, and the first outdoor liquid line 231 in this order. Then, the high-temperature and high-pressure liquid refrigerant is divided into two portions, which flow into the first outdoor heat exchanger liquid branch 212a and the second outdoor heat exchanger liquid branch 212b, respectively, and is throttled and expanded into a low-temperature and low-pressure liquid refrigerant by the first outdoor expansion valve 22a and the second outdoor expansion valve 22 b. The low-temperature and low-pressure liquid refrigerant flows into the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b, respectively.
In the heating mode, both the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b function as evaporators. Therefore, the low-temperature and low-pressure liquid refrigerant absorbs heat of the air flowing through the outer surfaces of the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b, and is evaporated into a low-temperature and low-pressure gas refrigerant. Meanwhile, when the ambient air passes through the outer surface of the first outdoor heat exchanger 21a, water vapor or moisture therein is removed by the adsorption action of the solid adsorbent, and the latent heat of adsorption generated is also transferred to the refrigerant in the first outdoor heat exchanger 21 a. The relative humidity of the air passing through the outer surface of the first adsorption outdoor heat exchanger 21a is thus greatly reduced so that the temperature of the refrigerant inside the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b is much higher than the dew point temperature of the dehumidified air. Fig. 2 is a schematic view showing a change in dew point temperature with time when air is dehumidified by an outdoor heat exchanger for adsorption. The adsorption capacity of the adsorbent coating of the first adsorption outdoor heat exchanger 21a gradually decreases over time until it reaches a saturated state (i.e. no more water vapour can be adsorbed). As shown in FIG. 2, for example, the ambient air temperature is 2 ℃, the relative humidity is 80%, and the flow rate is 162m3In the working condition of/h, when the dew point temperature of the ambient air before dehumidification is-1 ℃ and the evaporation temperature in the first adsorption outdoor heat exchanger 21a is-5 ℃, the heat exchange is carried out outside the first adsorption outdoor heat exchanger in about 20 minutesThe dew point temperature of the air dehumidified by the device 21a is reduced to a temperature lower than-5 c, for example, the dew point temperature of the dehumidified air may reach below-20 c within the first 2 minutes. This means that no frost is produced on the outer surface of the first adsorption outdoor heat exchanger 21a within about 20 minutes. Alternatively, when the ambient air temperature becomes-7 ℃ and the relative humidity is 80%, the non-frosting on the outer surface of the first adsorption outdoor heat exchanger 21a may last for about 42 minutes without changing other operating conditions. Alternatively, when the ambient air temperature becomes 5 ℃ and the relative humidity is 80%, the non-frosting on the outer surface of the first adsorption outdoor heat exchanger 21a may last for about 17 minutes without changing other operating conditions. Therefore, the first adsorption outdoor heat exchanger 21a can significantly extend the time for the formation of the frost layer on the outer surface of the first adsorption outdoor heat exchanger 21a, thereby reducing the frequency of defrosting of the air conditioning system 1 during heating. Since the second outdoor heat exchanger exchanges heat with the treated (air dehumidified) air, the air contains little water vapor, which results in a decrease in the dew point of the air, and therefore the second outdoor heat exchanger will not frost for a long time.
In the heating mode, the low-temperature and low-pressure gas refrigerant leaving the second outdoor heat exchanger 21b directly flows into the second four-way valve gas pipeline 143 through the second outdoor heat exchanger gas branch 211 b; the low-temperature and low-pressure gas refrigerant leaving the first adsorption outdoor heat exchanger 21a first passes through the first outdoor heat exchanger gas branch 211a and the e-port and s-port of the first bypass four-way valve 42 in this order, and then flows into the second four-way valve gas line 143 to join the low-temperature and low-pressure gas refrigerant from the second outdoor heat exchanger 21 b. The merged gas refrigerant flows in from the c-port of the main four-way valve 14, and then exits from the s-port of the main four-way valve 14 to enter the suction line 144. Finally, the low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started.
When the adsorbent coating of the first outdoor-adsorption heat exchanger 21a is saturated, the adsorbent coating loses its dehumidification ability, and thus the air conditioning system 1 can perform the forward defrosting to regenerate the adsorbent coating, thereby recovering its adsorption dehumidification ability. In the forward defrosting mode, the four ports of the main four-way valve 14 are communicated and configured in the same heating mode, namely the port d is directly communicated with the port e, and the port c is directly communicated with the port s; unlike in the heating mode, the first bypass four-way valve 42 needs to be energized, and therefore its d port communicates with the e port, but the e port does not communicate with the s port. When the forward defrosting mode is started, the high-temperature and high-pressure gas refrigerant from the compressor 11 is discharged from the discharge end 111 to the discharge line 141. The high-temperature and high-pressure gas refrigerant sequentially passing through the oil separator 12 and the check valve 13 is branched into a small portion on the exhaust line 141 to the high-temperature gas refrigerant bypass 41a to perform a forward defrosting function, and the remaining large portion of the high-temperature and high-pressure gas refrigerant enters the main four-way valve 14 from the d port to continue the heating function. In other words, when the air conditioning system 1 performs the forward defrosting, the heating is not interrupted, and thus the heating comfort of the user can be improved.
As shown in fig. 1, in the forward defrosting mode, the high-temperature and high-pressure gas refrigerant in the high-temperature gas refrigerant bypass 41a flows into the first bypass four-way valve 42 through the d port, and flows into the first adsorption outdoor heat exchanger 21a through the first outdoor heat exchanger gas branch 211a after leaving from the e port thereof. Since the temperature of the gas refrigerant is much higher than the surface temperature of the first adsorption outdoor heat exchanger 21a, the adsorbent coating on the first adsorption outdoor heat exchanger 21a performs a thermal process of heating and regeneration, that is, the adsorbent desorbs the water vapor adsorbed by the gas refrigerant in the first adsorption outdoor heat exchanger 21a by means of the heat of the gas refrigerant, thereby recovering the adsorption capacity. In this case, the first adsorption outdoor heat exchanger 21a functions as a condenser, and the gas refrigerant therein is condensed into a liquid refrigerant and then flows along the first outdoor heat exchanger liquid branch 212a toward the second outdoor heat exchanger liquid branch 212b via the first outdoor expansion valve 22 a.
In the forward defrosting mode, the high-temperature and high-pressure gas refrigerant that has entered the main four-way valve 14 still exits from the e-port of the main four-way valve 14, and flows through the first four-way valve gas line 142, the gas shutoff valve 33, and the indoor gas line 311 in this order. The high-temperature and high-pressure gas refrigerant is divided into four portions, and flows into the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d, respectively. The first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d still function as condensers in the heating mode. The high-temperature and high-pressure gas refrigerant is cooled to a high-temperature and high-pressure liquid refrigerant by transferring heat to the indoor air in the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31d, and the indoor air is heated. Therefore, when the first adsorption outdoor heat exchanger 21a is defrosted in the forward direction, the air conditioning system 1 continues to provide the heating function. The high-temperature and high-pressure liquid refrigerant then flows through the first indoor expansion valve 32a, the second indoor expansion valve 32b, the third indoor expansion valve 32c, and the fourth indoor expansion valve 32d (which do not perform the throttle expansion function) and joins in the indoor liquid pipe 312. The high-temperature and high-pressure liquid refrigerant then flows through the liquid stop valve 34, the subcooler 24, the second outdoor liquid line 232, the high-pressure accumulator 23, and the first outdoor liquid line 231 in this order.
Then, the high-temperature and high-pressure liquid refrigerant from the first outdoor liquid line 231 flows into the second outdoor heat exchanger liquid branch 212b to be merged with the high-temperature and high-pressure liquid refrigerant from the first outdoor heat exchanger liquid branch 212a, and is throttle-expanded into a low-temperature and low-pressure liquid refrigerant by the second outdoor expansion valve 22 b. The liquid refrigerant of low temperature and low pressure flows into the second exterior heat exchanger 21b and is evaporated therein into a gas refrigerant of low temperature and low pressure, and thus the second exterior heat exchanger 21b functions as an evaporator in this case. The low-temperature and low-pressure gas refrigerant leaving the second outdoor heat exchanger 21b passes through the second outdoor heat exchanger gas branch 211b and the second four-way valve gas line 143 in this order, flows into the main four-way valve 14 from the c-port, and then exits from the s-port of the main four-way valve 14 and enters the suction line 144. Finally, the low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started.
In the case where the frost formation on the outer surfaces of the first and second outdoor heat exchangers 21a and 21b is severe, the air conditioning system 1 may also perform regular or irregular reverse defrosting. In the reverse defrosting mode, the flow direction of the refrigerant in the air conditioning system 1 is similar to that in the cooling mode. Thus, during reverse defrost, the main four-way valve 14 is de-energized and its four ports are switched so that the d port is in direct communication with the c port and the e port is in direct communication with the s port; the first bypass four way valve 42 is de-energized and its d port is not in communication with both the e and s ports, but the e and s ports are in communication. The high-temperature and high-pressure gas refrigerant discharged from the compressor 11 passes through the oil separator 12, the check valve 13, and the main four-way valve 14 in this order, and then is divided into two portions, and flows into the first adsorption outdoor heat exchanger 21a (via the first bypass four-way valve 42) and the second outdoor heat exchanger 21b, respectively, so that the frost layers on the outer surfaces of the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b are melted by the high-temperature gas refrigerant. Therefore, in this case, the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b function as condensers. The high-temperature and high-pressure liquid refrigerant leaving the first adsorption outdoor heat exchanger 21a and the second outdoor heat exchanger 21b is subjected to throttle expansion by the first indoor expansion valve 32a, the second indoor expansion valve 32b, the third indoor expansion valve 32c, and the fourth indoor expansion valve 32d, and is then changed into a low-temperature and low-pressure liquid refrigerant. The low-temperature and low-pressure liquid refrigerant is evaporated into a low-temperature and low-pressure gas refrigerant by absorbing heat of the indoor air in the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d, respectively. The low-temperature and low-pressure gas refrigerant then flows through the main four-way valve 14 to the suction line 144, and is finally sucked by the compressor 11 to start a new cycle. Therefore, in the reverse defrosting mode, the indoor air is cooled, not heated, by the first, second, third, and fourth indoor heat exchangers 31a, 31b, 31c, and 31 d. In other words, when the reverse defrosting is performed, the heating function of the air conditioning system is interrupted, which may affect the heating comfort of the user to some extent.
By configuring the first adsorption outdoor heat exchanger 21a, the high-temperature gas refrigerant bypass 41a, and the first bypass four-way valve 42 in the air conditioning system 1, the air conditioning system 1 of the present invention can not only achieve the function of forward defrosting, thereby significantly extending the frosting time of the outer surface of the outdoor heat exchanger and reducing the defrosting frequency, but also improve the heating comfort of the air conditioning system 1. In addition, by providing the first bypass four-way valve 42 in the high-temperature gas refrigerant bypass 41a, it is possible to avoid a problem of a large positional pressure difference generated when the conventional solenoid valve is opened.
Fig. 3 is a system schematic of a second embodiment of the air conditioning system of the present invention. In one or more embodiments, a high temperature liquid refrigerant bypass 41b is provided in the circuit 1b of the air conditioning system 1. As shown in fig. 3, in one or more embodiments, one end of the high temperature liquid refrigerant bypass 41b is connected to the second outdoor liquid line 232 communicating with the high pressure accumulator 23, and the other end of the high temperature liquid refrigerant bypass 41b is connected to the d port of the first bypass four-way valve 42. The high-temperature liquid refrigerant bypass 41b and the first bypass four-way valve 42 allow the first outdoor adsorption heat exchanger 21a to be subjected to forward defrosting and desorption regeneration. When the forward defrosting is implemented, the communication configuration of the four ports of the main four-way valve 14 of the air-conditioning system 1 is the same as the heating mode, namely the port d is directly communicated with the port e, and the port c is directly communicated with the port s; the first bypass four-way valve 42 is energized so that its d port communicates with the e port, but the e port does not communicate with the s port. When the forward defrosting mode is started, the high-temperature and high-pressure gas refrigerant from the compressor 11 is discharged from the discharge end 111 to the discharge line 141. The high-temperature and high-pressure gas refrigerant passing through the oil separator 12 and the check valve 13 in this order enters the main four-way valve 14 from the d-port. The high-temperature and high-pressure gas refrigerant leaving from the e port of the main four-way valve 14 then enters the first indoor heat exchanger 31a, the second indoor heat exchanger 31b, the third indoor heat exchanger 31c, and the fourth indoor heat exchanger 31d, respectively, and is cooled into a high-temperature and high-pressure liquid refrigerant by transferring heat to the indoor air, and the indoor air is heated at the same time, so that the air conditioning system 1 can continue to perform a heating function. The high-temperature and high-pressure liquid refrigerant then flows along the indoor liquid line 312 and the second outdoor liquid line 232. To perform the forward defrosting, a small portion of the high-temperature and high-pressure liquid refrigerant enters the high-temperature liquid refrigerant bypass 41b before entering the high-pressure accumulator 23 and flows into the first outdoor adsorption heat exchanger 21a via the d-port and the e-port of the first bypass four-way valve 42, so that the adsorbent coating of the first outdoor adsorption heat exchanger 21a is desorbed and regenerated while also removing the frost layer on the outer surface of the first outdoor adsorption heat exchanger 21 a. The remaining most of the high-temperature and high-pressure liquid refrigerant enters the high-pressure accumulator 23, then flows to the second liquid branch 212b of the outdoor heat exchanger through the first outdoor liquid line 231, and is merged with the refrigerant from the first liquid branch 212a of the outdoor heat exchanger. After the refrigerant is throttled and expanded by the second outdoor expansion valve 22b, the low-temperature and low-pressure liquid refrigerant enters the second outdoor heat exchanger 21b to complete the evaporation process, and the generated low-temperature and low-pressure gas refrigerant directly flows into the second four-way valve gas pipeline 143 through the second outdoor heat exchanger gas branch 211 b. The gas refrigerant then flows in from the c-port of the main four-way valve 14 and then exits from the s-port of the main four-way valve 14 into the suction line 144. Finally, the low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started. The portions not mentioned in this embodiment may be the same as those in the above-described embodiment.
Fig. 4 is a system schematic of a third embodiment of the air conditioning system of the present invention. In this embodiment, in the loop 1c of the air conditioning system 1, in addition to the first adsorption outdoor heat exchanger 21a, the second outdoor heat exchanger is a second adsorption outdoor heat exchanger 21 b', for example, a finned tube heat exchanger provided with an adsorbent coating on its outer surface, wherein the adsorbent includes, but is not limited to, MOF and silica gel. As shown in fig. 4, the first adsorption outdoor heat exchanger 21a is connected to the high-temperature gas refrigerant bypass 41a by a first bypass four-way valve 42, and the second adsorption outdoor heat exchanger 21 b' is connected to the high-temperature gas refrigerant bypass 41a by a second bypass four-way valve 43. The second bypass four-way valve 43 also has four ports: a d-port, an e-port, an s-port, and a c-port, wherein the c-port is closed, the d-port is connected to the high temperature gas refrigerant bypass 41a, the e-port is connected to the second outdoor heat exchanger gas branch 211b, and the s-port is connected to the second four-way valve gas line 143. As shown in fig. 4, the first adsorption outdoor heat exchanger 21a is also connected to the corresponding first and second electromagnetic valves 26a and 27 a. In one or more embodiments, as shown in fig. 4, the first solenoid valve 26a is positioned on the first outdoor heat exchanger liquid branch 212a, and the second solenoid valve 27a is positioned on the first low temperature liquid refrigerant bypass 44a extending from a location on the first outdoor heat exchanger liquid branch 212a between the first adsorption outdoor heat exchanger 21a and the first solenoid valve 26a to the suction line 144. Similarly, the second adsorption outdoor heat exchanger 21 b' is also connected to the corresponding first and second electromagnetic valves 26b and 27 b. In one or more embodiments, as shown in fig. 4, the first solenoid valve 26b is positioned on the second outdoor heat exchanger liquid branch 212b, and the second solenoid valve 27b is positioned on the second low temperature liquid refrigerant bypass 44b extending from the second outdoor heat exchanger liquid branch 212b between the second adsorption outdoor heat exchanger 21 b' and the first solenoid valve 26b to the suction line 144.
The air conditioning system 1 can realize different functions such as cooling, heating, forward defrosting, reverse defrosting, and the like by controlling the combination of the main four-way valve 14, the first bypass four-way valve 42, the second bypass four-way valve 43, the first solenoid valves 26a, 26b, and the second solenoid valves 27a, 27b in the circuit 1 c. In the cooling, heating, and reverse defrost modes, the first bypass four-way valve 42 and the second bypass four-way valve 43 are both in the de-energized state. The main four-way valve 14 is in a power-off state during cooling and reverse defrosting, and is in a power-on state during heating. In the cooling, heating, and reverse defrost modes, the first solenoid valves 26a, 26b are both in an open state to allow the refrigerant to flow therethrough, and the second solenoid valves 27a, 27b are both in a closed state. When the air conditioning system 1 performs cooling, heating, and reverse defrosting, the flow direction of the refrigerant in the circuit 1c is substantially the same as the flow direction of the refrigerant in the cooling mode, the heating mode, and the reverse defrosting mode in the above embodiment, respectively.
In order that the air conditioning system 1 does not interrupt heating during forward defrosting, the first adsorption outdoor heat exchanger 21a and the second adsorption outdoor heat exchanger 21 b' are alternately subjected to forward defrosting and desorption regeneration.
When the forward defrosting is performed on the first adsorption outdoor heat exchanger 21a, the second adsorption outdoor heat exchanger 21 b' continues to participate in the normal heating cycle. Therefore, the first bypass four-way valve 42 is energized, and the d port communicates with the e port to introduce the high-temperature and high-pressure gas refrigerant from the high-temperature gas refrigerant bypass 41a into the first adsorption outdoor heat exchanger 21 a; the first solenoid valve 26a of the first outdoor heat exchanger liquid branch 212a is closed, and the second solenoid valve 27a is opened to introduce the refrigerant leaving the first adsorption outdoor heat exchanger 21a into the suction line 144 through the first low temperature liquid refrigerant bypass 44a, and join the refrigerant in the suction line 144 to flow into the gas-liquid separator 15. When the second adsorption outdoor heat exchanger 21 b' participates in the heating cycle, the second bypass four-way valve 43 is powered off, and the d port is not communicated with the e port and the s port, but the e port is communicated with the s port; the first solenoid valve 26b on the second outdoor heat exchanger liquid branch 212b is opened and the second solenoid valve 27b on the second low temperature liquid refrigerant bypass 44b is closed. Therefore, the high-temperature and high-pressure liquid refrigerant from the first outdoor liquid line 231 flows to the second outdoor heat exchanger liquid branch 212b, throttled and expanded by the second outdoor expansion valve 22b, then flows through the first solenoid valve 26b, and then flows into the second adsorption outdoor heat exchanger 21 b'. The refrigerant completes the evaporation process in the second adsorption outdoor heat exchanger 21b ', then exits the second adsorption outdoor heat exchanger 21 b', and flows to the second four-way valve gas line 143 via the s-port and e-port of the second bypass four-way valve 43. The gas refrigerant then flows in from the c-port of the main four-way valve 14 and then exits from the s-port of the main four-way valve 14 into the suction line 144. Finally, the low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started.
When the second adsorption outdoor heat exchanger 21 b' is subjected to forward defrosting, the first adsorption outdoor heat exchanger 21a continues to participate in the normal heating cycle. Therefore, the second bypass four-way valve 43 is energized, and its d port is communicated with the e port to introduce the high-temperature and high-pressure gas refrigerant from the high-temperature gas refrigerant bypass 41a into the second adsorption outdoor heat exchanger 21 b'; the first solenoid valve 26b of the second exterior heat exchanger liquid branch 212b is closed and the second solenoid valve 27b is opened to introduce the refrigerant leaving the second adsorption exterior heat exchanger 21 b' to the suction line 144 through the second low temperature liquid refrigerant bypass 44b and to flow into the gas-liquid separator 15 after being merged with the refrigerant on the suction line 144. In the case where the first adsorption outdoor heat exchanger 21a participates in the heating cycle, the first bypass four-way valve 42 is de-energized, and the d port thereof is not communicated with the e port and the s port, but the e port thereof is communicated with the s port; the first solenoid valve 26a on the first outdoor heat exchanger liquid branch 212a is open and the second solenoid valve 27a on the first low temperature liquid refrigerant bypass 44a is closed. Therefore, the high-temperature and high-pressure liquid refrigerant from the first outdoor liquid line 231 flows to the first outdoor heat exchanger liquid branch 212a, throttled and expanded by the first outdoor expansion valve 22a, then flows through the first solenoid valve 26a, and then flows into the first adsorption outdoor heat exchanger 21 a. The refrigerant completes the evaporation process in the first outdoor adsorption heat exchanger 21a, then exits the first outdoor adsorption heat exchanger 21a and flows to the second four-way valve gas line 143 via the s-port and e-port of the first bypass four-way valve 42. The gas refrigerant then flows in from the c-port of the main four-way valve 14 and then exits from the s-port of the main four-way valve 14 into the suction line 144. Finally, the low-temperature low-pressure gas refrigerant is sucked into the compressor 11 through the suction port 112 after passing through the gas-liquid separator 15, and a new cycle can be started.
In order to defrost in the forward direction, the solenoid valve is arranged on the low-pressure liquid pipeline to switch the flow direction of the refrigerant, so that a large position pressure difference cannot be generated, because the pipe diameter of the liquid pipeline is relatively small and the pressure is not high.
Fig. 5 is a system schematic of a fourth embodiment of the air conditioning system of the present invention. In this embodiment, similar to the embodiment shown in fig. 4, in the loop 1d of the air conditioning system 1, in addition to the first adsorption outdoor heat exchanger 21a, the second outdoor heat exchanger is a second adsorption outdoor heat exchanger 21 b', for example, a finned tube heat exchanger provided with an adsorbent coating on the outer surface, wherein the adsorbent includes, but is not limited to, MOF and silica gel. The embodiment shown in fig. 5 is different from the embodiment shown in fig. 4 in that a high-temperature liquid refrigerant bypass 41b is provided in the circuit 1d instead of the high-temperature gas refrigerant bypass 41a provided in the circuit 1 c. In one or more embodiments, one end of the high temperature liquid refrigerant bypass 41b is connected to the second outdoor liquid line 232, and the other end of the high temperature liquid refrigerant bypass 41b is connected to a d-port of the first bypass four-way valve 42 and a d-port of the second bypass four-way valve 43, respectively. Similar to the circuit 1c shown in fig. 4, the air conditioning system 1 can respectively realize different functions of cooling, heating, forward defrosting, reverse defrosting, and the like by the combined control of the main four-way valve 14, the first bypass four-way valve 42, the second bypass four-way valve 43, the first solenoid valves 26a, 26b, and the second solenoid valves 27a, 27b on the circuit 1 d. In the cooling, heating, and reverse defrost modes, the first bypass four-way valve 42 and the second bypass four-way valve 43 are both in the de-energized state. The main four-way valve 14 is in a power-off state in the cooling and reverse defrosting mode and in a power-on state in the heating mode. In the cooling, heating, and reverse defrost modes, the first solenoid valves 26a, 26b are both in an open state to allow the refrigerant to flow therethrough, and the second solenoid valves 27a, 27b are both in a closed state. When the air conditioning system 1 performs cooling, heating, and reverse defrosting, the flow direction of the refrigerant in the circuit 1d is substantially the same as the flow direction of the refrigerant in the cooling mode, the heating mode, and the reverse defrosting mode in the above embodiment, respectively. During forward defrosting, the air conditioning system 1 does not interrupt heating, and performs alternate forward defrosting and desorption regeneration also on the first adsorption outdoor heat exchanger 21a and the second adsorption outdoor heat exchanger 21 b'. When the forward defrosting is performed on the first adsorption outdoor heat exchanger 21a, the second adsorption outdoor heat exchanger 21 b' continues to participate in the normal heating cycle. Therefore, the first bypass four-way valve 42 is energized to introduce the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass 41b into the first outdoor adsorption heat exchanger 21a via the first bypass four-way valve 42, and the second bypass four-way valve 43 is de-energized. Meanwhile, the first solenoid valve 26a on the first outdoor heat exchanger liquid branch 212a is closed, and the second solenoid valve 27a on the first low-temperature liquid refrigerant bypass 44a is opened; conversely, the first solenoid valve 26b on the second outdoor heat exchanger liquid branch 212b is open, and the second solenoid valve 27b on the second low temperature liquid refrigerant bypass 44b is closed. When the second adsorption outdoor heat exchanger 21 b' is subjected to forward defrosting, the first adsorption outdoor heat exchanger 21a continues to participate in the normal heating cycle. Accordingly, the first bypass four-way valve 42 is de-energized, and the second bypass four-way valve 43 is energized to introduce the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass 41b into the second adsorption outdoor heat exchanger 21 b' via the second bypass four-way valve 43. Meanwhile, the first solenoid valve 26b on the second outdoor heat exchanger liquid branch 212b is closed, and the second solenoid valve 27a on the second low-temperature liquid refrigerant bypass 44b is opened; conversely, the first solenoid valve 26a on the first outdoor heat exchanger liquid branch 212a is open, and the second solenoid valve 27a on the first low temperature liquid refrigerant bypass 44a is closed.
Fig. 6 is a flowchart of a control method of the air conditioning system of the present invention. As shown in fig. 6, in order to control the forward defrosting of the air conditioning system 1 and the desorption regeneration of the adsorption outdoor heat exchanger described above, the control method of the air conditioning system 1 of the present invention includes steps S1, S2, S3, and S4. Unless explicitly stated to the contrary, the steps do not require a particular order of execution. In step S1, the outdoor global temperature Tao and the outdoor relative humidity Rho are measured to obtain the outdoor dew point temperature Tdewo. In step S2, the outlet temperature T of each adsorption outdoor heat exchanger is measured. In step S3, the outlet temperature T of the adsorption outdoor heat exchanger is compared with the outdoor dew point temperature Tdewo. When T-Tdewo is less than the first preset temperature value, the adsorption of the adsorbent coating of the adsorption outdoor heat exchanger reaches a saturated state, and the adsorption can not be continued to adsorb the external water vapor, so that the desorption regeneration of the heat exchanger outside the adsorption chamber is needed, and meanwhile, the frost layer on the outer surface of the heat exchanger outside the adsorption chamber is removed. The first predetermined temperature value may be, for example, 2 ℃ or other suitable temperature value. Therefore, in step S4, the control method controls and energizes the bypass four-way valve corresponding to the adsorption outdoor heat exchanger, for example, the first bypass four-way valve 42 or the second bypass four-way valve 43, so that the high-temperature gas refrigerant or the high-temperature liquid refrigerant bypassing the high-temperature gas refrigerant is introduced into the adsorption outdoor heat exchanger to perform the forward defrosting, and the adsorbent on the outer surface of the adsorption outdoor heat exchanger is released the water vapor adsorbed by the adsorbent by the high-temperature refrigerant to realize the regeneration.
In one or more embodiments, the control method of the air conditioning system of the present invention further includes: determining outlet pressures of the first and second outdoor heat exchangers 21a and 21 b; determining a corresponding refrigerant saturation temperature based on each outlet pressure; and controlling the lowest refrigerant saturation temperature to be higher than a second preset temperature value. The second predetermined temperature value may be, for example, 0.5 ℃ or other suitable value. During forward defrosting, the adsorbent on the adsorption outdoor heat exchanger is desorbed, and a large amount of water vapor with relatively high temperature is released. Therefore, the saturation temperature corresponding to the outlet pressure of each outdoor heat exchanger is controlled to be higher than the second preset temperature value, for example, 0.5 ℃, so that the outdoor heat exchanger can be ensured not to frost in a certain period of time.
In one or more embodiments, the control method of the air conditioning system also controls the defrosting frequency of the forward defrosting so as to avoid influencing the heating performance of the air conditioning system as much as possible. When the outdoor environment temperature Tao is less than or equal to 5 ℃ and less than or equal to 5 ℃, the control method controls the interval time of the forward defrosting to be a first preset time period, such as 30 minutes or other suitable time periods. When the outdoor environment temperature Tao < -5 ℃, the control method controls the interval time of the forward defrosting to be a second preset time period, and the second preset time period is longer than the first preset time period, and the second preset time period can be 50 minutes or other suitable time periods, for example. This is because when the outdoor ambient temperature Tao is less than-5 ℃, the dew point temperature is likely to be lower than the refrigerant evaporation temperature in the outdoor heat exchanger, and therefore, the time for frosting on the outdoor heat exchanger is longer than that when the outdoor ambient temperature Tao is less than-5 ℃ and less than 5 ℃. In addition, the control method of the air conditioning system also controls the air conditioning system to perform reverse defrosting when necessary. The specific control method of reverse defrosting can be the same as that in the prior art.
So far, the technical solutions of the present invention have been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (10)
1. An air conditioning system, characterized in that the air conditioning system is configured as a circuit in which a refrigerant circulates and which has a compressor, a main four-way valve, an indoor heat exchanger, and a throttle mechanism, and in that the circuit further comprises:
a first adsorption outdoor heat exchanger and a second outdoor heat exchanger connected in parallel, the first adsorption outdoor heat exchanger being located upstream of the second outdoor heat exchanger in an air flow direction;
a high-temperature gas refrigerant bypass or a high-temperature liquid refrigerant bypass; and
a first bypass four-way valve disposed in the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant bypass and configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the first outdoor adsorption heat exchanger to perform forward defrosting and desorb regeneration of the first outdoor adsorption heat exchanger when the air conditioning system is operating in a heating mode.
2. The air conditioning system of claim 1, wherein the first adsorptive outdoor heat exchanger is stacked with the second outdoor heat exchanger or the first adsorptive outdoor heat exchanger is positioned a predetermined distance from the second outdoor heat exchanger.
3. The air conditioning system as claimed in claim 1 or 2, wherein the second outdoor heat exchanger is also configured as a second adsorption outdoor heat exchanger, and a second bypass four-way valve is provided in the circuit, the second bypass four-way valve being disposed in parallel with the first bypass four-way valve in the high-temperature gas refrigerant bypass or high-temperature liquid refrigerant bypass, the second bypass four-way valve being configured to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the second adsorption outdoor heat exchanger to perform the forward defrosting and desorb regeneration of the second adsorption outdoor heat exchanger when the air conditioning system is operating in the heating mode.
4. The air conditioning system of claim 3, wherein each of the first and second adsorption outdoor heat exchangers is connected to corresponding first and second solenoid valves, the first solenoid valves positioned in the circuit in a direction of flow of the refrigerant both in liquid lines upstream of the corresponding first and second adsorption outdoor heat exchangers in the heating mode, and the second solenoid valves respectively positioned in low temperature refrigerant bypasses of the corresponding first and second adsorption outdoor heat exchangers, the low temperature refrigerant bypasses communicating in the circuit to suction side lines of the compressor from locations between the corresponding first and second adsorption outdoor heat exchangers and the corresponding first solenoid valves, respectively.
5. The air conditioning system of claim 3, wherein the first and second adsorption outdoor heat exchangers are each comprised of finned tube heat exchangers having an adsorbent coating on an outer surface thereof.
6. The air conditioning system as claimed in claim 1 or 2, wherein the second outdoor heat exchanger is configured as a non-adsorption outdoor heat exchanger, and the second outdoor heat exchanger is arranged on two parallel branches of the circuit with the first bypass four-way valve, respectively.
7. The air conditioning system as claimed in claim 1 or 2, wherein the high temperature gas refrigerant bypass is connected to a discharge line in the circuit, and the high temperature liquid refrigerant bypass is connected to a high pressure liquid line in the circuit.
8. A control method of an air conditioning system, characterized in that, when the air conditioning system according to any one of claims 1 to 7 is operated in the heating mode, the control method comprises:
measuring the outdoor ambient temperature and the outdoor relative humidity to obtain an outdoor dew point temperature;
measuring the outlet temperature of each heat exchanger outside the adsorption chamber;
comparing the outlet temperature to the outdoor dew point temperature;
and when the difference between the outlet temperature and the outdoor dew point temperature is lower than a first preset temperature value, controlling a corresponding bypass four-way valve to introduce the high-temperature gas refrigerant from the high-temperature gas refrigerant bypass or the high-temperature liquid refrigerant from the high-temperature liquid refrigerant bypass into the outdoor adsorption heat exchanger to perform forward defrosting and enable the outdoor adsorption heat exchanger to perform desorption regeneration.
9. The control method of an air conditioning system as recited in claim 8, wherein the interval time of the forward defrosting is a first predetermined period of time when-5 ℃ ≦ the outdoor ambient temperature ≦ 5 ℃, the interval time of the forward defrosting is a second predetermined period of time when the outdoor ambient temperature < -5 ℃, and the second predetermined period of time is longer than the first predetermined period of time.
10. The control method of an air conditioning system according to claim 8 or 9, characterized by further comprising:
determining outlet pressures of the first and second outdoor heat exchangers;
determining a corresponding refrigerant saturation temperature based on each of the outlet pressures; and is
And controlling the lowest saturation temperature of the refrigerant to be higher than a second preset temperature value.
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Application publication date: 20201103 |