WO2020113938A1 - 空调系统、空调控制方法和装置、计算机可读存储介质 - Google Patents

空调系统、空调控制方法和装置、计算机可读存储介质 Download PDF

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Publication number
WO2020113938A1
WO2020113938A1 PCT/CN2019/091706 CN2019091706W WO2020113938A1 WO 2020113938 A1 WO2020113938 A1 WO 2020113938A1 CN 2019091706 W CN2019091706 W CN 2019091706W WO 2020113938 A1 WO2020113938 A1 WO 2020113938A1
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WIPO (PCT)
Prior art keywords
heat exchanger
air
compressor
conditioning system
heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2019/091706
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English (en)
French (fr)
Inventor
刘华
孔环灵
尤文超
杜辉
杨智峰
陈博强
杨瑞
邓晶
林国游
邵元浩
石祥
刘小康
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Publication of WO2020113938A1 publication Critical patent/WO2020113938A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles
    • F25B47/022—Defrosting cycles hot gas defrosting
    • 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
    • F25B2347/00—Details for preventing or removing deposits or corrosion
    • F25B2347/02—Details of defrosting cycles
    • 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
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/24—Thermal storage element
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the present disclosure relates to the technical field of air conditioning, and in particular, to an air conditioning system, an air conditioning control method and device, and a computer-readable storage medium.
  • the air-conditioning system of the related art generally has high energy consumption problems such as dehumidification energy consumption, heating energy consumption, defrosting energy consumption, or fresh air energy consumption. This will result in a waste of resources.
  • an air conditioning system including: a compressor connected by a pipeline to form a first circuit, an indoor heat exchanger, a first throttle member, and an outdoor heat exchanger; a heat accumulator, In parallel with the indoor heat exchanger, wherein the compressor, the heat accumulator and the outdoor heat exchanger are connected by a pipeline to form a second circuit.
  • the air conditioning system further includes: a second throttling component disposed on the pipeline between the first throttling component and the outdoor heat exchanger, and included in the first loop and In the second loop.
  • the air conditioning system further includes: a first control valve disposed on the pipeline between the heat accumulator and the compressor and included in the second circuit.
  • the air-conditioning system further includes: a third throttle component disposed on the pipeline between the heat accumulator and the second throttle component and included in the second circuit.
  • the heat accumulator includes multiple sets of heat storage modules connected in parallel.
  • the air conditioning system further includes: a heat recovery heat exchanger connected in parallel with the outdoor heat exchanger, wherein the compressor, the heat recovery heat exchanger, and the first throttle component A third circuit is formed by connecting with the indoor heat exchanger through a pipeline.
  • the heat recovery heat exchanger is connected to a pipeline between the indoor heat exchanger and the first throttle member through a pipeline provided with a check valve.
  • the air conditioning system further includes: a second control valve disposed on the pipeline between the heat recovery heat exchanger and the compressor and included in the third circuit.
  • the air conditioning system further includes: a fourth throttling component, disposed on the pipeline between the heat recovery heat exchanger and the first throttling component, and included in the third circuit in.
  • the air conditioning system further includes a directional valve including a first valve port connected to the inlet of the compressor and a second valve port connected to the outlet of the compressor A third valve port connected to the indoor heat exchanger and the heat accumulator, and a fourth valve port connected to the outdoor heat exchanger and the heat recovery heat exchanger.
  • the air conditioning system further includes: a humidifier disposed near the heat recovery heat exchanger.
  • the air conditioning system further includes: a first filter, which is provided at the air inlet of the air conditioning system and is used for performing first filtering of air.
  • the air conditioning system further includes: a fresh air subsystem, which is disposed near the air inlet of the air conditioning system.
  • the fresh air subsystem includes: a full heat exchanger for making the outdoor fresh air temperature close to the indoor temperature through heat exchange.
  • the fresh air subsystem includes: a second filter for second filtering air.
  • an air conditioner control method including: in a defrosting mode, controlling at least part of the high-temperature refrigerant flowing out of the compressor to an outdoor heat exchanger, and performing an operation on the outdoor heat exchanger Heating to achieve defrosting, condensing into a liquid state and flowing into the compressor through a regenerator.
  • a portion of the high-temperature refrigerant flowing out of the compressor flows to the outdoor heat exchanger, and the outdoor heat exchanger is heated to achieve defrosting, condensed into a liquid state, and then flows into the compressor through the regenerator ;
  • Another part of the high-temperature refrigerant flowing out of the compressor flows to the heat recovery heat exchanger, heating the heat recovery heat exchanger to achieve heating, condensing into a liquid state and flowing into the compressor through the heat accumulator.
  • the air conditioning control method further includes: controlling the humidifier disposed near the heat recovery heat exchanger to turn on, and passing another portion of the high temperature refrigerant to the heat recovery heat exchanger from the humidifier The water is heated to achieve humidification.
  • the flow rate of another part of the high-temperature refrigerant to the heat recovery heat exchanger is controlled by the throttle member.
  • the air conditioning control method further includes: in the heating mode, controlling a part of the high-temperature refrigerant flowing out of the compressor to the indoor heat exchanger to heat the indoor heat exchanger, and another part of the high-temperature refrigerant flowing to the The heat accumulator heats the heat accumulator, condenses to a liquid state, and flows into the compressor through the outdoor heat exchanger.
  • the air conditioning control method further includes: controlling the fresh air subsystem to turn on to filter air.
  • an air conditioner control device including: a memory; and a processor coupled to the memory, the processor configured to be based on instructions stored in the memory, Perform the air conditioning control method as described in any of the foregoing embodiments.
  • a computer-readable storage medium on which a computer program is stored, which when executed by a processor implements the air-conditioning control method as described in any of the foregoing embodiments.
  • FIG. 1A is a schematic diagram showing the structure of an air conditioning system according to some embodiments of the present disclosure
  • FIG. 1B is a schematic structural diagram illustrating an air conditioning system according to other embodiments of the present disclosure.
  • FIG. 1C is a schematic diagram showing the structure of an air conditioning system according to still other embodiments of the present disclosure.
  • FIG. 2A is a schematic diagram showing the structure of an indoor unit of an air conditioning system according to some embodiments of the present disclosure
  • FIG. 2B is a side view of the structure shown in FIG. 2A;
  • FIG. 3 is a schematic diagram showing the structure of a fresh air subsystem according to some embodiments of the present disclosure
  • FIG. 4 is a schematic diagram showing the structure of a heat accumulator according to some embodiments of the present disclosure.
  • FIG. 5 is a schematic diagram showing the structure of a humidifier according to some embodiments of the present disclosure.
  • 6A is a schematic diagram showing the principle of the defrosting mode of the air conditioning system according to some embodiments of the present disclosure
  • 6B is a schematic diagram illustrating the defrosting mode of the air conditioning system according to other embodiments of the present disclosure.
  • FIG. 7A is a schematic diagram illustrating the heating mode of the air conditioning system according to some embodiments of the present disclosure.
  • FIG. 7B is a schematic diagram illustrating the heating mode of the air conditioning system according to other embodiments of the present disclosure.
  • FIG. 7C is a schematic diagram illustrating the heating mode of the air-conditioning system according to still other embodiments of the present disclosure.
  • FIG. 8A is a schematic diagram illustrating the cooling mode of the air conditioning system according to some embodiments of the present disclosure.
  • FIG. 8B is a schematic diagram illustrating the cooling mode of the air conditioning system according to some other embodiments of the present disclosure.
  • FIG. 9 is a block diagram illustrating an air-conditioning control device according to some embodiments of the present disclosure.
  • FIG. 10 is a block diagram illustrating a computer system for implementing some embodiments of the present disclosure.
  • the present disclosure proposes a solution that can solve the energy consumption problem of the air conditioning system and realize energy conservation and environmental protection.
  • FIG. 1A is a schematic diagram showing the structure of an air conditioning system according to some embodiments of the present disclosure.
  • the air-conditioning system 10 includes a compressor 100 connected by a pipeline to form a first circuit, an indoor heat exchanger 110, a first throttle member 111, and an outdoor heat exchanger 120.
  • the first throttling member 111 is used for throttling, depressurizing and adjusting the flow rate of the refrigerant entering and leaving the indoor heat exchanger 110.
  • the first throttle member 111 is, for example, an electronic expansion valve.
  • the second throttle component 121 is also included in the first circuit.
  • the second throttle member 121 is provided on the pipeline between the first throttle member 111 and the outdoor heat exchanger 120.
  • the second throttle member 121 is used to throttle the pressure of the refrigerant entering and leaving the outdoor heat exchanger 120 and adjust the flow rate.
  • the second throttle member 121 is, for example, an electronic expansion valve.
  • the first circuit further includes a directional valve 101.
  • the reversing valve 101 includes a first valve port connected to the inlet of the compressor 100, a second valve port connected to the outlet of the compressor 100, a third valve port connected to the indoor heat exchanger 110 and the heat accumulator 130, and The fourth valve port connected to the outdoor heat exchanger 120.
  • the first valve port of the directional valve communicates with the third valve port
  • the second valve port communicates with the fourth valve port.
  • the first valve port of the directional valve communicates with the fourth valve port
  • the second valve port communicates with the third valve port.
  • the directional valve 101 is, for example, a four-way valve.
  • the air conditioning system 10 also includes a heat accumulator 130. As shown in FIG. 1A, the heat accumulator 130 is connected in parallel with the indoor heat exchanger 110. The compressor 100, the heat accumulator 130, and the outdoor heat exchanger 120 are connected by a pipeline to form a second circuit. As can be seen from FIG. 1A, the directional valve 101 and the second throttle member 121 are also located in the second circuit.
  • a third throttle component 131 is also included in the second circuit.
  • the third throttle member 131 is provided on the pipeline between the second throttle member 121 and the heat accumulator 130.
  • the third throttle member 131 is used to throttle the pressure of the refrigerant entering and leaving the heat accumulator 130 and adjust the flow rate.
  • the third throttle member 131 is, for example, an electronic expansion valve.
  • the second circuit further includes a first control valve 132.
  • the first control valve 132 is provided on the pipeline between the heat accumulator 130 and the compressor 100. That is, the heat accumulator 130 is connected to the pipeline between the compressor 100 and the indoor heat exchanger 110 through the pipeline provided with the first control valve 132.
  • the first control valve 132 is used to control the refrigerant in and out of the regenerator 130, thereby controlling the connection or disconnection of the second circuit.
  • the first control valve 132 is, for example, a solenoid valve.
  • the air conditioning system 10 also includes a heat recovery heat exchanger 140. As shown in FIG. 1A, the heat recovery heat exchanger 140 is connected in parallel with the outdoor heat exchanger 120. The compressor 100, the heat recovery heat exchanger 140, the first throttle member 111, and the indoor heat exchanger 110 are connected by a pipeline to form a third circuit. As can be seen from FIG. 1A, the directional valve 101 is also located in the third circuit.
  • the heat recovery heat exchanger 140 is connected to the pipeline between the indoor heat exchanger 110 and the first throttle member 111 through a pipeline provided with a check valve 143.
  • the one-way valve 143 is used to prevent the refrigerant from being stored in the heat recovery heat exchanger 140 when the heat recovery heat exchanger 140 is closed.
  • the front end of the one-way valve 143 has a capillary tube, which can be designed to have a small pipe diameter and a large length at the front end to allow the refrigerant to be discharged from the heat recovery heat exchanger 140.
  • the amount of refrigerant bypassing the check valve 143 is small.
  • the influence of the one-way valve 143 on heat exchange performance is negligible.
  • the third circuit may further include a second control valve 142.
  • the second control valve 142 is provided on the pipeline between the heat recovery heat exchanger 140 and the reversing valve 101.
  • the second control valve 142 is connected to the second port of the directional valve 101, and the outdoor heat exchanger 120 is connected to the fourth port of the directional valve 101.
  • a fourth throttle component 141 may also be included in the third circuit.
  • the fourth throttle member 141 is provided on the pipeline between the heat recovery heat exchanger 140 and the first throttle member 111. It can also be said that the fourth throttle member 141 is provided on the pipeline between the heat recovery heat exchanger 140 and the second throttle member 121, or between the heat recovery heat exchanger 140 and the third throttle member 131 On the pipeline.
  • the fourth throttling member 141 is used for throttling, depressurizing and adjusting the flow rate of the refrigerant entering and exiting the heat recovery heat exchanger 140.
  • the fourth throttle member 141 is, for example, an electronic expansion valve.
  • the indoor heat exchanger 110, the heat accumulator 130, and the heat recovery heat exchanger 140 all belong to the indoor unit and are located on the right side of the line AB; and the compressor 100 and the outdoor heat exchanger 120 belong to the outdoor unit and are located at Left side of line AB.
  • the indoor unit may further include an indoor fan 150, a humidifier 170, and an electric heater 180.
  • the outdoor unit may further include an outdoor fan 160.
  • FIG. 1B is a schematic diagram showing the structure of an air conditioning system according to other embodiments of the present disclosure.
  • the difference between FIG. 1B and FIG. 1A is that the heat accumulator 130' is located outdoors and belongs to an outdoor unit. Only the differences between FIG. 1B and FIG. 1A will be described below, and the similarities will not be repeated.
  • the throttle member 131 ′ and the control valve 132 ′ corresponding to the heat accumulator 130 ′ are also located outdoors.
  • the throttling member 131' is used for throttling and reducing the flow rate of the refrigerant entering and exiting the heat accumulator 130', for example, an electronic expansion valve.
  • the control valve 132' is used to control the refrigerant in and out of the regenerator 130', and is, for example, a solenoid valve.
  • FIG. 1C is a schematic diagram showing the structure of an air conditioning system according to still other embodiments of the present disclosure. 1C differs from FIG. 1A in that it includes a plurality of heat accumulators 130 connected in parallel. Only the differences between FIG. 1C and FIG. 1A will be described below, and the similarities will not be repeated.
  • multiple heat accumulators 130 are connected in parallel between the throttle member 131 and the control valve 132.
  • the throttling member 131 is used for throttling pressure reduction and flow adjustment of the refrigerant entering and exiting the plurality of heat accumulators 130, for example, an electronic expansion valve.
  • the control valve 132 is used to control the refrigerant in and out of the plurality of heat accumulators 130 and is, for example, a solenoid valve.
  • FIG. 2A is a schematic diagram illustrating an indoor unit of an air conditioning system according to some embodiments of the present disclosure.
  • 2B is a side view of the structure shown in FIG. 2A. The structure of the air-conditioning system 20 will be described below with reference to FIGS. 2A and 2B.
  • the air conditioning system 20 includes a fresh air subsystem 210, a filter 220, a heat accumulator 230, an air inlet 250, and an air outlet 260. As shown in FIG. 2B, the air conditioning system 20 further includes a heat exchanger 240, a humidifier 270, and a heat exchanger 280.
  • the fresh air subsystem 210 is disposed near the air inlet 250 of the air conditioning system.
  • the fresh air subsystem 210 can be turned on for indoor air replacement to achieve the function of purifying indoor air.
  • the fresh air subsystem 210 may have the structure shown in FIG. 3.
  • FIG. 3 shows a schematic structural diagram of a fresh air subsystem according to some embodiments of the present disclosure.
  • the fresh air subsystem 210 includes a total heat exchanger 2101 and a filter 2102.
  • the total heat exchanger 2101 is used to make the outdoor fresh air temperature close to the indoor temperature through heat exchange. This can reduce or even avoid the extra energy consumption caused by the temperature difference between indoor and outdoor.
  • the filter 2102 is used to filter the air introduced from outside.
  • the filter 220 is provided at the air inlet 250 of the air conditioning system. In other words, the filter 220 is disposed near the fresh air subsystem 210 for further filtering air.
  • the heat accumulator 230 is located at the bottom of the air conditioning system. In the heating mode, the heat accumulator 230 can store part of the heat. When the outdoor heat exchanger reaches the defrosting temperature point, the heat accumulator 230 may function as an indoor heat exchanger. That is, the indoor heat exchanger can be turned off, and the heat stored in the heat accumulator 230 can be provided to the outdoor heat exchanger for defrosting use, thereby achieving energy saving and environmental protection.
  • the heat accumulator 230 may have a structure as shown in FIG. 4.
  • FIG. 4 shows a schematic structural diagram of a heat accumulator according to some embodiments of the present disclosure.
  • the heat accumulator 230 includes a heat storage member 2301, a fixed plate 2302, and a support plate 2303.
  • the heat storage member 2301 includes a heat storage material.
  • the heat storage member 2301 is fixed to the fixed plate 2302 and the support plate 2303.
  • the heat exchanger 240 in FIG. 2B can perform heat recovery, and the heat exchanger 240 can replace the electric heater to achieve the effect of energy saving and environmental protection.
  • the heat exchanger 240 can also compensate for the decrease in temperature to achieve the effect of constant temperature dehumidification.
  • the humidifier 270 is located near the heat exchanger 240.
  • the humidifier 270 sprays water on the heat exchanger 240 to evaporate the water mist to achieve the function of humidifying the indoor air.
  • the humidifier 270 has a structure as shown in FIG. 5, for example.
  • FIG. 5 shows a schematic structural view of a humidifier according to some embodiments of the present disclosure.
  • the humidifier 270 includes a humidifying member 2701 and a humidifying nozzle 2702.
  • the humidifier 270 is located near the heat exchanger 280, for example, fixed to the heat exchanger 280.
  • the humidifying component 2701 includes the waterway pipeline of the humidifier 270, the water valve, and related fixing devices. When humidification is required, the water can be converted into water mist after passing through the humidification nozzle 2702.
  • FIG. 6A is a schematic diagram illustrating a defrosting mode of an air conditioning system according to some embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned off, the indoor fan 150 is turned on, the reversing valve 101 is in a cooling state, the first control valve 132 is turned on, the second control valve 142 is turned off, and the first throttle member 111 Closed, the maximum opening of the second throttle member 121, the third throttle member 131 is adjusted according to demand, the fourth throttle member 141 is closed, and the humidifier 170 is closed.
  • the high-temperature refrigerant such as refrigerant
  • the compressor 100 can be controlled to flow to the outdoor heat exchanger 120, and the outdoor heat exchanger 120 is heated to achieve defrosting, condensed into a liquid state, and then flows into the compressor through the regenerator 130 100. That is, the refrigerant flows through the second circuit.
  • the low-temperature and low-pressure refrigerant vapor (such as a low-temperature refrigerant) absorbed from the indoor unit returns to the suction side of the compressor 100 through the reversing valve 101 in the cooled state, and is compressed by the compressor 100 to a high temperature and high pressure Refrigerant gas (such as high temperature refrigerant). Since the second control valve 142 is closed, the refrigerant passes through the reversing valve 101 again, and then directly flows into the outdoor heat exchanger 120. Since the outdoor fan 160 is turned off, the refrigerant will directly heat the outdoor heat exchanger 120 to achieve defrosting, while condensing itself into a liquid state.
  • a high temperature and high pressure Refrigerant gas such as high temperature refrigerant
  • the refrigerant will directly flow into the indoor unit side. Since the first throttle member 111 is closed, the liquid refrigerant will be throttled and decompressed directly through the third throttle member 131 to flow into the heat accumulator 130. The refrigerant evaporates and absorbs heat in the heat accumulator 130, and finally returns to the suction side of the compressor 100 through the reversing valve 101 to complete a refrigeration cycle.
  • the heat exchange with indoor air can be achieved within the defrosting cycle, but the defrosting function is completed. That is, the energy storage of the heat accumulator 130 is used to reduce or even avoid defrosting energy consumption, thereby achieving energy saving and environmental protection.
  • the opening degree of the third throttle member 131 (for example, an electronic expansion valve) can be adjusted.
  • the electric heater 180 may also be turned on.
  • 6B is a schematic diagram illustrating the defrosting mode of the air conditioning system according to other embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned off, the indoor fan 150 is turned on, the reversing valve 101 is in a cooling state, the first control valve 132 is turned on, the second control valve 142 is turned on, and the first throttle member 111 Closed, the maximum opening of the second throttle member 121, the third throttle member 131 is adjusted according to demand, the fourth throttle member 141 is adjusted according to demand, and the humidifier 170 is closed.
  • FIG. 6B is different from FIG. 6A in that the second control valve 142 is opened and the fourth throttle member 141 is adjusted according to demand.
  • the second control valve 142 since the second control valve 142 is closed, the high-temperature refrigerant flowing out of the compressor 100 does not flow to the heat recovery heat exchanger 140, but all flows to the outdoor heat exchanger 120.
  • the second control valve 142 since the second control valve 142 is opened, a part of the high-temperature refrigerant flowing out of the compressor 100 flows to the outdoor heat exchanger 120, and another part flows to the heat recovery heat exchanger 140.
  • a portion of the high-temperature refrigerant flowing to the outdoor heat exchanger 120 heats the outdoor heat exchanger 120 to achieve defrosting, condenses into a liquid state, and flows into the compressor 100 through the regenerator 130.
  • Another part of the high-temperature refrigerant flowing to the heat recovery heat exchanger 140 heats the heat recovery heat exchanger 140 to achieve heating, condenses into a liquid state, and flows into the compressor 100 through the heat accumulator 130.
  • the low-temperature and low-pressure refrigerant vapor absorbed from the indoor unit returns to the suction side of the compressor 100 through the reversing valve 101 in the cooled state, and is compressed by the compressor 100 into a high-temperature and high-pressure refrigerant gas. Since the second control valve 142 is opened, the refrigerant will be divided into two paths.
  • the first-path refrigerant After passing through the reversing valve 101 again, the first-path refrigerant directly flows into the outdoor heat exchanger 120. Since the outdoor fan 160 is turned off, the first-path refrigerant will directly heat the outdoor heat exchanger 120 to achieve defrosting, while condensing itself into a liquid state. Since the second throttle member 121 has the maximum opening degree, the refrigerant will directly flow into the indoor unit side.
  • the second-path refrigerant flows into the heat recovery heat exchanger 140 through the second control valve 142.
  • the second refrigerant can be heated by the return air in the heat recovery heat exchanger 140 to maintain the necessary heating capacity.
  • the liquid refrigerant will be throttled and decompressed directly through the third throttle member 131 to flow into the heat accumulator 130.
  • the refrigerant evaporates and absorbs heat in the heat accumulator 130, and finally returns to the suction side of the compressor 100 through the reversing valve 101 to complete a refrigeration cycle.
  • the defrosting can be realized in the defrosting cycle while achieving a certain amount of heating function. That is, during the defrosting cycle, the heat pump heat recovery technology (that is, the use of heat recovery heat exchangers) is used to replace the pure electric heating system to reduce or even avoid additional heating energy consumption, thereby achieving energy saving and environmental protection. In addition, while defrosting while preserving a certain amount of heating, it can also improve comfort.
  • the heat pump heat recovery technology that is, the use of heat recovery heat exchangers
  • the opening of the fourth throttle member 141 (for example, an electronic expansion valve) can be adjusted.
  • the electric heater 180 can also be turned on when the heating demand is large.
  • the humidifier can also be opened.
  • the second-path refrigerant in the heat recovery heat exchanger 140 realizes the heating of the atomized water sprayed from the humidifier 170, which increases the evaporation efficiency of the atomized water and compensates for the evaporation and absorption of the atomized water.
  • the cooling effect of heat on the return air is shown in FIG. 6B.
  • FIG. 7A is a schematic diagram illustrating the heating mode of the air conditioning system according to some embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned on, the indoor fan 150 is turned on, the reversing valve 101 is in the heating state, the first control valve 132 is turned on, the second control valve 142 is turned off, and the first throttle part 111 is the maximum opening degree, the second throttle member 121 is adjusted according to demand, the third throttle member 131 is closed after being full, the fourth throttle member 141 is closed, and the humidifier 170 is closed.
  • a part of the high-temperature refrigerant flowing out of the compressor 100 can be controlled to flow to the indoor heat exchanger 110 to heat the indoor heat exchanger 110, and another part of the high-temperature refrigerant can flow to the heat accumulator 130 to heat the heat accumulator 130.
  • the low-temperature and low-pressure refrigerant vapor absorbed from the outdoor unit returns to the suction side of the compressor 100 through the reversing valve 101 in the heating state, and is compressed by the compressor 100 into a high-temperature and high-pressure refrigerant gas. Since the second control valve 142 is closed, the refrigerant passes through the reversing valve 101 again and directly flows into the indoor side. Since the first control valve 132 is opened and the third throttle member 131 is at its maximum opening, the refrigerant will be divided into two paths.
  • the first refrigerant flows into the indoor heat exchanger 110, heats the indoor air, and condenses into a liquid by heat exchange.
  • the second-path refrigerant flows into the heat accumulator 130 through the first control valve 132, heats the heat accumulator material of the heat accumulator 130, and condenses to a liquid state while releasing its own heat.
  • first and second liquid refrigerants merge, they are throttled and decompressed by the second throttle member 121, and then flow into the outdoor heat exchanger 120 to evaporate and absorb heat.
  • the finally evaporated low-temperature and low-pressure refrigerant vapor returns to the suction side of the compressor 100 through the reversing valve 101 to complete a heating cycle.
  • the heating function of indoor air is realized.
  • the third throttle member 131 can be closed, thereby reducing or even avoiding system abnormalities caused by the convergence of the refrigerant that cannot continue to condense in the second refrigerant and the first refrigerant.
  • the heat accumulator 130 stores heat, and the stored heat can be used for defrosting, thereby reducing or even avoiding additional defrosting energy consumption.
  • the opening degree of the second throttle member 121 (for example, an electronic expansion valve) can be adjusted.
  • the electric heater 180 can also be turned on when the heating demand is large.
  • a heat accumulator is used to store part of the heat energy generated in the heating mode of the air conditioning system, and the stored heat energy is used for defrosting when defrosting is needed, thereby solving the problem of defrosting energy consumption.
  • FIG. 7B is a schematic diagram illustrating the heating mode of the air conditioning system according to other embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned on, the indoor fan 150 is turned on, the reversing valve 101 is in the heating state, the first control valve 132 is turned off, the second control valve 142 is turned off, and the first throttle part 111 maximum opening degree, the second throttle member 121 is adjusted according to demand, the third throttle member 131 is closed, the fourth throttle member 141 is closed, and the humidifier 170 is closed.
  • FIG. 7B is different from FIG. 7A in that the first control valve 132 is closed and the third throttle member 131 is closed, that is, the heat accumulator 130 does not operate.
  • the refrigerant flows through the first circuit and the second circuit; while in FIG. 7B, the refrigerant flows only through the first circuit.
  • FIG. 7C is a schematic diagram illustrating the heating mode of the air-conditioning system according to still other embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned on, the indoor fan 150 is turned on, the reversing valve 101 is in the heating state, the first control valve 132 is turned off, the second control valve 142 is turned on, and the first throttle part 111 maximum opening degree, the second throttle member 121 is adjusted according to demand, the third throttle member 131 is closed, the fourth throttle member 141 is adjusted according to demand, and the humidifier 170 is turned on.
  • FIG. 7C The difference between FIG. 7C and FIG. 7A is that: the first control valve 132 is closed, the third throttle component 131 is closed, that is, the heat accumulator 130 does not work; but the second control valve 142 is opened, and the fourth throttle component 141 is on demand
  • the regulator and the humidifier 170 are turned on, that is, the heat recovery heat exchanger 140 works, and the humidifier 170 works.
  • the low-temperature and low-pressure refrigerant vapor absorbed from the outdoor unit returns to the suction side of the compressor 100 through the reversing valve 101 in the heating state, and is compressed by the compressor 100 into a high-temperature and high-pressure refrigerant gas. Since the second control valve 142 is opened, the refrigerant will be divided into two paths.
  • the first refrigerant flows into the indoor heat exchanger 110, heats the indoor air, and condenses into a liquid by heat exchange.
  • the second refrigerant passes through the second control valve 142 and flows into the heat recovery heat exchanger 140 while condensing into a liquid state. Since the humidifier 170 is turned on, the second refrigerant is used to heat the atomized water sprayed from the humidifier 170 in the heat recovery heat exchanger 140, which increases the evaporation efficiency of the atomized water and compensates for the evaporation and absorption of the atomized water. The cooling effect of heat on the return air.
  • the third throttle member 131 Since the third throttle member 131 is closed, the first and second channels of liquid refrigerant merge, and then the second throttle member 121 throttles and reduces the pressure, and then flows into the outdoor heat exchanger 120 to evaporate and absorb heat. The finally evaporated low-temperature and low-pressure refrigerant vapor returns to the suction side of the compressor 100 through the reversing valve 101 to complete a heating cycle.
  • the opening of the fourth throttle member 141 (for example, an electronic expansion valve) can be adjusted.
  • FIG. 8A is a schematic diagram illustrating a cooling mode of an air conditioning system according to some embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned on, the indoor fan 150 is turned on, the reversing valve 101 is in a cooling state, the first control valve 132 is turned off, the second control valve 142 is turned on, and the first throttle member 111 is based on Demand adjustment, the maximum opening of the second throttle member 121, the third throttle member 131 is closed, and the fourth throttle member 141 is adjusted according to demand. That is, the refrigerant flows through the first circuit and the third circuit.
  • the low-temperature and low-pressure refrigerant vapor absorbed from the indoor unit returns to the suction side of the compressor 100 through the reversing valve 101 in the cooled state, and is compressed by the compressor 100 into a high-temperature and high-pressure refrigerant gas. Since the second control valve 142 is opened, the refrigerant will be divided into two paths.
  • the first-path refrigerant After passing through the reversing valve 101 again, the first-path refrigerant directly flows into the outdoor heat exchanger 120, exchanges heat and condenses into a liquid state, and flows into the indoor unit side.
  • the second-path refrigerant flows into the indoor heat recovery heat exchanger 140 through the second control valve 142, and the heat is condensed into a liquid state.
  • the second-path refrigerant realizes reheating of the air passing through the heat recovery heat exchanger 140 in the heat recovery heat exchanger 140.
  • the opening degree of the fourth throttle member 141 can be adjusted to control the flow rate of the second refrigerant.
  • the first-path liquid refrigerant will directly merge with the second-path refrigerant, and after being throttled and depressurized by the first throttle member 111 It flows into the indoor heat exchanger 110 to evaporate and absorb heat. The finally evaporated low-temperature and low-pressure refrigerant vapor returns to the suction side of the compressor 100 through the reversing valve 101 to complete a refrigeration cycle.
  • the opening degree of the fourth throttle member 141 can be adjusted to control the flow rate of the second-path refrigerant, that is, to control the reheat amount of the heat recovery heat exchanger 140.
  • the reheat is less than the cooling capacity of the first refrigerant, the overall cooling process is achieved; when the reheat is equal to the cooling capacity of the first refrigerant, the overall temperature is achieved; when the reheat is greater than the first cooling
  • the electric heater 180 can also be turned on when the heating demand is large.
  • the state of the humidifier 170 can be switched according to different needs of humidity. Under the dehumidification demand, the humidifier 170 is turned off. In the temperature adjustment process, the heat recovery heat exchanger 140 is used to reheat the air to achieve dehumidification, which can reduce or even avoid the additional energy consumption caused by the use of a pure electric heating system, thereby achieving energy saving and environmental protection.
  • the humidifier 170 Under the demand of humidification, the humidifier 170 is opened. As shown in FIG. 8A, the second-path refrigerant in the heat recovery heat exchanger 140 can heat the atomized water sprayed from the humidifier 170, increase the evaporation efficiency of the atomized water, and realize humidification.
  • FIG. 8B is a schematic diagram illustrating the cooling mode of the air conditioning system according to other embodiments of the present disclosure.
  • the compressor 100 is turned on, the outdoor fan 160 is turned on, the indoor fan 150 is turned on, the reversing valve 101 is in a cooling state, the first control valve 132 is turned off, the second control valve 142 is turned off, and the first throttle member 111 is based on Demand adjustment, the maximum opening degree of the second throttle member 121, the third throttle member 131 is closed, the fourth throttle member 141 is closed, and the humidifier 170 is closed.
  • FIG. 8B is different from FIG. 8A in that the second control valve 142 is closed and the fourth throttle member 141 is closed, that is, the heat recovery heat exchanger 130 does not operate.
  • the refrigerant flows through the first circuit and the third circuit; while in FIG. 8B, the refrigerant flows only through the first circuit.
  • an air conditioning system which can not only realize the aforementioned functions of defrosting, temperature adjustment, humidification, and dehumidification, but also use the fresh air subsystem to achieve the function of purifying air.
  • the air conditioning system can integrate heat accumulators, heat pump subsystems (ie heat recovery heat exchangers), humidifiers, fresh air subsystems, and filters to achieve the energy-saving effect of constant temperature and humidity air conditioning systems in the process of temperature and humidity control.
  • Different functions of the air conditioning system can be implemented by the air conditioning control device to execute the corresponding method.
  • the defrosting mode at least part of the high-temperature refrigerant flowing out of the compressor is controlled to flow to the outdoor heat exchanger, and the outdoor heat exchanger is heated to achieve defrosting, condensed into a liquid state, and then flows into the heat exchanger through the regenerator compressor.
  • defrosting needs heating at the same time
  • a part of the high-temperature refrigerant flowing out of the compressor is controlled to flow to the outdoor heat exchanger, and another part of the high-temperature refrigerant flows to the heat recovery heat exchanger, which are respectively used to heat the outdoor heat exchanger to Defrosting and heating the heat recovery heat exchanger to achieve heating, condensing into a liquid state and flowing into the compressor through the regenerator.
  • the humidifier provided near the heat recovery heat exchanger is controlled to open, and another part of the high-temperature refrigerant passing through the heat recovery heat exchanger heats the water from the humidifier, To achieve humidification.
  • a part of the high-temperature refrigerant flowing out of the compressor is controlled to flow to the indoor heat exchanger to heat the indoor heat exchanger, and another part of the high-temperature refrigerant flows to the heat accumulator to perform heat storage. It is heated and condensed into a liquid state and flows into the compressor through the outdoor heat exchanger. You can also control the fresh air subsystem to open to filter the air.
  • FIG. 9 is a block diagram illustrating an air-conditioning control device according to some embodiments of the present disclosure.
  • the air-conditioning control device 90 includes a memory 910 and a processor 920 coupled to the memory 910.
  • the memory 910 is used to store instructions for executing the corresponding embodiment of the air-conditioning control method.
  • the processor 920 is configured to execute the air-conditioning control method in any of the embodiments of the present disclosure based on the instructions stored in the memory 910.
  • each step in the foregoing air-conditioning control method may be implemented by a processor, and may be implemented in any manner of software, hardware, firmware, or a combination thereof.
  • embodiments of the present disclosure may also take the form of computer program products implemented on one or more non-volatile storage media containing computer program instructions. Therefore, an embodiment of the present disclosure also provides a computer-readable storage medium on which computer instructions are stored, which when executed by a processor implements the air-conditioning control method in any of the foregoing embodiments.
  • FIG. 10 is a block diagram illustrating a computer system for implementing some embodiments of the present disclosure.
  • the computer system can be expressed in the form of a general-purpose computing device.
  • the computer system includes a memory 1010, a processor 1020, and a bus 1000 connecting different system components.
  • the memory 1010 may include, for example, a system memory, a non-volatile storage medium, and the like.
  • the system memory stores, for example, an operating system, application programs, a boot loader (Boot Loader), and other programs.
  • System memory may include volatile storage media, such as random access memory (RAM) and/or cache memory.
  • RAM random access memory
  • the non-volatile storage medium stores, for example, instructions to execute the corresponding embodiments of the display method.
  • Non-volatile storage media include, but are not limited to, disk storage, optical storage, flash memory, and so on.
  • the processor 1020 can be implemented by discrete hardware components such as a general-purpose processor, a digital signal processor (DSP), an application specific integrated circuit (ASIC), a field programmable gate array (FPGA), or other programmable logic devices, discrete gates, or transistors achieve.
  • each module such as the judgment module and the determination module, can be implemented by executing instructions of the corresponding steps in the central processing unit (CPU) running memory, or by a dedicated circuit that executes the corresponding steps.
  • the bus 1000 can use any of various bus structures.
  • the bus structure includes but is not limited to an industry standard architecture (ISA) bus, a micro channel architecture (MCA) bus, and a peripheral component interconnect (PCI) bus.
  • ISA industry standard architecture
  • MCA micro channel architecture
  • PCI peripheral component interconnect
  • the computer system may further include an input and output interface 1030, a network interface 1040, a storage interface 1050, and the like. These interfaces 1030, 1040, 1050 and the memory 1010 and the processor 1020 may be connected by a bus 1000.
  • the input-output interface 1030 can provide a connection interface for input-output devices such as a display, a mouse, and a keyboard.
  • the network interface 1040 provides a connection interface for various networked devices.
  • the storage interface 1050 provides a connection interface for external storage devices such as floppy disks, U disks, and SD cards.

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Abstract

一种空调系统(10)、空调控制方法和装置(90)，以及计算机可读存储介质。空调系统(10)包括通过管路连接形成第一回路的压缩机(100)、室内换热器(110)、第一节流部件(111)和室外换热器(120)；蓄热器(130)与室内换热器(110)并联。压缩机(100)、蓄热器(130)和室外换热器(120)通过管路连接形成第二回路。该空调控制方法包括在化霜模式下，控制从压缩机(100)流出的至少部分高温冷媒流向室外换热器(120)，对室外换热器(120)进行加热以实现化霜，冷凝为液态后经蓄热器(130)流进压缩机(100)。该空调控制装置(90)执行该空调控制方法，该计算机可读存储介质上存储的计算机程序实现该空调控制方法。该空调系统及方法能够解决耗能问题，实现节能环保。

Description

空调系统、空调控制方法和装置、计算机可读存储介质
相关申请的交叉引用
本申请是以CN申请号为201811486676.0，申请日为2018年12月6日的申请为基础，并主张其优先权，该CN申请的公开内容在此作为整体并入本申请中。
技术领域
本公开涉及空调技术领域，特别涉及一种空调系统、空调控制方法和装置、计算机可读存储介质。
背景技术
相关技术的空调系统普遍存在诸如除湿耗能、制热耗能、化霜耗能、或新风耗能等高耗能问题。这将导致资源浪费。
发明内容
根据本公开实施例的一个方面，提供了一种空调系统，包括：通过管路连接形成第一回路的压缩机、室内换热器、第一节流部件和室外换热器；蓄热器，与所述室内换热器并联，其中所述压缩机、所述蓄热器和所述室外换热器通过管路连接形成第二回路。
在一些实施例中，所述空调系统还包括：第二节流部件，设置在所述第一节流部件和所述室外换热器之间的管路上、且包括在所述第一回路和所述第二回路中。
在一些实施例中，所述空调系统还包括：第一控制阀，设置在所述蓄热器和所述压缩机之间的管路上、且包括在所述第二回路中。
在一些实施例中，所述空调系统还包括：第三节流部件，设置在所述蓄热器和所述第二节流部件之间的管路上、且包括在所述第二回路中。
在一些实施例中，所述蓄热器包括并联的多组蓄热模块。
在一些实施例中，所述空调系统，还包括：热回收换热器，与所述室外换热器并联，其中所述压缩机、所述热回收换热器、所述第一节流部件和所述室内换热器通过管路连接形成第三回路。
在一些实施例中，所述热回收换热器通过设置有单向阀的管路连接到所述室内换 热器和所述第一节流部件之间的管路。
在一些实施例中，所述空调系统还包括：第二控制阀，设置在所述热回收换热器与所述压缩机之间的管路上、且包括在所述第三回路中。
在一些实施例中，所述空调系统还包括：第四节流部件，设置在所述热回收换热器与所述第一节流部件之间的管路上、且包括在所述第三回路中。
在一些实施例中，所述空调系统还包括：换向阀，所述换向阀包括与所述压缩机的进口连接的第一阀口、与所述压缩机的出口连接的第二阀口、与所述室内换热器和所述蓄热器连接的第三阀口、以及与所述室外换热器和所述热回收换热器连接的第四阀口。
在一些实施例中，所述空调系统还包括：加湿器，设置在所述热回收换热器附近。
在一些实施例中，所述空调系统还包括：第一过滤器，设置在所述空调系统的进风口，用于对空气进行第一过滤。
在一些实施例中，所述空调系统还包括：新风子系统，设置在所述空调系统的进风口附近。
在一些实施例中，所述新风子系统包括：全热交换器，用于通过热交换使得室外新风温度接近室内温度。
在一些实施例中，所述新风子系统包括：第二过滤器，用于对空气进行第二过滤。
根据本公开实施例的另一方面，提供了一种空调控制方法，包括：在化霜模式下，控制从压缩机流出的至少部分高温冷媒流向室外换热器，对所述室外换热器进行加热以实现化霜，冷凝为液态后经蓄热器流进所述压缩机。
在一些实施例中，从压缩机流出的一部分高温冷媒流向室外换热器，对所述室外换热器进行加热以实现化霜，冷凝为液态后经所述蓄热器流进所述压缩机；从压缩机流出的另一部分高温冷媒流向热回收换热器，对所述热回收换热器进行加热以实现制热，冷凝为液态后经所述蓄热器流进所述压缩机。
在一些实施例中，所述空调控制方法还包括：控制设置在所述热回收换热器附近的加湿器打开，经过所述热回收换热器的另一部分高温冷媒对来自所述加湿器的水进行加热，以实现加湿。
在一些实施例中，通过节流部件控制流向所述热回收换热器的另一部分高温冷媒的流量。
在一些实施例中，所述空调控制方法还包括：在制热模式下，控制从压缩机流出 的一部分高温冷媒流向室内换热器对所述室内换热器进行加热，另一部分高温冷媒流向所述蓄热器对所述蓄热器进行加热，分别冷凝为液态后经所述室外换热器流进所述压缩机。
在一些实施例中，所述空调控制方法还包括：控制新风子系统打开以过滤空气。
根据本公开实施例的又一方面，提供了一种空调控制装置，包括：存储器；和耦接至所述存储器的处理器，所述处理器被配置为基于存储在所述存储器中的指令，执行如前述任一实施例所述的空调控制方法。
根据本公开实施例的再一方面，提供了一种计算机可读存储介质，其上存储有计算机程序，该程序被处理器执行时实现如前述任一实施例所述的空调控制方法。
通过以下参照附图对本公开的示例性实施例的详细描述，本公开的其它特征及其优点将会变得清楚。
附图说明
构成说明书的一部分的附图描述了本公开的实施例，并且连同说明书一起用于解释本公开的原理。
参照附图，根据下面的详细描述，可以更加清楚地理解本公开，其中：
图1A是示出根据本公开一些实施例的空调系统的结构示意图；
图1B是示出根据本公开另一些实施例的空调系统的结构示意图；
图1C是示出根据本公开又一些实施例的空调系统的结构示意图；
图2A是示出根据本公开一些实施例的空调系统的室内机的结构示意图；
图2B是图2A所示的结构的侧视图；
图3是示出根据本公开一些实施例的新风子系统的结构示意图；
图4是示出示出根据本公开一些实施例的蓄热器的结构示意图；
图5是示出根据本公开一些实施例的加湿器的结构示意图；
图6A是示出根据本公开一些实施例的空调系统的化霜模式的原理示意图；
图6B是示出根据本公开另一些实施例的空调系统的化霜模式的原理示意图；
图7A是示出根据本公开一些实施例的空调系统的制热模式的原理示意图；
图7B是示出根据本公开另一些实施例的空调系统的制热模式的原理示意图；
图7C是示出根据本公开又一些实施例的空调系统的制热模式的原理示意图；
图8A是示出根据本公开一些实施例的空调系统的制冷模式的原理示意图；
图8B是示出根据本公开另一些实施例的空调系统的制冷模式的原理示意图；
图9是示出根据本公开一些实施例的空调控制装置的框图；
图10是示出用于实现本公开一些实施例的计算机系统的框图。
应当明白，附图中所示出的各个部分的尺寸并不是按照实际的比例关系绘制的。此外，相同或类似的参考标号表示相同或类似的构件。
具体实施方式
现在将参照附图来详细描述本公开的各种示例性实施例。对示例性实施例的描述仅仅是说明性的，决不作为对本公开及其应用或使用的任何限制。本公开可以以许多不同的形式实现，不限于这里所述的实施例。提供这些实施例是为了使本公开透彻且完整，并且向本领域技术人员充分表达本公开的范围。应注意到：除非另外具体说明，否则在这些实施例中阐述的部件和步骤的相对布置应被解释为仅仅是示例性的，而不是作为限制。
本公开使用的所有术语(包括技术术语或者科学术语)与本公开所属领域的普通技术人员理解的含义相同，除非另外特别定义。还应当理解，在诸如通用字典中定义的术语应当被解释为具有与它们在相关技术的上下文中的含义相一致的含义，而不应用理想化或极度形式化的意义来解释，除非这里明确地这样定义。
对于相关领域普通技术人员已知的技术、方法和设备可能不作详细讨论，但在适当情况下，所述技术、方法和设备应当被视为说明书的一部分。
针对相关技术中存在的资源浪费问题，本公开提出一种解决方案，能够解决空调系统的耗能问题，实现节能环保。
图1A是示出根据本公开一些实施例的空调系统的结构示意图。
如图1A所示，空调系统10包括通过管路连接形成第一回路的压缩机100、室内换热器110、第一节流部件111和室外换热器120。第一节流部件111用于对进出室内换热器110的冷媒进行节流降压和流量调节。第一节流部件111例如为电子膨胀阀。
在一些实施例中，第一回路中还包括第二节流部件121。第二节流部件121设置在第一节流部件111和室外换热器120之间的管路上。第二节流部件121用于对进出室外换热器120的冷媒进行节流降压和流量调节。第二节流部件121例如为电子膨胀阀。
在另一些实施例中，第一回路中还包括换向阀101。换向阀101包括与压缩机100 的进口连接的第一阀口、与压缩机100的出口连接的第二阀口、与室内换热器110和蓄热器130连接的第三阀口、以及与室外换热器120连接的第四阀口。在制冷状态下，换向阀的第一阀口与第三阀口连通、第二阀口与第四阀口连通。在制热状态下，换向阀的第一阀口与第四阀口连通、第二阀口与第三阀口连通。换向阀101例如为四通阀。
空调系统10还包括蓄热器130。如图1A所示，蓄热器130与室内换热器110并联。压缩机100、蓄热器130和室外换热器120通过管路连接形成第二回路。从图1A可以看出，换向阀101和第二节流部件121也位于第二回路中。
在一些实施例中，第二回路中还包括第三节流部件131。第三节流部件131设置在第二节流部件121和蓄热器130之间的管路上。第三节流部件131用于对进出蓄热器130的冷媒进行节流降压和流量调节。第三节流部件131例如为电子膨胀阀。
如图1A所示，第二回路中还包括第一控制阀132。第一控制阀132设置在蓄热器130和压缩机100之间的管路上。即，蓄热器130通过设有第一控制阀132的管路连接到压缩机100和室内换热器110之间的管路。第一控制阀132用于控制蓄热器130中的冷媒进出，从而控制第二回路的连通或断开。第一控制阀132例如为电磁阀。
在一些实施例中，空调系统10还包括热回收换热器140。如图1A所示，热回收换热器140与室外换热器120并联。压缩机100、热回收换热器140、第一节流部件111和室内换热器110通过管路连接形成第三回路。从图1A可以看出，换向阀101也位于第三回路中。
如图1A所示，热回收换热器140通过设置有单向阀143的管路连接到室内换热器110和第一节流部件111之间的管路。单向阀143用于在热回收换热器140关闭的情况下防止冷媒在热回收换热器140中储存。单向阀143的前端有毛细管，可以设计为前端小管径、大长度，以允许冷媒可以从热回收换热器140中泄压出来。单向阀143旁通的冷媒量很少。单向阀143对换热性能的影响可忽略。
第三回路中还可以包括第二控制阀142。第二控制阀142设置在热回收换热器140与换向阀101之间的管路上。第二控制阀142与换向阀101的第二阀口连接，室外换热器120与换向阀101的第四阀口连接。
第三回路中还可以包括第四节流部件141。第四节流部件141设置在热回收换热器140与第一节流部件111之间的管路上。也可以说，第四节流部件141设置在热回收换热器140与第二节流部件121之间的管路上，或者设置在热回收换热器140与第三节流部件131之间的管路上。第四节流部件141用于对进出热回收换热器140的冷 媒进行节流降压和流量调节。第四节流部件141例如为电子膨胀阀。
如图1A所示，室内换热器110、蓄热器130、热回收换热器140均属于室内机，位于线AB右侧；而压缩机100、室外换热器120均属于室外机，位于线AB左侧。如图1A所示，室内机还可以包括室内风机150、加湿器170和电加热器180。室外机还可以包括室外风机160。
图1B是示出根据本公开另一些实施例的空调系统的结构示意图。图1B与图1A的不同之处在于，蓄热器130'位于室外，属于室外机。下面将仅描述图1B与图1A的不同之处，相同之处不再赘述。
如图1B所示，与蓄热器130'相应(例如通过管路连接)的节流部件131'和控制阀132'也位于室外。如前所述，节流部件131'用于对进出蓄热器130'的冷媒进行节流降压和流量调节，例如为电子膨胀阀。控制阀132'用于控制蓄热器130'中的冷媒进出，例如为电磁阀。
图1C是示出根据本公开又一些实施例的空调系统的结构示意图。图1C与图1A的不同之处在于，包括多个并联的蓄热器130。下面将仅描述图1C与图1A的不同之处，相同之处不再赘述。
如图1C所示，多个蓄热器130并联在节流部件131和控制阀132之间。如前所述，节流部件131用于对进出多个蓄热器130的冷媒进行节流降压和流量调节，例如为电子膨胀阀。控制阀132用于控制多个蓄热器130中的冷媒进出，例如为电磁阀。
图2A是示出根据本公开一些实施例的空调系统的室内机的结构示意图。图2B是图2A所示的结构的侧视图。下面将结合图2A和2B描述空调系统20的结构。
如图2A所示，空调系统20包括新风子系统210、过滤器220、蓄热器230、进风口250、出风口260。如图2B所示，空调系统20还包括换热器240、加湿器270和换热器280。
如图2A和2B所示，在空调系统20工作时，空气从进风口250通过过滤器220进入换热器280进行换热，经过交换的空气从出风口260排出。
如图2A所示，新风子系统210设置在空调系统的进风口250附近。当室内空气污浊时，可以开启新风子系统210进行室内空气置换，实现对室内空气净化的功能。
新风子系统210可以具有如图3所示的结构。图3示出根据本公开一些实施例的新风子系统的结构示意图。如图3所示，新风子系统210包括全热交换器2101和过滤器2102。全热交换器2101用于通过热交换使得室外新风温度接近室内温度。这样 可以减少甚至避免因为室内外温差而导致额外的耗能。过滤器2102用于对从室外引入的空气进行过滤。
过滤器220设置在空调系统的进风口250。或者说，过滤器220设置在新风子系统210附近，用于对空气进一步过滤。
如图2A所示，蓄热器230位于空调系统的底部。在制热模式下，蓄热器230可以将一部分热量储存起来。当室外换热器达到化霜温度点时，蓄热器230的作用可以相当于室内换热器。即，可以将室内换热器关闭，而将蓄热器230储存的热量提供给室外换热器化霜使用，从而实现节能环保。
蓄热器230可以具有如图4所示的结构。图4示出根据本公开一些实施例的蓄热器的结构示意图。如图4所示，蓄热器230包括蓄热部件2301、固定板2302和支撑板2303。蓄热部件2301中具有蓄热材料。蓄热部件2301固定于固定板2302和支撑板2303上。
图2B中的换热器240可以进行热回收，并且换热器240可以代替电加热器，以达到节能环保的效果。当空调系统进入除湿模式时，换热器240也可以补偿温度的降低，达到恒温除湿的效果。
如图2B所示，加湿器270位于换热器240附近。当室内需要加湿时，则加湿器270将水喷洒在换热器240上使水雾蒸发，达到对室内空气进行加湿的功能。
加湿器270例如具有如图5所示的结构。图5示出根据本公开一些实施例的加湿器的结构示意图。如图5所示，加湿器270包括加湿部件2701和加湿喷嘴2702。加湿器270位于换热器280附近，例如固定于换热器280上。加湿部件2701包括加湿器270的水路管道、水阀及相关的固定装置。当需要加湿时，可使水经过加湿喷嘴2702后转化为水雾。
图6A是示出根据本公开一些实施例的空调系统的化霜模式的原理示意图。
在该化霜模式下，压缩机100开启、室外风机160关闭、室内风机150开启、换向阀101处于制冷状态、第一控制阀132开启、第二控制阀142关闭、第一节流部件111关闭、第二节流部件121最大开度、第三节流部件131根据需求调节、第四节流部件141关闭、加湿器170关闭。这样，可以控制从压缩机100流出的高温冷媒(如制冷剂)流向室外换热器120，对室外换热器120进行加热以实现化霜，冷凝为液态后经蓄热器130流进压缩机100。即，冷媒流过第二回路。
如图6A所示，从室内机吸收过来的低温低压制冷剂蒸汽(如低温冷媒)，经过 制冷状态下的换向阀101回到压缩机100的吸气侧，被压缩机100压缩成高温高压制冷剂气体(如高温冷媒)。由于第二控制阀142关闭，制冷剂再次经过换向阀101后，直接流入室外换热器120。由于室外风机160为关闭，制冷剂将直接对室外换热器120进行加热以实现化霜，同时自身冷凝为液态。由于第二节流部件121为最大开度，制冷剂将直接流入室内机侧。由于第一节流部件111关闭，液态制冷剂将直接通过第三节流部件131节流降压后流入蓄热器130中。制冷剂在蓄热器130中完成蒸发吸热，最终经换向阀101回到压缩机100的吸气侧，完成一次制冷循环。
如此周而复始，可以在化霜周期内实现不与室内空气进行热交换，但是完成化霜功能。即，采用蓄热器130储能来减少甚至避免化霜耗能，从而实现节能环保。
根据不同的需求，可以对第三节流部件131(例如电子膨胀阀)的开度进行调节。在一些实施例中，当升温需求较大时，还可以开启电加热器180。
图6B是示出根据本公开另一些实施例的空调系统的化霜模式的原理示意图。
在该化霜模式下，压缩机100开启、室外风机160关闭、室内风机150开启、换向阀101处于制冷状态、第一控制阀132开启、第二控制阀142开启、第一节流部件111关闭、第二节流部件121最大开度、第三节流部件131根据需求调节、第四节流部件141根据需求调节、加湿器170关闭。
图6B与图6A的不同之处在于，第二控制阀142开启，第四节流部件141根据需求调节。在图6A中，由于第二控制阀142关闭，从压缩机100流出的高温冷媒不流向热回收换热器140，而全部流向室外换热器120。在图6B中，由于第二控制阀142开启，从压缩机100流出的高温冷媒中有一部分流向室外换热器120，还有另一部分流向热回收换热器140。流向室外换热器120的一部分高温冷媒对室外换热器120进行加热以实现化霜，冷凝为液态后经蓄热器130流进压缩机100。流向热回收换热器140的另一部分高温冷媒对热回收换热器140进行加热以实现制热，冷凝为液态后经蓄热器130流进压缩机100。
如图6B所示，从室内机吸收过来的低温低压制冷剂蒸汽，经过制冷状态下的换向阀101回到压缩机100的吸气侧，被压缩机100压缩成高温高压制冷剂气体。由于第二控制阀142开启，制冷剂将分为2路。
第1路制冷剂再次经过换向阀101后，直接流入室外换热器120。由于室外风机160为关闭，第1路制冷剂将直接对室外换热器120进行加热以实现化霜，同时自身冷凝为液态。由于第二节流部件121为最大开度，制冷剂将直接流入室内机侧。
第2路制冷剂经过第二控制阀142流入热回收换热器140中。第2路制冷剂在热回收换热器140中可实现回风的加热，以维持必要的制热量。
由于第一节流部件111关闭，液态制冷剂将直接通过第三节流部件131节流降压后流入蓄热器130中。制冷剂在蓄热器130中完成蒸发吸热，最终经换向阀101回到压缩机100的吸气侧，完成一次制冷循环。
如此周而复始，可以在化霜周期内实现化霜同时实现一定的制热量的功能。即，在化霜周期内，采用热泵热回收技术(即利用热回收换热器)来代替纯电热系统来减少甚至避免额外的制热耗能，从而实现节能环保。并且，在化霜同时保定一定的制热量，还可以提升舒适性。
根据不同的需求，可以对第四节流部件141(例如电子膨胀阀)的开度进行调节。在一些实施例中，当升温需求较大时，也可以开启电加热器180。
在化霜周期内有加湿需求的情况下，还可以打开加湿器。如图6B所示，第2路制冷剂在热回收换热器140中实现对加湿器170喷出的雾化水进行加热，加大雾化水的蒸发效率，同时补偿雾化水的蒸发吸热对回风的降温效果。
图7A是示出根据本公开一些实施例的空调系统的制热模式的原理示意图。
在该制热模式下，压缩机100开启、室外风机160开启、室内风机150开启、换向阀101处于制热状态、第一控制阀132开启、第二控制阀142关闭、第一节流部件111最大开度、第二节流部件121根据需求调节、第三节流部件131在蓄满后关闭、第四节流部件141关闭、加湿器170关闭。这样，可以控制从压缩机100流出的一部分高温冷媒流向室内换热器110对室内换热器110进行加热，另一部分高温冷媒流向蓄热器130对蓄热器130进行加热，这两部分高温冷媒分别冷凝为液态后经室外换热器120流进压缩机100。即，冷媒流过第一回路和第二回路。
如图7A所示，从室外机吸收过来的低温低压制冷剂蒸汽，经过制热状态下的换向阀101回到压缩机100的吸气侧，被压缩机100压缩成高温高压制冷剂气体。由于第二控制阀142关闭，制冷剂再次经过换向阀101后，直接流入室内侧。由于第一控制阀132开启，第三节流部件131最大开度，制冷剂将分为2路。
第1路制冷剂流入室内换热器110，对室内空气进行加热，同时自身换热冷凝为液态。第2路制冷剂经过第一控制阀132流入蓄热器130中，对蓄热器130的蓄热材料进行加热，同时自身放热被冷凝为液态。
第1路与第2路液态制冷剂汇合后，通过第二节流部件121节流降压后流入室外 换热器120中进行蒸发吸热。最终蒸发后的低温低压制冷剂蒸汽经换向阀101回到压缩机100吸气侧，完成一次制热循环。
如此周而复始，实现室内空气的加热功能。在蓄热器130蓄满热量后，可以关闭第三节流部件131，从而减少甚至避免因第2路制冷剂中无法继续冷凝的制冷剂与第1路制冷剂汇合而造成的系统异常。在制热模式下，蓄热器130储存热量，这些储存的热量可用于化霜，从而减少甚至避免额外的化霜耗能。
根据不同的需求，可以对第二节流部件121(例如电子膨胀阀)的开度进行调节。在一些实施例中，当升温需求较大时，也可以开启电加热器180。
在上述实施例中，采用蓄热器将空调系统制热模式下产生的热能储存一部分，在需要化霜时利用储存的这些热能进行除霜，从而解决化霜耗能的问题。
图7B是示出根据本公开另一些实施例的空调系统的制热模式的原理示意图。
在该制热模式下，压缩机100开启、室外风机160开启、室内风机150开启、换向阀101处于制热状态、第一控制阀132关闭、第二控制阀142关闭、第一节流部件111最大开度、第二节流部件121根据需求调节、第三节流部件131关闭、第四节流部件141关闭、加湿器170关闭。
图7B与图7A的不同之处在于，第一控制阀132关闭，第三节流部件131关闭，即蓄热器130不工作。在图7A中，冷媒流过第一回路和第二回路；而在图7B中，冷媒仅流过第一回路。
图7C是示出根据本公开又一些实施例的空调系统的制热模式的原理示意图。
在该制热模式下，压缩机100开启、室外风机160开启、室内风机150开启、换向阀101处于制热状态、第一控制阀132关闭、第二控制阀142开启、第一节流部件111最大开度、第二节流部件121根据需求调节、第三节流部件131关闭、第四节流部件141根据需求调节、加湿器170开启。
图7C与图7A的不同之处在于：第一控制阀132关闭，第三节流部件131关闭，即蓄热器130不工作；但第二控制阀142开启、第四节流部件141根据需求调节、加湿器170开启，即热回收换热器140工作，且加湿器170工作。
如图7C所示，从室外机吸收过来的低温低压制冷剂蒸汽，经过制热状态下的换向阀101回到压缩机100的吸气侧，被压缩机100压缩成高温高压制冷剂气体。由于第二控制阀142开启，制冷剂会分成2路。
第1路制冷剂流入室内换热器110，对室内空气进行加热，同时自身换热冷凝为 液态。第2路制冷剂经过第二控制阀142流入热回收换热器140中，同时冷凝为液态。由于加湿器170开启，第2路制冷剂在热回收换热器140中实现对加湿器170喷出的雾化水进行加热，加大雾化水的蒸发效率，同时补偿雾化水的蒸发吸热对回风的降温效果。
由于第三节流部件131关闭，第1路与第2路液态制冷剂汇合后，通过第二节流部件121节流降压后流入室外换热器120中进行蒸发吸热。最终蒸发后的低温低压制冷剂蒸汽经换向阀101回到压缩机100吸气侧，完成一次制热循环。
如此周而复始，实现室内空气的加热、加湿功能。根据不同的需求，可以对第四节流部件141(例如电子膨胀阀)的开度进行调节。
图8A是示出根据本公开一些实施例的空调系统的制冷模式的原理示意图。
在该制冷模式下，压缩机100开启、室外风机160开启、室内风机150开启、换向阀101处于制冷状态、第一控制阀132关闭、第二控制阀142开启、第一节流部件111根据需求调节、第二节流部件121最大开度、第三节流部件131关闭、第四节流部件141根据需求调节。即，冷媒流过第一回路和第三回路。
如图8A所示，从室内机吸收过来的低温低压制冷剂蒸汽，经过制冷状态下的换向阀101回到压缩机100的吸气侧，被压缩机100压缩成高温高压制冷剂气体。由于第二控制阀142开启，制冷剂会分成2路。
第1路制冷剂再次经过换向阀101后，直接流入室外换热器120，换热冷凝为液态，流入室内机侧。第2路制冷剂经过第二控制阀142流入室内的热回收换热器140，换热冷凝为液态。第2路制冷剂在热回收换热器140中实现对经过热回收换热器140的空气的再热。根据不同的需求，可以对第四节流部件141的开度进行调节，以控制第2路制冷剂的流量大小。
由于第二节流部件121为最大开度、第三节流部件131为关闭状态，第1路液态制冷剂将直接与第2路制冷剂汇合，通过第一节流部件111节流降压后流入室内换热器110中进行蒸发吸热。最终蒸发后的低温低压制冷剂蒸汽经换向阀101回到压缩机100的吸气侧，完成一次制冷循环。
如此周而复始，可以实现室内空气的调温的功能。根据不同的需求，可以对第四节流部件141的开度进行调节，以控制第2路制冷剂的流量大小，即控制热回收换热器140的再热量。当再热量小于第1路制冷剂的制冷量时，总体实现的是降温过程；当再热量等于第1路制冷剂的制冷量时，总体实现的是恒温过程；当再热量大于第1 路制冷剂的制冷量时，总体实现的是升温过程。在一些实施例中，当升温需求较大时，也可以开启电加热器180。
在调温过程中，根据湿度的不同需求，可以切换加湿器170的状态。在除湿需求下，关闭加湿器170。在调温过程中，利用热回收换热器140来对空气再热以实现除湿，能够减少甚至避免采用纯电加热系统导致的额外耗能，从而实现节能环保。
在加湿需求下，打开加湿器170。如图8A所示，第2路制冷剂在热回收换热器140中可实现对加湿器170喷出的雾化水进行加热，加大雾化水的蒸发效率，实现加湿。
图8B是示出根据本公开另一些实施例的空调系统的制冷模式的原理示意图。
在该制冷模式下，压缩机100开启、室外风机160开启、室内风机150开启、换向阀101处于制冷状态、第一控制阀132关闭、第二控制阀142关闭、第一节流部件111根据需求调节、第二节流部件121最大开度、第三节流部件131关闭、第四节流部件141关闭、加湿器170关闭。
图8B与图8A的不同之处在于，第二控制阀142关闭，第四节流部件141关闭，即热回收换热器130不工作。在图8A中，冷媒流过第一回路和第三回路；而在图8B中，冷媒仅流过第一回路。
根据本公开的一些实施例，提供了一种空调系统，除了能够实现前述化霜、调温、加湿、除湿等功能之外，还能够利用新风子系统达到净化空气的功能。空调系统可以集蓄热器、热泵子系统(即热回收换热器)、加湿器、新风子系统、过滤器于一体，实现恒温恒湿空调系统在控温控湿过程中的节能效果。
空调系统的不同功能都可以通过空调控制装置来执行相应的方法来实现。
例如，在化霜模式下，控制从压缩机流出的至少部分高温冷媒流向室外换热器，对所述室外换热器进行加热以实现化霜，冷凝为液态后经蓄热器流进所述压缩机。在化霜同时需要制热的情形下，控制从压缩机流出的一部分高温冷媒流向室外换热器、另一部分高温冷媒流向热回收换热器，分别用于对所述室外换热器进行加热以实现化霜和对所述热回收换热器进行加热以实现制热，冷凝为液态后经所述蓄热器流进所述压缩机。在化霜同时需要加湿的情形下，控制设置在所述热回收换热器附近的加湿器打开，经过所述热回收换热器的另一部分高温冷媒对来自所述加湿器的水进行加热，以实现加湿。
又例如，在制热模式下，控制从压缩机流出的一部分高温冷媒流向室内换热器对 所述室内换热器进行加热，另一部分高温冷媒流向所述蓄热器对所述蓄热器进行加热，分别冷凝为液态后经所述室外换热器流进所述压缩机。还可以控制新风子系统打开以过滤空气。
图9是示出根据本公开一些实施例的空调控制装置的框图。
如图9所示，空调控制装置90包括：存储器910以及耦接至该存储器910的处理器920。存储器910用于存储执行空调控制方法对应实施例的指令。处理器920被配置为基于存储在存储器910中的指令，执行本公开中任意一些实施例中的空调控制方法。
应当理解，前述空调控制方法中的各个步骤都可以通过处理器来实现，并且可以软件、硬件、固件或其结合的任一种方式实现。
除了空调控制方法、装置之外，本公开实施例还可采用在一个或多个包含有计算机程序指令的非易失性存储介质上实施的计算机程序产品的形式。因此，本公开实施例还提供一种计算机可读存储介质，其上存储有计算机指令，该指令被处理器执行时实现前述任意实施例中的空调控制方法。
图10是示出用于实现本公开一些实施例的计算机系统的框图。
如图10所示，计算机系统可以通用计算设备的形式表现。计算机系统包括存储器1010、处理器1020和连接不同系统组件的总线1000。
存储器1010例如可以包括系统存储器、非易失性存储介质等。系统存储器例如存储有操作系统、应用程序、引导装载程序(Boot Loader)以及其他程序等。系统存储器可以包括易失性存储介质，例如随机存取存储器(RAM)和/或高速缓存存储器。非易失性存储介质例如存储有执行显示方法的对应实施例的指令。非易失性存储介质包括但不限于磁盘存储器、光学存储器、闪存等。
处理器1020可以用通用处理器、数字信号处理器(DSP)、应用专用集成电路(ASIC)、现场可编程门阵列(FPGA)或其它可编程逻辑设备、分立门或晶体管等分立硬件组件方式来实现。相应地，诸如判断模块和确定模块的每个模块，可以通过中央处理器(CPU)运行存储器中执行相应步骤的指令来实现，也可以通过执行相应步骤的专用电路来实现。
总线1000可以使用多种总线结构中的任意总线结构。例如，总线结构包括但不限于工业标准体系结构(ISA)总线、微通道体系结构(MCA)总线、外围组件互连(PCI)总线。
计算机系统还可以包括输入输出接口1030、网络接口1040、存储接口1050等。这些接口1030、1040、1050以及存储器1010和处理器1020之间可以通过总线1000连接。输入输出接口1030可以为显示器、鼠标、键盘等输入输出设备提供连接接口。网络接口1040为各种联网设备提供连接接口。存储接口1050为软盘、U盘、SD卡等外部存储设备提供连接接口。
至此，已经详细描述了本公开的各种实施例。为了避免遮蔽本公开的构思，没有描述本领域所公知的一些细节。本领域技术人员根据上面的描述，完全可以明白如何实施这里公开的技术方案。
虽然已经通过示例对本公开的一些特定实施例进行了详细说明，但是本领域的技术人员应该理解，以上示例仅是为了进行说明，而不是为了限制本公开的范围。本领域的技术人员应该理解，可在不脱离本公开的范围和精神的情况下，对以上实施例进行修改或者对部分技术特征进行等同替换。本公开的范围由所附权利要求来限定。

Claims (23)

  1. 一种空调系统，包括：
    通过管路连接形成第一回路的压缩机、室内换热器、第一节流部件和室外换热器；
    蓄热器，与所述室内换热器并联，其中，所述压缩机、所述蓄热器和所述室外换热器通过管路连接形成第二回路。
  2. 如权利要求1所述的空调系统，还包括：第二节流部件，设置在所述第一节流部件和所述室外换热器之间的管路上、且包括在所述第一回路和所述第二回路中。
  3. 如权利要求2所述的空调系统，还包括：第一控制阀，设置在所述蓄热器和所述压缩机之间的管路上、且包括在所述第二回路中。
  4. 如权利要求2所述的空调系统，还包括：第三节流部件，设置在所述蓄热器和所述第二节流部件之间的管路上、且包括在所述第二回路中。
  5. 如权利要求1所述的空调系统，其中，所述蓄热器包括并联的多组蓄热模块。
  6. 如权利要求1所述的空调系统，还包括：
    热回收换热器，与所述室外换热器并联，其中所述压缩机、所述热回收换热器、所述第一节流部件和所述室内换热器通过管路连接形成第三回路。
  7. 如权利要求6所述的空调系统，其中，所述热回收换热器通过设置有单向阀的管路连接到所述室内换热器和所述第一节流部件之间的管路。
  8. 如权利要求6所述的空调系统，还包括：第二控制阀，设置在所述热回收换热器与所述压缩机之间的管路上、且包括在所述第三回路中。
  9. 如权利要求6所述的空调系统，还包括：第四节流部件，设置在所述热回收换热器与所述第一节流部件之间的管路上、且包括在所述第三回路中。
  10. 如权利要求6所述的空调系统，还包括：换向阀，所述换向阀包括与所述压缩机的进口连接的第一阀口、与所述压缩机的出口连接的第二阀口、与所述室内换热器和所述蓄热器连接的第三阀口、以及与所述室外换热器和所述热回收换热器连接的第四阀口。
  11. 如权利要求6所述的空调系统，还包括：
    加湿器，设置在所述热回收换热器附近。
  12. 如权利要求1所述的空调系统，还包括：
    第一过滤器，设置在所述空调系统的进风口，用于对空气进行第一过滤。
  13. 如权利要求1-12任一项所述的空调系统，还包括：
    新风子系统，设置在所述空调系统的进风口附近。
  14. 如权利要求13所述的空调系统，其中，所述新风子系统包括：全热交换器，用于通过热交换使得室外新风温度接近室内温度。
  15. 如权利要求13所述的空调系统，其中，所述新风子系统包括：第二过滤器，用于对空气进行第二过滤。
  16. 一种空调控制方法，包括：
    在化霜模式下，控制从压缩机流出的至少部分高温冷媒流向室外换热器，对所述室外换热器进行加热以实现化霜，冷凝为液态后经蓄热器流进所述压缩机。
  17. 如权利要求16所述的空调控制方法，其中：
    从压缩机流出的一部分高温冷媒流向室外换热器，对所述室外换热器进行加热以实现化霜，冷凝为液态后经所述蓄热器流进所述压缩机；
    从压缩机流出的另一部分高温冷媒流向热回收换热器，对所述热回收换热器进行加热以实现制热，冷凝为液态后经所述蓄热器流进所述压缩机。
  18. 如权利要求17所述的空调控制方法，还包括：
    控制设置在所述热回收换热器附近的加湿器打开，经过所述热回收换热器的另一部分高温冷媒对来自所述加湿器的水进行加热，以实现加湿。
  19. 如权利要求17所述的空调控制方法，其中，通过节流部件控制流向所述热回收换热器的另一部分高温冷媒的流量。
  20. 如权利要求16所述的空调控制方法，还包括：
    在制热模式下，控制从压缩机流出的一部分高温冷媒流向室内换热器对所述室内换热器进行加热，另一部分高温冷媒流向所述蓄热器对所述蓄热器进行加热，分别冷凝为液态后经所述室外换热器流进所述压缩机。
  21. 如权利要求16所述的空调控制方法，还包括：
    控制新风子系统打开以过滤空气。
  22. 一种空调控制装置，包括：
    存储器；以及
    耦接至所述存储器的处理器，所述处理器被配置为基于存储在所述存储器中的指令，执行如权利要求16-21中任一项所述的空调控制方法。
  23. 一种计算机可读存储介质，其上存储有计算机程序，该程序被处理器执行时实现权利要求16-21中任一项所述的空调控制方法。
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