WO2022088838A1 - 一种空调系统的制热控制装置、方法和空调系统 - Google Patents

一种空调系统的制热控制装置、方法和空调系统 Download PDF

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Publication number
WO2022088838A1
WO2022088838A1 PCT/CN2021/111805 CN2021111805W WO2022088838A1 WO 2022088838 A1 WO2022088838 A1 WO 2022088838A1 CN 2021111805 W CN2021111805 W CN 2021111805W WO 2022088838 A1 WO2022088838 A1 WO 2022088838A1
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WIPO (PCT)
Prior art keywords
expansion valve
electronic expansion
temperature
opening degree
conditioning system
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PCT/CN2021/111805
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English (en)
French (fr)
Inventor
王永立
杨玉生
胡强
顾思忠
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珠海格力电器股份有限公司
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Publication of WO2022088838A1 publication Critical patent/WO2022088838A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B5/00—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity
    • F25B5/02—Compression machines, plants or systems, with several evaporator circuits, e.g. for varying refrigerating capacity arranged in parallel
    • 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
    • F24F11/67—Switching between heating and cooling modes
    • 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
    • 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
    • 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
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—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
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor

Definitions

  • the application belongs to the technical field of air conditioning systems, and in particular relates to a heating control device and method for an air conditioning system, and an air conditioning system.
  • a microchannel heat exchanger is a heat exchanger with a channel equivalent diameter of 10-1000 ⁇ m.
  • the micro-channel heat exchanger there are dozens of micro-flow channels in the flat tube, and the micro-flow channels are connected with circular headers at both ends of the flat tube. Baffles are arranged in the header to separate the heat exchanger flow channels into multiple processes.
  • the double-row micro-channel heat exchanger has the problem of unreasonable distribution of the refrigerant in the front and rear rows.
  • the purpose of this application is to provide a heating control device, method and air-conditioning system for an air-conditioning system, so as to solve the problem of unreasonable distribution of refrigerants in the front and rear rows of the double-row micro-channel heat exchanger.
  • the flow of the front and rear micro-channel heat exchangers in the channel heat exchanger is precisely controlled to achieve the effect of reasonably distributing the refrigerant in the double-row micro-channel heat exchanger according to the heat exchange capacity of the heat exchanger.
  • the outdoor heat exchanger of the air-conditioning system includes two or more rows of micro-channel heat exchangers, and the two or more rows of micro-channel heat exchangers are arranged in parallel;
  • a throttling unit is arranged on the pipeline between the micro-channel heat exchanger and the plate heat exchanger of the air-conditioning system;
  • the heating control device of the air-conditioning system includes: an acquisition unit and a control unit;
  • the obtaining unit is configured to obtain the suction temperature and the compressor frequency of the compressor of the air conditioning system, and obtain the outdoor ambient temperature of the air conditioning system;
  • the control unit is configured to, in the heating mode, according to The suction temperature, the compressor frequency and the outdoor ambient temperature control the opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of microchannel heat exchangers.
  • the two or more rows of microchannel heat exchangers include: an inner microchannel heat exchanger and an outer microchannel heat exchanger; the throttling unit corresponding to the inner microchannel heat exchanger includes an inner electronic Expansion valve, the throttling unit corresponding to the external microchannel heat exchanger includes an external electronic expansion valve; wherein, the control unit, according to the suction temperature, the compressor frequency and the outdoor ambient temperature, Controlling the opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of microchannel heat exchangers includes: determining the current opening degree of the external electronic expansion valve according to the intake air temperature , and adjust the opening degree of the external electronic expansion valve according to the determined current opening degree of the external electronic expansion valve; according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the external electronic expansion valve , determining the current opening degree of the internal electronic expansion valve, and adjusting the opening degree of the internal electronic expansion valve according to the determined current opening degree of the internal electronic expansion valve.
  • control unit determines the current opening degree of the external electronic expansion valve according to the intake air temperature, comprising: adjusting the difference between the intake air temperature and the intake air saturation temperature The temperature difference is taken as the suction superheat, and the suction saturation temperature is the saturation temperature corresponding to the suction pressure of the compressor at the suction temperature; according to the difference between the suction superheat and the target superheat The difference value determines the current opening degree of the external electronic expansion valve.
  • control unit determines the current opening degree of the inner electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve, including: Determine the opening correction coefficient of the inner electronic expansion valve according to the compressor frequency and the outdoor ambient temperature; The product is determined as the current opening degree of the internal electronic expansion valve.
  • the control unit determines the opening correction coefficient of the internal electronic expansion valve, including: determining the current frequency interval according to the compressor frequency ; According to the outdoor ambient temperature, determine the current temperature interval; According to the corresponding relationship between the set frequency range, the set temperature range and the set correction coefficient, the set frequency in the corresponding relationship is the same as the current frequency range. The interval and the setting correction coefficient corresponding to the same setting temperature interval as the current temperature interval are determined as the opening correction coefficient of the internal electronic expansion valve.
  • control unit controls the microchannel heat exchange in each row of the two or more rows of the microchannel heat exchangers
  • the opening degree of the throttling unit corresponding to the device further includes: after adjusting the opening degree of the external electronic expansion valve according to the determined current opening degree of the external electronic expansion valve, setting a time interval at intervals and re-according to the said external electronic expansion valve.
  • the suction temperature determines the current opening of the outer electronic expansion valve; after adjusting the opening of the inner electronic expansion valve according to the determined current opening of the inner electronic expansion valve, the interval is set for a time period, and the The compressor frequency, the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve are determined, and the current opening degree of the inner electronic expansion valve is re-determined.
  • an air-conditioning system comprising: the above-mentioned heating control device of the air-conditioning system.
  • the present application provides a heating control method for an air-conditioning system in another aspect, wherein the outdoor heat exchanger of the air-conditioning system includes two or more rows of microchannel heat exchangers, and the two or more rows of microchannels The heat exchangers are arranged in parallel; a throttling unit is arranged on the pipeline between each row of the microchannel heat exchanger and the plate heat exchanger of the air conditioning system; the heating control method of the air conditioning system includes: : obtain the suction temperature and compressor frequency of the compressor of the air-conditioning system, and obtain the outdoor ambient temperature of the air-conditioning system; in the heating mode, according to the suction temperature, the compressor frequency and the The outdoor ambient temperature is used to control the opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of microchannel heat exchangers.
  • the two or more rows of microchannel heat exchangers include: inner rows of microchannel heat exchangers and outer rows of microchannel heat exchangers; throttling units corresponding to the inner rows of microchannel heat exchangers It includes an inner electronic expansion valve, and the throttling unit corresponding to the outer row microchannel heat exchanger includes an outer electronic expansion valve; wherein, according to the suction temperature, the compressor frequency and the outdoor ambient temperature, the control system is The opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of microchannel heat exchangers includes: determining the current opening degree of the external electronic expansion valve according to the suction temperature, and Adjust the opening degree of the external electronic expansion valve according to the determined current opening degree of the external electronic expansion valve; determine the opening degree of the external electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the external electronic expansion valve the current opening degree of the internal electronic expansion valve, and adjust the opening degree of the internal electronic expansion valve according to the determined current opening
  • determining the current opening degree of the external electronic expansion valve according to the intake air temperature includes: taking the temperature difference between the intake air temperature and the intake air saturation temperature as the intake superheat degree,
  • the suction saturation temperature is the saturation temperature corresponding to the suction pressure of the compressor at the suction temperature;
  • the external electronic expansion valve is determined according to the difference between the suction superheat and the target superheat. the current opening.
  • determining the current opening degree of the inner electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve includes: according to the compressor frequency and the outdoor ambient temperature to determine the opening correction coefficient of the inner electronic expansion valve; the product of the current opening of the outer electronic expansion valve and the opening correction coefficient of the inner electronic expansion valve is determined as the The current opening of the internal electronic expansion valve.
  • determining the opening correction coefficient of the internal electronic expansion valve according to the compressor frequency and the outdoor ambient temperature includes: determining a current frequency interval according to the compressor frequency; According to the corresponding relationship between the set frequency range, the set temperature range and the set correction coefficient, the set frequency range that is the same as the current frequency range and the set frequency range that is the same as the current frequency range in the corresponding relationship The setting correction coefficient corresponding to the setting temperature interval with the same current temperature interval is determined as the opening correction coefficient of the internal electronic expansion valve.
  • the node corresponding to each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers is controlled the opening degree of the flow unit, further comprising: after adjusting the opening degree of the external electronic expansion valve according to the determined current opening degree of the external electronic expansion valve, and at intervals of a set time period, re-determining the selected external electronic expansion valve according to the intake air temperature.
  • the current opening degree of the external electronic expansion valve after adjusting the opening degree of the internal electronic expansion valve according to the determined current opening degree of the internal electronic expansion valve, the interval is set for a time length, and the compressor frequency,
  • the outdoor ambient temperature and the current opening degree of the outer electronic expansion valve are used to re-determine the current opening degree of the inner electronic expansion valve.
  • the solution of the present application realizes precise control of the refrigerant flow by connecting the front and rear microchannel heat exchangers in the double-row micro-channel heat exchanger with electronic expansion valves respectively, and the double-row micro-channel heat exchange is realized by the double electronic expansion valve.
  • the refrigerant in the front and rear microchannel heat exchangers in the heat exchanger is precisely controlled, so as to solve the problem of unreasonable distribution of refrigerant in the front and rear microchannel heat exchangers existing in the double-row microchannel heat exchanger, and realize the realization of the front and rear microchannel heat exchangers.
  • the refrigerant in the heat exchanger is reasonably distributed according to the capacity of the heat exchanger.
  • the refrigerant flow in the front and rear microchannel heat exchangers in the dual-row microchannel heat exchanger is precisely controlled by the double electronic expansion valve, and the refrigerant in the front and rear microchannel heat exchangers is reasonably distributed.
  • the effect of improving the heat exchange efficiency of the double-row microchannel heat exchanger is achieved.
  • FIG. 1 shows a schematic structural diagram of an embodiment of a heating control device for an air-conditioning system of the present application
  • FIG. 2 is a schematic structural diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application
  • FIG. 3 is a schematic diagram of a frequency interval control flow diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application
  • FIG. 4 is a schematic diagram of an outdoor ambient temperature interval control flow diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application
  • FIG. 5 is a schematic flow chart of the opening degree control process of the dual electronic expansion valves of an embodiment of the parallel dual-row microchannel heat exchanger air conditioning system of the present application;
  • FIG. 6 is a schematic flowchart of an embodiment of a heating control method for an air-conditioning system of the present application
  • FIG. 7 is a schematic flowchart of an embodiment of controlling the opening degree of the electronic expansion valve corresponding to each row of the microchannel heat exchanger in the above two rows of the microchannel heat exchanger in the method of the present application;
  • FIG. 8 is a schematic flowchart of an embodiment of determining the current opening degree of the external electronic expansion valve according to the intake air temperature in the method of the present application;
  • FIG. 9 is a schematic flowchart of an embodiment of determining the current opening degree of the internal electronic expansion valve in the method of the present application.
  • FIG. 10 is a schematic flowchart of an embodiment of determining the opening correction coefficient of the internal electronic expansion valve in the method of the present application
  • FIG. 11 is a schematic flowchart of an embodiment of cyclically controlling the opening of the electronic expansion valve corresponding to each row of the microchannel heat exchangers in the above two rows of the microchannel heat exchangers in the method of the application.
  • FIG. 1 shows a schematic structural diagram of an embodiment of a heating control device of an air conditioning system of the present application.
  • the outdoor heat exchanger of the air conditioning system includes two or more rows of microchannel heat exchangers, and the two or more rows of microchannel heat exchangers are arranged in parallel.
  • a throttling unit is arranged on the pipeline between each row of the microchannel heat exchanger and the plate heat exchanger 7 of the air conditioning system.
  • the heating control device of the air conditioning system includes: an acquisition unit and a control unit.
  • the obtaining unit is configured to obtain the suction temperature and compressor frequency of the compressor of the air-conditioning system, and obtain the outdoor ambient temperature of the air-conditioning system.
  • the control unit is configured to, in the heating mode, control the micro-channel heat exchangers in each row of the two or more rows of the micro-channel heat exchangers according to the suction air temperature, the compressor frequency and the outdoor ambient temperature.
  • the opening degree of the throttling unit corresponding to the channel heat exchanger is used to control the refrigerant flow rate of each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers.
  • the throttle element is an electronic expansion valve.
  • the front and rear microchannel heat exchangers correspond to one electronic expansion valve respectively.
  • the refrigerant is reasonably distributed according to the heat exchange capacity of the heat exchanger.
  • the suction superheat degree of the compressor in the air-conditioning system is adjusted in relation to the opening degree of the external electronic expansion valve of the double-row microchannel heat exchanger.
  • Electronic expansion valve opening degree related adjustment is related to the compressor frequency and the outdoor ambient temperature.
  • two or more rows of the microchannel heat exchangers include: an inner row of microchannel heat exchangers 3 and an outer row of microchannel heat exchangers 4.
  • the throttling unit corresponding to the inner row microchannel heat exchanger 3 includes an inner electronic expansion valve 5
  • the throttling unit corresponding to the outer row microchannel heat exchanger 4 includes an outer electronic expansion valve 6 .
  • control unit controls each row of the microchannels in the two or more rows of the microchannel heat exchangers according to the intake air temperature, the compressor frequency and the outdoor ambient temperature
  • the opening degree of the electronic expansion valve corresponding to the heat exchanger including:
  • the control unit is further configured to determine the current opening degree of the external electronic expansion valve 6 according to the intake air temperature, and adjust the external electronic expansion valve 6 according to the determined current opening degree of the external electronic expansion valve 6 .
  • control unit determines the current opening degree of the external electronic expansion valve 6 according to the intake air temperature, including:
  • the control unit is further configured to use the temperature difference between the intake air temperature and the intake air saturation temperature as the intake air superheat degree.
  • the suction saturation temperature is the saturation temperature corresponding to the suction pressure of the compressor at the suction temperature.
  • the control unit is further configured to determine the current opening degree of the external electronic expansion valve 6 according to the difference between the intake superheat degree and the target superheat degree.
  • the low pressure of the air-conditioning system is detected by the low-pressure sensor 17 of the suction line, and the suction saturation temperature Tb corresponding to this pressure is obtained through the built-in conversion software of the air-conditioning system.
  • the actual intake superheat degree ⁇ T is compared with the given target superheat degree ⁇ Tt, and the opening degree of the external electronic expansion valve 6 is determined through PI adjustment.
  • the control unit is further configured to determine the current opening degree of the inner electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve, and determine the current opening degree of the inner electronic expansion valve according to the determined
  • the current opening degree of the internal electronic expansion valve adjusts the opening degree of the internal electronic expansion valve.
  • the inner electronic expansion valve 5 and the outer electronic expansion valve 6 are synchronously adjusted to ensure the reasonable distribution of the refrigerant in the inner and outer microchannel heat exchangers and improve the heat exchange efficiency; low temperature conditions can also prevent The unreasonable distribution of refrigerant causes the tube temperature to be too low, which causes the heat exchanger to form frost, which has the effect of prolonging the heating cycle under low temperature conditions.
  • the outdoor heat exchanger in the air-conditioning system is a micro-channel heat exchanger, and two rows of micro-channel heat exchangers are provided, and each row of micro-channel heat exchangers is independently connected to an electronic expansion valve.
  • the outer electronic expansion valve can control the refrigerant flow in the outer microchannel heat exchanger
  • the inner electronic expansion valve can control the refrigerant flow in the inner microchannel heat exchanger.
  • Dual electronic expansion valves are used to achieve accurate distribution of refrigerant flow, improve heat exchange efficiency, delay defrosting time, prolong heating cycle, and increase heating capacity.
  • control unit determines the current opening degree of the inner electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve, including:
  • the control unit is further configured to determine an opening correction coefficient of the internal electronic expansion valve 5 according to the compressor frequency and the outdoor ambient temperature.
  • control unit determines an opening correction coefficient of the internal electronic expansion valve, including:
  • the control unit is further configured to determine the current frequency interval according to the compressor frequency.
  • the compressor frequency is divided into four intervals, A, B, C, and D.
  • the frequency is lower than 30Hz at startup, it is located in the D interval, and the interval is T seconds to judge. If the frequency is higher than or equal to 30Hz, the C interval is entered. Otherwise, keep running in the D interval. After entering the C interval, make a judgment at an interval of T seconds. If the frequency is lower than or equal to 25Hz, it will return to the D interval. If the frequency is higher than or equal to 60 Hz, it will enter the B interval, otherwise it will remain in the C interval. After entering the B interval, make a judgment at an interval of T seconds. If the frequency is higher than or equal to 90Hz, it will enter the A interval.
  • the frequency is lower than or equal to 55Hz, it will be reduced to the C interval, otherwise it will remain in the B interval. After entering the A section, it is judged at an interval of T seconds, and the frequency is lower than or equal to 85Hz to enter the B section, otherwise it remains unchanged in the A section.
  • the control unit is further configured to determine the current temperature interval according to the outdoor ambient temperature.
  • the outdoor ambient temperature is divided into four temperature intervals, W, X, Y, and Z. Assuming that the defrost is located in the Z interval, the detection is performed at intervals of T seconds. When the outdoor ambient temperature To is high or equal to -8°C, it enters the Y interval, otherwise it keeps run in the Z range. After entering the Y interval, the detection is performed at intervals of T seconds. When the outdoor ambient temperature is lower than or equal to -10°C, it returns to the Z interval. When the outdoor ambient temperature is higher than or equal to 7°C, it enters the X interval, otherwise it remains in the Y interval. After entering the X interval, it is judged at intervals of T seconds.
  • the control unit is further configured to, according to the corresponding relationship between the set frequency range, the set temperature range and the set correction coefficient, set the set frequency range that is the same as the current frequency range in the corresponding relationship, and
  • the setting correction coefficient corresponding to the setting temperature interval that is the same as the current temperature interval is determined as the opening correction coefficient of the internal electronic expansion valve 5 .
  • the inner and outer row microchannel heat exchangers are respectively connected by setting double electronic expansion valves.
  • the control logic realizes the precise distribution of the refrigerant in the front and rear rows, which improves the heat exchange efficiency by 10%.
  • the frost formation rate of the heat exchanger under low temperature conditions is delayed, and the heating cycle is prolonged.
  • the control unit is further configured to determine the product of the current opening degree of the outer electronic expansion valve and the opening degree correction coefficient of the inner electronic expansion valve as the current opening degree of the inner electronic expansion valve.
  • control unit in the heating mode, controls the electronic circuits corresponding to each row of the microchannel heat exchangers according to the suction temperature, the compressor frequency and the outdoor ambient temperature.
  • the opening of the expansion valve also includes:
  • the control unit is further configured to, after adjusting the opening degree of the external electronic expansion valve 6 according to the determined current opening degree of the external electronic expansion valve 6, at an interval for a set period of time, according to the intake air temperature again.
  • the current opening of the external electronic expansion valve is determined.
  • the control unit is further configured to, after adjusting the opening degree of the internal electronic expansion valve 5 according to the determined current opening degree of the internal electronic expansion valve 5, at an interval for a set period of time, re-according to the compressor frequency , the outdoor ambient temperature, and the current opening degree of the outer electronic expansion valve 6 , and re-determine the current opening degree of the inner electronic expansion valve 5 .
  • the difference between the actual suction superheat ⁇ T and the target superheat ⁇ Tt is calculated again, and the reciprocating cycle is calculated and adjusted to ensure the stability of the system operation.
  • the technical solution of the present application is adopted, and the precise control of the refrigerant flow is realized by setting electronic expansion valves for the inner and outer row microchannel heat exchangers respectively. , in order to improve the heat exchange efficiency of the double-row microchannel heat exchanger.
  • an air conditioning system is also provided.
  • the air conditioning system includes a heating control device of the air conditioning system.
  • the heat exchange efficiency of the front and rear microchannel heat exchangers is different due to the different inlet air temperatures.
  • the front microchannel heat exchangers are arranged on the windward side, and the heat exchange efficiency is high, so more refrigerant needs to be supplied; the inlet of the rear microchannel heat exchangers The air temperature is lower, the heat exchange efficiency becomes worse, and less refrigerant is required.
  • the double-row microchannel heat exchanger and its air conditioning system need to be provided with two pressure sensors and temperature sensors, as well as multiple ball valves, and the opening degree of the electronic expansion valve is not related to the degree of superheat. Therefore, it has many components, complicated control, and imprecise control of opening degree, which may easily lead to abnormal suction superheat compressor liquid shock or system performance degradation, and poor system stability and reliability.
  • the double-row microchannel heat exchanger and its air conditioning system are provided with two rows of microchannel heat exchangers, but during heating, the front and rear microchannel heat exchangers are connected in series, resulting in poor heat exchange reliability.
  • the solution of the present application provides a dual-row microchannel heat exchanger air conditioning system and a heating control method thereof, using dual electronic Expansion valve control, an electronic expansion valve is installed in the front and rear micro-channel heat exchangers, and the refrigerant flow in the front and rear micro-channel heat exchangers is precisely controlled through double electronic expansion valves, so that the refrigerant in the double-row micro-channel heat exchangers is controlled.
  • the suction superheat degree of the compressor in the air conditioning system is adjusted in association with the opening degree of the external electronic expansion valve of the outer row microchannel heat exchanger, and the opening degree of the inner electronic expansion valve of the inner row microchannel heat exchanger It is adjusted in relation to the opening degree of the external electronic expansion valve through the opening correction coefficient ⁇ .
  • the opening correction coefficient ⁇ is related to the frequency of the compressor and the outdoor ambient temperature, and is given by a large number of experimental data.
  • the refrigerant in the internal and external exhaust microchannel heat exchangers can be accurately distributed to achieve efficient heat exchange, delay the frost formation time of the microchannel heat exchanger, prolong the heating cycle, and increase the heating capacity.
  • FIG. 2 is a schematic structural diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application.
  • the parallel double-row micro-channel heat exchanger air-conditioning system includes: a compressor 1, a four-way valve 2, an outer-unit inner-row micro-channel heat exchanger 3, and an outer-unit outer-row micro-channel heat exchanger 4, Internal Electronic Expansion Valve 5, External Electronic Expansion Valve 6, Plate Heat Exchanger 7, Air Supplement Electronic Expansion Valve 8, Globe Valves 9, 14, Internal Electronic Expansion Valves 10, 12, Internal Heat Exchangers 11, 13, External Fan 15, gas-liquid separator 16, low pressure sensor 17, suction temperature sensor 18.
  • the inlet air temperature of the inner row microchannel heat exchanger 3 is the temperature after being exchanged with the outer row microchannel heat exchanger 4, its temperature is lower than that of the outer row microchannel heat exchanger.
  • the heat exchange effect is lower than that of the outer row microchannel heat exchanger 4, so the refrigerant flow rate of the inner row microchannel heat exchanger 3 is lower than that of the outer row microchannel heat exchanger 4.
  • the inner row microchannel heat exchanger 3 corresponds to the refrigerant flow rate.
  • the opening degree of the inner electronic expansion valve 5 is lower than the opening degree of the outer electronic expansion valve 6 corresponding to the outer row microchannel heat exchanger 4 .
  • the inlet air temperature of the inner row microchannel heat exchanger 3 is related to the ambient temperature and the tube temperature of the outer row microchannel heat exchanger 4.
  • the tube temperature of the outer row microchannel heat exchanger 4 decreases with the increase of the refrigerant circulation volume. Again it depends on the compressor frequency. Therefore, the compressor frequency and outdoor temperature parameters are used as factors for the correction coefficient ⁇ of the inner electronic expansion valve 5 and the outer electronic expansion valve 6 .
  • FIG. 3 is a schematic diagram of a frequency range control flow diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application.
  • Zone D, Zone C, Zone B, and ZoneA are the intervals D, C, B, and A where the compressor frequency is located, and Ft is the compressor frequency.
  • the compressor frequency is divided into four intervals: A, B, C, and D.
  • the interval is T seconds to judge. If the frequency is higher than or equal to 30Hz, enter the C interval, otherwise keep running in D interval. After entering the C interval, make a judgment at an interval of T seconds. If the frequency is lower than or equal to 25Hz, it will return to the D interval. If the frequency is higher than or equal to 60 Hz, it will enter the B interval, otherwise it will remain in the C interval. After entering the B section, the interval is T seconds to judge. If the frequency is higher than or equal to 90Hz, it will enter the A section.
  • the frequency is lower than or equal to 55Hz, it will be reduced to the C section, otherwise it will remain in the B section. After entering the A section, it is judged at an interval of T seconds, and the frequency is lower than or equal to 85Hz to enter the B section, otherwise it remains unchanged in the A section.
  • FIG. 4 is a schematic diagram of an outdoor environment interval control flow diagram of an embodiment of the parallel double-row microchannel heat exchanger air conditioning system of the present application.
  • Zone W, Zone X, Zone Y, and Zone Z are the outdoor ambient temperature range.
  • the outdoor ambient temperature is divided into four temperature intervals, W, X, Y, and Z. Assuming that the defrost is located in the Z interval, the detection is performed at an interval of T seconds. When the outdoor ambient temperature To is higher than or equal to -8°C, it enters Y interval, otherwise keep running in the Z interval. After entering the Y interval, the detection is performed at intervals of T seconds. When the outdoor environment is lower than or equal to -10°C, it returns to the Z interval. When the outdoor ambient temperature is higher than or equal to 7°C, it enters the X interval, otherwise it remains in the Y interval. After entering the X range, it is judged at intervals of T seconds.
  • Table 1 Corresponding numerical table of the opening correction coefficient ⁇ of the internal electronic expansion valve 5
  • aa-dd is the specific value of the correction coefficient ⁇ corresponding to different frequency ranges and external ambient temperature ranges, and the value of the correction coefficient ⁇ is between 0 and 1.
  • the heating cycle process is as follows: the low-temperature and low-pressure gas enters the suction port of the compressor 1 from the outlet of the gas-liquid separator 16, and is compressed into a high-temperature and high-pressure gas through the four-way valve 2 and enters the stop valve 14, and then passes through the internal unit. After the heat exchange of the heat exchangers 11 and 13, a high temperature and high pressure liquid is formed. After passing through the electronic expansion valves 10 and 12 of the internal machine respectively, they merge and pass through the stop valve 9. Some of them pass through the air supplement electronic expansion valve 8 for throttling and cooling, and enter the plate heat exchange.
  • the low-temperature and low-pressure gas coming out of the plate heat exchanger 7 enters the supplemental gas enthalpy increasing pipe of the compressor 1, and another large part of the high-temperature liquid refrigerant enters the plate heat exchanger 7 through the main circuit for further subcooling, and is divided into two paths , one route is throttled by the inner electronic expansion valve 5 and then enters the inner row microchannel heat exchanger 3 for heat exchange, and the other route is throttled through the outer electronic expansion valve 6 and then enters the outer row microchannel heat exchanger 4 for heat exchange, After the low-temperature and low-pressure gases from the gas collecting pipe are combined, they pass through the four-way valve 2 and then enter the gas-liquid separator 16 . The low-temperature and low-pressure gas from the gas-liquid separator 16 enters the suction port of the compressor 1 through the suction pipe to complete a heating cycle.
  • FIG. 5 is a schematic flowchart of the opening degree control of the dual electronic expansion valves of an embodiment of the parallel dual-row microchannel heat exchanger air conditioning system of the present application.
  • the low pressure of the system is detected by the low pressure sensor 17 of the suction line, and the suction saturation temperature Tb corresponding to this pressure is obtained through the built-in conversion software of the air conditioning system.
  • the actual intake superheat degree ⁇ T is compared with the given target superheat degree ⁇ Tt, and the opening degree of the external electronic expansion valve 6 is determined through PI adjustment.
  • Detect parameters such as compressor frequency and outdoor ambient temperature and look up Table 1 to obtain the correction coefficient ⁇ of the internal electronic expansion valve 5 .
  • the inner electronic expansion valve 5 (ie the electronic expansion valve 5 of the inner row microchannel heat exchanger) is adjusted synchronously with the outer electronic expansion valve 6 to ensure the reasonable distribution of the refrigerant in the inner and outer row microchannel heat exchangers and improve the heat exchange efficiency. Under the low temperature condition, it can also prevent the unreasonable distribution of the refrigerant from causing the tube temperature to be too low and cause frosting of the heat exchanger, thereby prolonging the heating cycle under the low temperature condition.
  • the opening degree of the inner electronic expansion valve EKV and the opening degree of the outer electronic expansion valve EKV are adjusted externally , at an interval of T seconds, the difference between the actual suction superheat degree ⁇ T and the target superheat degree ⁇ Tt is calculated again, and the cycle adjustment is performed to ensure the air conditioning system. Operational stability.
  • the refrigerant flow is regulated by dual electronic expansion valves, and the pipelines connected by the two electronic expansion valves are respectively connected to the inner and outer rows of microchannel heat exchangers.
  • the demand for refrigerant between the front and rear microchannel heat exchangers is different.
  • the precise distribution of the refrigerant in the front and rear rows is realized, and the heat exchange efficiency is improved by 10%; at the same time, through reasonable control logic
  • the refrigerant distribution strategy delays the frost formation rate of the heat exchanger under low temperature conditions and prolongs the heating cycle.
  • the microchannel heat exchangers may be in three or more rows, and each row of the microchannel heat exchangers is correspondingly provided with an electronic expansion valve to control the flow of the refrigerant.
  • the parameters for dividing the compressor frequency and the outdoor ambient temperature interval in FIG. 3 , FIG. 4 and Table 1 may be other values.
  • the technical solution of the present application is adopted, and the electronic expansion valve is respectively connected to the front and rear microchannel heat exchangers in the double-row microchannel heat exchanger, so as to realize the precise control of the refrigerant flow.
  • the refrigerant flow is adjusted by the double electronic expansion valve, which solves the problem of different refrigerant demand between the front and rear microchannel heat exchangers under different working conditions and different compressor frequencies. , which improves the heat exchange efficiency.
  • a heating control method of an air-conditioning system corresponding to an air-conditioning system is also provided, as shown in FIG. 6 , a schematic flowchart of an embodiment of the method of the present application.
  • the outdoor heat exchanger of the air conditioning system includes a micro-channel heat exchanger, the number of the micro-channel heat exchanger is two or more rows, and the micro-channel heat exchangers in two or more rows are arranged in parallel.
  • a throttling unit is arranged on the pipeline between each row of the microchannel heat exchangers and the plate heat exchanger 7 of the air conditioning system.
  • the heating control method of the air conditioning system includes: step S110 and step S120.
  • step S110 the suction temperature and the compressor frequency of the compressor of the air conditioning system are obtained, and the outdoor ambient temperature of the air conditioning system is obtained.
  • Step S120 in the heating mode, according to the suction temperature, the compressor frequency and the outdoor ambient temperature, control the position of each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers.
  • the opening degree of the corresponding throttling unit is used to control the refrigerant flow of each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers.
  • the control of dual electronic expansion valves is adopted, and an electronic expansion valve is respectively set in the front and rear microchannel heat exchangers.
  • the flow is precisely controlled, so that the refrigerant in the front and rear microchannel heat exchangers in the double-row microchannel heat exchanger can be reasonably distributed according to the heat exchange capacity of the heat exchanger.
  • the suction superheat degree of the compressor in the air-conditioning system is adjusted in relation to the opening degree of the external electronic expansion valve of the double-row microchannel heat exchanger.
  • Electronic expansion valve opening degree related adjustment is related to the compressor frequency and the outdoor ambient temperature, which is given by a large number of test data.
  • two or more rows of the microchannel heat exchangers include: an inner row of microchannel heat exchangers 3 and an outer row of microchannel heat exchangers 4 .
  • the throttling unit corresponding to the inner row microchannel heat exchanger 3 includes an inner electronic expansion valve 5
  • the throttling unit corresponding to the outer row microchannel heat exchanger 4 includes an outer electronic expansion valve 6 .
  • the heating cycle process is as follows: the low-temperature and low-pressure gas enters the suction port of the compressor 1 from the outlet of the gas-liquid separator 16, and after being compressed into a high-temperature and high-pressure gas, passes through the four-way valve 2 and enters the stop valve 14, and then passes through the internal heat exchanger 11. After heat exchange in 13 and 13, high temperature and high pressure liquid is formed. After passing through the electronic expansion valves 10 and 12 of the internal machine respectively, they merge and pass through the stop valve 9. Some of them pass through the air supplement electronic expansion valve 8 for throttling and cooling, and enter the plate heat exchanger 7.
  • the low-temperature and low-pressure gas coming out of the plate heat exchanger 7 enters the air supply and enthalpy increasing pipe of the compressor 1, and the other large part of the high-temperature liquid refrigerant enters the plate heat exchanger 7 through the main road for further subcooling, and is divided into two paths, one of which passes through the inner
  • the electronic expansion valve 5 is throttled, it enters the inner row microchannel heat exchanger 3 for heat exchange, and the other path is throttled by the outer electronic expansion valve 6 and then enters the outer row microchannel heat exchanger 4 for heat exchange, and comes out from the gas header.
  • the low temperature and low pressure gas After the low temperature and low pressure gas is combined, it enters the gas-liquid separator 16 through the four-way valve 2 .
  • the low-temperature and low-pressure gas from the gas-liquid separator 16 enters the suction port of the compressor 1 through the suction pipe to complete a heating cycle.
  • step S120 in the heating mode, according to the suction temperature, the compressor frequency and the outdoor ambient temperature, the microchannel heat exchangers in each row of the two or more rows of the microchannel heat exchangers are controlled.
  • the opening degree of the throttling unit corresponding to the heater please refer to the following exemplary description.
  • step S120 The specific process of controlling the opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers in step S120 includes steps S210 and S220.
  • Step S210 determining the current opening degree of the external electronic expansion valve 6 according to the intake air temperature, and adjusting the opening degree of the external electronic expansion valve 6 according to the determined current opening degree of the external electronic expansion valve 6 .
  • the specific process of determining the current opening degree of the external electronic expansion valve by the gas temperature may include steps S310 and S320.
  • Step S310 the temperature difference between the intake air temperature and the intake air saturation temperature is taken as the intake air superheat degree.
  • the suction saturation temperature is the saturation temperature corresponding to the suction pressure of the compressor 1 at the suction temperature.
  • step S320 the current opening degree of the external electronic expansion valve 6 is determined according to the difference between the intake superheat degree and the target superheat degree.
  • the actual intake superheat degree ⁇ T is compared with the given target superheat degree ⁇ Tt, and the opening degree of the external electronic expansion valve 6 is determined through PI adjustment.
  • Step S220 Determine the current opening degree of the internal electronic expansion valve 5 according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the external electronic expansion valve 6, and determine the current opening degree of the internal electronic expansion valve 5 according to the determined internal electronic expansion valve.
  • the current opening degree of the expansion valve 5 adjusts the opening degree of the internal electronic expansion valve 5 .
  • the inner electronic expansion valve 5 and the outer electronic expansion valve 6 are synchronously adjusted to ensure the reasonable distribution of the refrigerant in the inner and outer exhaust microchannel heat exchangers and improve the heat exchange efficiency; the low temperature condition can also prevent the distribution of refrigerant. Unreasonable causes the tube temperature to be too low, causing frosting of the heat exchanger, thereby prolonging the heating cycle under low temperature conditions.
  • the specific process of determining the current opening degree of the internal electronic expansion valve according to the compressor frequency, the outdoor ambient temperature, and the current opening degree of the external electronic expansion valve in step S220 may be: See the example description below.
  • step S220 The specific process of determining the current opening degree of the internal electronic expansion valve in step S220 is further described below with reference to the schematic flowchart of an embodiment of determining the current opening degree of the internal electronic expansion valve in the method of the present application shown in FIG. 9 . It includes: step S410 and step S420.
  • Step S410 Determine an opening correction coefficient of the internal electronic expansion valve according to the compressor frequency and the outdoor ambient temperature.
  • the specific process of determining the opening correction coefficient of the internal electronic expansion valve according to the compressor frequency and the outdoor ambient temperature in step S410 may refer to the following exemplary description.
  • step S410 The specific process of determining the opening correction coefficient of the internal electronic expansion valve in step S410 is further described below with reference to the schematic flowchart of an embodiment of determining the opening correction coefficient of the internal electronic expansion valve in the method of the present application shown in FIG. 10 . , which may include steps S510 to S530.
  • Step S510 Determine the current frequency interval according to the compressor frequency.
  • the compressor frequency is divided into four intervals, A, B, C, and D.
  • the frequency is lower than 30Hz at startup, it is located in the D interval, and the interval is T seconds to judge. If the frequency is higher than or equal to 30Hz, the C interval is entered. Otherwise, keep running in the D interval. After entering the C interval, make a judgment at an interval of T seconds. If the frequency is lower than or equal to 25Hz, it will return to the D interval. If the frequency is higher than or equal to 60 Hz, it will enter the B interval, otherwise it will remain in the C interval. After entering the B interval, make a judgment at an interval of T seconds. If the frequency is higher than or equal to 90Hz, it will enter the A interval.
  • the frequency is lower than or equal to 55Hz, it will be reduced to the C interval, otherwise it will remain in the B interval. After entering the A section, it is judged at an interval of T seconds, and the frequency is lower than or equal to 85Hz to enter the B section, otherwise it remains unchanged in the A section.
  • Step S520 Determine the current temperature interval according to the outdoor ambient temperature.
  • the outdoor ambient temperature is divided into four temperature intervals, W, X, Y, and Z. It is assumed that the defrosting is located in the Z interval, and the interval is T seconds.
  • the outdoor ambient temperature To is higher than or equal to -8°C, it enters the Y interval, otherwise Keep running in the Z range. After entering the Y interval, the detection is performed at intervals of T seconds.
  • the outdoor environment is lower than or equal to -10°C, it returns to the Z interval.
  • the outdoor ambient temperature is higher than or equal to 7°C, it enters the X interval, otherwise it remains in the Y interval. After entering the X range, it is judged at intervals of T seconds.
  • Step S530 according to the corresponding relationship between the set frequency range, the set temperature range and the set correction coefficient, the set frequency range that is the same as the current frequency range and the set frequency range that is the same as the current temperature range in the corresponding relationship
  • the set correction coefficient corresponding to the set temperature interval of is determined as the opening correction coefficient of the internal electronic expansion valve 5 .
  • step S420 the product of the current opening degree of the outer electronic expansion valve 6 and the opening degree correction coefficient of the inner electronic expansion valve 5 is determined as the current opening degree of the inner electronic expansion valve.
  • step S120 in the heating mode, according to the intake air temperature, the compressor frequency and the outdoor ambient temperature, control each row of the two or more rows of the microchannel heat exchangers.
  • the opening degree of the throttling unit corresponding to the microchannel heat exchanger further includes: cyclically controlling the opening degree of the throttling unit corresponding to each row of the microchannel heat exchanger in the two or more rows of the microchannel heat exchanger the process of.
  • the following is a schematic flow diagram of an embodiment of cyclically controlling the opening degree of the electronic expansion valve corresponding to each row of the microchannel heat exchangers in the above two rows of the microchannel heat exchangers in the method of the present application shown in FIG. 11 , and further The specific process of cyclically controlling the opening degree of the throttling unit corresponding to each row of the microchannel heat exchangers in the two or more rows of the microchannel heat exchangers is described, which may include steps S610 and S620.
  • Step S610 after adjusting the opening degree of the external electronic expansion valve 6 according to the determined current opening degree of the external electronic expansion valve 6, the external electronic expansion valve 6 is re-determined according to the suction temperature at a set time interval.
  • Step S620 after adjusting the opening degree of the internal electronic expansion valve 5 according to the determined current opening degree of the internal electronic expansion valve 5, set a time interval, and re-according to the compressor frequency and the outdoor ambient temperature. , and the current opening degree of the outer electronic expansion valve 6 , and re-determine the current opening degree of the inner electronic expansion valve 5 .
  • the opening degree EKV of the inner electronic expansion valve and the opening degree EKV of the outer electronic expansion valve are adjusted externally , at an interval of T seconds, the difference between the actual intake superheat degree ⁇ T and the target superheat degree ⁇ Tt is calculated again, and the cycle is adjusted, To ensure the stability of the operation of the air conditioning system.

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Abstract

本申请一种空调系统的制热控制装置、方法和空调系统，所述控制装置，包括：获取单元，获取空调系统的压缩机(1)的吸气温度和压缩机频率，并获取空调系统的室外环境温度；控制单元，在制热模式下，根据吸气温度、压缩机频率和室外环境温度，控制两排以上微通道换热器中每排微通道换热器(3,4)所对应的节流单元的开度。所述空调系统的室外换热器包括并联设置的所述两排以上微通道换热器(3,4)，在每排微通道换热器的管路上均设置有所述节流单元。

Description

一种空调系统的制热控制装置、方法和空调系统
相关申请的交叉引用
本申请要求于2020年10月30日提交中国专利局，申请号为202011195968.6，申请名称为“一种空调系统的制热控制装置、方法和空调系统”的中国专利申请的优先权,在此将其全文引入作为参考。
技术领域
本申请属于空调系统技术领域，具体涉及一种空调系统的制热控制装置、方法和空调系统。
背景技术
微通道换热器，就是通道当量直径为10-1000μm的换热器。在微通道换热器中，扁平管内有数十条细微流道，细微流道在扁平管的两端与圆形集管相联。集管内设置隔板，将换热器流道分隔成多个流程。双排微通道换热器，存在前后排冷媒分配不合理的问题。
上述内容仅用于辅助理解本申请的技术方案，并不代表上述内容是现有技术。
发明内容
本申请的目的在于，提供一种空调系统的制热控制装置、方法和空调系统，以解决双排微通道换热器存在前后排冷媒分配不合理的问题，通过双电子膨胀阀对双排微通道换热器中前后排微通道换热器的流量进行精准控制，以实现根据换热器换热能力合理分配双排微通道换热器中的冷媒的效果。
本申请提供的一种空调系统的制热控制装置中，所述空调系统的室外换热器包括两排以上微通道换热器，所述两排以上微通道换热器并联设置；在每排所述微通道换热器与所述空调系统的板式换热器之间的管路上，均设置有节流单元；所述空调系统的制热控制装置包括：获取单元和控制单元；其中，所述获取单元，被配置为获取所述空调系统的压缩机的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度；所述控制单元，被配置为在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度。
在一些实施方式中，所述两排以上微通道换热器，包括：内微通道换热器和外微通道换热器；所述内微通道换热器所对应的节流单元包括内电子膨胀阀，所述外排微通道换热器所对应 的节流单元包括外电子膨胀阀；其中，所述控制单元，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度，包括：根据所述吸气温度确定所述外电子膨胀阀的当前开度，并根据确定的所述外电子膨胀阀的当前开度调节所述外电子膨胀阀的开度；根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，并根据确定的所述内电子膨胀阀的当前开度调节所述内电子膨胀阀的开度。
在一些实施方式中，所述控制单元，所述控制单元，根据所述吸气温度确定所述外电子膨胀阀的当前开度，包括：将所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度，所述吸气饱和温度，是在所述吸气温度下所述压缩机的吸气压力所对应的饱和温度；根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀的当前开度。
在一些实施方式中，所述控制单元，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，包括：根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数；将所述外电子膨胀阀的当前开度和所述内电子膨胀阀的开度修正系数的乘积，确定为所述内电子膨胀阀的当前开度。
在一些实施方式中，所述控制单元，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数，包括：根据所述压缩机频率，确定当前频率区间；根据所述室外环境温度，确定当前温度区间；根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀的开度修正系数。
在一些实施方式中，所述控制单元，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，还包括：在根据确定的所述外电子膨胀阀的当前开度对所述外电子膨胀阀进行开度调节之后，间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀的当前开度；在根据确定的所述内电子膨胀阀的当前开度对所述内电子膨胀阀进行开度调节之后，间隔设定时长，重新根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，并重新确定所述内电子膨胀阀的当前开度。
与上述装置相匹配，本申请再一方面提供一种空调系统，包括：以上所述的空调系统的制热控制装置。
与上述空调系统相匹配，本申请再一方面提供一种空调系统的制热控制方法中，所述空调系统的室外换热器包括两排以上微通道换热器，所述两排以上微通道换热器并联设置；在每排 所述微通道换热器与所述空调系统的板式换热器之间的管路上，均设置有节流单元；所述空调系统的制热控制方法，包括：获取所述空调系统的压缩机的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度；在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度。
在一些实施方式中，所述两排以上微通道换热器，包括：内排微通道换热器和外排微通道换热器；所述内排微通道换热器所对应的节流单元包括内电子膨胀阀，所述外排微通道换热器所对应的节流单元包括外电子膨胀阀；其中，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度，包括：根据所述吸气温度确定所述外电子膨胀阀的当前开度，并根据确定的所述外电子膨胀阀的当前开度调节所述外电子膨胀阀的开度；根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，并根据确定的所述内电子膨胀阀的当前开度调节所述内电子膨胀阀的开度。
在一些实施方式中，根据所述吸气温度确定所述外电子膨胀阀的当前开度，包括：将所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度，所述吸气饱和温度，是在所述吸气温度下所述压缩机的吸气压力所对应的饱和温度；根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀的当前开度。
在一些实施方式中，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，包括：根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数；将所述外电子膨胀阀的当前开度和所述内电子膨胀阀的开度修正系数的乘积，确定为所述内电子膨胀阀的当前开度。
在一些实施方式中，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数，包括：根据所述压缩机频率，确定当前频率区间；根据所述室外环境温度，确定当前温度区间；根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀的开度修正系数。
在一些实施方式中，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，还包括：在根据确定的所述外电子膨胀阀的当前开度对所述外电子膨胀阀进行开度调节之后，间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀的当前开度；在根据确定的所述内电子膨胀阀的当前开度对所述内电子膨胀阀进行开度调节之后，间隔设定时长，重新根据所述压缩机频率、所 述室外环境温度、以及所述外电子膨胀阀的当前开度，并重新确定所述内电子膨胀阀的当前开度。
由此，本申请的方案，通过对双排微通道换热器中前后排微通道换热器分别接电子膨胀阀实现对冷媒流量的精准控制，通过双电子膨胀阀对双排微通道换热器中前后排微通道换热器中的冷媒进行精准控制，从而解决双排微通道换热器存在的前后排微通道换热器中冷媒分配不合理的问题，实现前后排微通道换热器中的冷媒按照换热器能力合理分配。
进一步地，本申请的方案，通过双电子膨胀阀对双排微通道换热器中前后排微通道换热器中的冷媒流量进行精准控制，合理分配前后排微通道换热器中的冷媒，以解决在不同工况、不同压缩机频率时前后排微通道换热器的换热效率不同的问题，达到提升双排微通道换热器的换热效率的效果。
本申请的其它特征和优点将在随后的说明书中阐述，并且，部分地从说明书中变得显而易见，或者通过实施本申请而了解。
下面通过附图和实施例，对本申请的技术方案做进一步的详细描述。
附图说明
图1示出了本申请的空调系统的制热控制装置的一实施例的结构示意图；
图2为本申请的并联双排微通道换热器空调系统的一实施例的结构示意图；
图3为本申请的并联双排微通道换热器空调系统的一实施例的频率区间控制流程示意图；
图4为本申请的并联双排微通道换热器空调系统的一实施例的室外环境温度区间控制流程示意图；
图5为本申请的并联双排微通道换热器空调系统的一实施例的双电子膨胀阀的开度控制流程示意图；
图6为本申请的空调系统的制热控制方法的一实施例的流程示意图；
图7为本申请的方法中控制两排以上所述微通道换热器中每排所述微通道换热器所对应的电子膨胀阀的开度的一实施例的流程示意图；
图8为本申请的方法中根据所述吸气温度确定所述外电子膨胀阀的当前开度的一实施例的流程示意图；
图9为本申请的方法中确定所述内电子膨胀阀的当前开度的一实施例的流程示意图；
图10为本申请的方法中确定所述内电子膨胀阀的开度修正系数的一实施例的流程示意图；
图11为本申请的方法中循环控制两排以上所述微通道换热器中每排所述微通道换热器所 对应的电子膨胀阀的开度的一实施例的流程示意图。
结合附图，本申请实施例中附图标记如下：
1-压缩机；2-四通阀；3-内排微通道换热器；4-外排微通道换热器；5-内电子膨胀阀；6-外电子膨胀阀；7-板式换热器；8-补气电子膨胀阀；9、14-截止阀；10、12-内机电子膨胀阀；11、13-内机换热器；15-外风机；16-气液分离器；17-低压传感器；18-吸气感温包。
具体实施方式
为使本申请的目的、技术方案和优点更加清楚，下面将结合本申请具体实施例及相应的附图对本申请技术方案进行清楚、完整地描述。显然，所描述的实施例仅是本申请一部分实施例，而不是全部的实施例。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都属于本申请保护的范围。
根据本申请的实施例，提供了一种空调系统的制热控制装置。参见图1，图1示出了本申请的空调系统的制热控制装置的一实施例的结构示意图。所述空调系统的室外换热器包括两排以上微通道换热器，所述两排以上微通道换热器并联设置。在每排所述微通道换热器与所述空调系统的板式换热器7之间的管路上，均设置有节流单元。所述空调系统的制热控制装置，包括：获取单元和控制单元。
其中，所述获取单元，被配置为获取所述空调系统的压缩机的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度。
所述控制单元，被配置为在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，以对两排以上所述微通道换热器中每排所述微通道换热器的冷媒流量进行控制。
具体地，节流元件为电子膨胀阀。采用双电子膨胀阀控制，前后排微通道换热器分别对应一个电子膨胀阀，通过双电子膨胀阀对双排微通道换热器中的流量进行精准控制，使双排微通道换热器中的冷媒根据换热器的换热能力合理分配。空调系统中压缩机的吸气过热度与双排微通道换热器的外电子膨胀阀开度关联调节，双排微通道换热器的内电子膨胀阀开度通过开度修正系数β与外电子膨胀阀开度关联调节。其中，开度修正系数β与压缩机频率和室外环境温度关联。
由此，通过对内外排微通道换热器中的冷媒精准分配，实现高效换热实现延缓微通道换热器的结霜时间，延长制热周期，提升制热量的目的。
如图2所示，在一些实施方式中，两排以上所述微通道换热器，包括：内排微通道换热器 3和外排微通道换热器4。所述内排微通道换热器3所对应的节流单元包括内电子膨胀阀5，所述外排微通道换热器4所对应的节流单元包括外电子膨胀阀6。
其中，所述控制单元，在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的电子膨胀阀的开度，包括：
所述控制单元，具体还被配置为根据所述吸气温度确定所述外电子膨胀阀6的当前开度，并根据确定的所述外电子膨胀阀6的当前开度调节所述外电子膨胀阀6的开度。
在一些实施方式中，所述控制单元，根据所述吸气温度确定所述外电子膨胀阀6的当前开度，包括：
所述控制单元，具体还被配置为将所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度。所述吸气饱和温度，是在所述吸气温度下所述压缩机的吸气压力所对应的饱和温度。
所述控制单元，具体还被配置为根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀6的当前开度。
具体地，制热运行过程中，通过吸气管路的低压传感器17检测空调系统低压，通过空调系统内置换算软件得出此压力对应的吸气饱和温度Tb，通过吸气管路上的感温包检测吸气温度T1，实际吸气过热度ΔT＝吸气温度T1-吸气饱和温度Tb。实际吸气过热度ΔT与给定的目标过热度ΔTt比较，通过PI调节确定外电子膨胀阀6的开度。
所述控制单元，具体还被配置为根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，并根据确定的所述内电子膨胀阀的当前开度调节所述内电子膨胀阀的开度。
具体地，制热运行过程中，内电子膨胀阀5与外电子膨胀阀6同步调节，保证内、外排微通道换热器中的冷媒合理分配，提高换热效率；低温工况还可以防止冷媒分配不合理造成管温过低，引起换热器结霜，起到低温工况延长制热周期的效果。
微通道机型采用双排微通道换热器时，因前后排进风温度不同，所需冷媒流量也不同。本申请的方案中，空调系统中的室外换热器为微通道换热器，设置有两排微通道换热器，每排微通道换热器单独与一个电子膨胀阀连接，制热运行时可实现外电子膨胀阀控制外排微通道换热器中的冷媒流量，内电子膨胀阀控制内排微通道换热器中的冷媒流量。采用双电子膨胀阀实现冷媒流量精确分配，提升换热效率，延缓化霜时间，延长制热周期，提升制热量。
在一些实施方式中，所述控制单元，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度，包括：
所述控制单元，具体还被配置为根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀5的开度修正系数。
在一些实施方式中，所述控制单元，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数，包括：
所述控制单元，具体还被配置为根据所述压缩机频率，确定当前频率区间。
具体地，将压缩机频率划分为A、B、C、D四个区间，启动时频率低于30Hz，位于D区间，间隔T秒进行判断，如果频率高于或等于30Hz，则进入C区间，否则保持在D区间运行。进入C区间后，间隔T秒进行判断，如果频率低于或等于25Hz则回到D区间，如果频率高于或等于60Hz，则进入B区间，否则保持在C区间。进入B区间后，间隔T秒进行判断，如果频率高于或等于90Hz则进入A区间，如果频率低于或等于55Hz则降低到C区间，否则保持在B区间。进入A区间后，间隔T秒进行判断，频率低于或等于85Hz进入B区间，否则保持在A区间不变。
所述控制单元，具体还被配置为根据所述室外环境温度，确定当前温度区间。
具体地，将室外环境温度划分为W、X、Y、Z四个温度区间，假设除霜位于Z区间，间隔T秒检测，当室外环境温度To高或等于-8℃进入Y区间，否则保持在Z区间运行。进入Y区间后，间隔T秒进行检测，当室外环境温度低于或等于-10℃时，回到Z区间，当室外环境温度高于或等于7℃，进入X区间，否则保持在Y区间。进入X区间后，间隔T秒进行判断，如果室外环境低于或等于5℃，进入Y区间，如果室外环境温度高于或等于18℃，进入W区间，否则保持X区间不变。进入W区间后，如果室外环境温度低于或等于16℃，进入X区间，否则保持W区间运行。
所述控制单元，具体还被配置为根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀5的开度修正系数。
具体地，在不同工况下使用不同的搭配组合进行验证，通过大量试验得出三者的逻辑关系表，确定修正系数β的数值，详见表1。在表1中，aa-dd为修正系数β在不同温度区间和外环区间对应的具体数值，修正系数β数值位于0和1之间。
由此，针对不同工况、不同压缩机频率时双排微通道换热器前后排冷媒需求量不同的问题，通过设置双电子膨胀阀分别连接内、外排微通道换热器，通过合理的控制逻辑实现前后排冷媒精准分配，使得换热效率提升10％。同时通过合理的冷媒分配策略，延缓了低温工况下换热器的结霜速度，延长了制热周期。
所述控制单元，具体还被配置为将所述外电子膨胀阀的当前开度和所述内电子膨胀阀的开度修正系数的乘积，确定为所述内电子膨胀阀的当前开度。
具体地，制热运行过程中，检测压缩机频率，室外环境温度等参数，查表1得到内电子膨胀阀修正系数β。内电子膨胀阀开度EKV 内＝β*EKV 外。
在一些实施方式中，所述控制单元，在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制每排所述微通道换热器所对应的电子膨胀阀的开度，还包括：
所述控制单元，具体还被配置为在根据确定的所述外电子膨胀阀6的当前开度对所述外电子膨胀阀6进行开度调节之后间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀的当前开度。
所述控制单元，具体还被配置为在根据确定的所述内电子膨胀阀5的当前开度对所述内电子膨胀阀5进行开度调节之后间隔设定时长，重新根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀6的当前开度，并重新确定所述内电子膨胀阀5的当前开度。
具体地，EKV 内和EKV 外电子膨胀阀调整后间隔时间T，再次计算实际吸气过热度ΔT与目标过热度ΔTt的差值，往复循环计算调节，保证系统运行的稳定性。
经大量的试验验证，采用本申请的技术方案，通过对内外排微通道换热器分别设置电子膨胀阀实现对冷媒流量的精准控制，从而，通过合理分配前后排微通道换热器中的冷媒，以提升双排微通道换热器的换热效率。
根据本申请的实施例，还提供了一种空调系统。所述空调系统包括所述空调系统的制热控制装置。
前后排微通道换热器由于进风温度不同，导致换热效率不同，前排微通道换热器设置在迎风面，换热效率高，需多供给冷媒；后排微通道换热器的进风温度较低，换热效率变差，所需冷媒较少。
相关方案中，双排微通道换热器及其空调系统，需要设置2个压力传感器和温度传感器、以及多个球阀，且电子膨胀阀开度与过热度没有关联性。因此，其元器件多，控制复杂，而且开度控制不精确，容易导致吸气过热度异常压缩机液击或系统性能衰减，系统稳定性可靠性差。
相关方案中，双排微通道换热器及其空调系统，设置有两排微通道换热器，但在制热时，前后排微通道换热器是串联，换热可靠性差。
针对前后排微通道换热器中冷媒分配不合理的问题，在一些实施方式中，本申请的方案，提供了一种双排微通道换热器空调系统及其制热控制方法，采用双电子膨胀阀控制，前后排微 通道换热器分别设置一个电子膨胀阀，通过双电子膨胀阀对前后排微通道换热器中的冷媒流量进行精准控制，使双排微通道换热器中的冷媒根据换热器换热能力合理分配。
由于不同室外环境温度、不同运行频率下的内外排微通道换热器所需的冷媒量不同，影响换热效率。在本申请的方案中，空调系统中的压缩机的吸气过热度与外排微通道换热器的外电子膨胀阀开度关联调节，内排微通道换热器的内电子膨胀阀开度通过开度修正系数β与外电子膨胀阀开度关联调节。其中，开度修正系数β与压缩机的频率和室外环境温度关联，并通过大量试验数据给出。
通过以上流量调节装置，对内外排微通道换热器中的冷媒精准分配，实现高效换热，实现延缓微通道换热器结霜时间，延长制热周期，提升制热量的目的。
在一些实施方式中，结合图2至图5所示的例子，对本申请的方案的具体实施过程进行示例性说明。
图2为本申请的并联双排微通道换热器空调系统的一实施例的结构示意图。如图2所示，并联双排微通道换热器空调系统，包括：压缩机1，四通阀2，外机内排微通道换热器3，外机外排微通道换热器4，内电子膨胀阀5，外电子膨胀阀6，板式换热器7，补气电子膨胀阀8，截止阀9、14，内机电子膨胀阀10、12，内机换热器11、13，外风机15，气液分离器16，低压传感器17，吸气感温包18。
由于内排微通道换热器3进风温度是与外排微通道换热器4交换后的温度，其温度比相比外排微通道换热器低，内排微通道换热器3的换热效果低于外排微通道换热器4，因此内排微通道换热器3的冷媒流量低于外排微通道换热器4的冷媒流量，内排微通道换热器3对应的内电子膨胀阀5的开度低于外排微通道换热器4对应的外电子膨胀阀6开度。内排微通道换热器3进风温度与环境温度、外排微通道换热器4管温有关，外排微通道换热器4管温随着冷媒循环量增大而降低，冷媒循环量又取决于压缩机频率。因此，将压缩机频率、室外温度参数作为内电子膨胀阀5与外电子膨胀阀6修正系数β的因子。
图3为本申请的并联双排微通道换热器空调系统的一实施例的频率区间控制流程示意图。图3中，Zone D、Zone C、Zone B、ZoneA为压缩机频率所处的区间D、C、B、A，Ft是压缩机频率。
如图3所示，将压缩机频率划分为A、B、C、D四个区间，启动时频率低于30Hz，位于D区间，间隔T秒进行判断，如果频率高于或等于30Hz，则进入C区间，否则保持在D区间运行。进入C区间后，间隔T秒进行判断，如果频率低于或等于25Hz则回到D区间，如果频率高于或等于60Hz，则进入B区间，否则保持在C区间。进入B区间后，间隔T秒进行判断， 如果频率高于或等于90Hz则进入A区间，如果频率低于或等于55Hz则降低到C区间，否则保持在B区间。进入A区间后，间隔T秒进行判断，频率低于或等于85Hz进入B区间，否则保持在A区间不变。
图4为本申请的并联双排微通道换热器空调系统的一实施例的室外环境区间控制流程示意图。图4中，Zone W、Zone X、Zone Y、Zone Z为室外环境温度区间范围。
如图4所示，将室外环境温度划分为W、X、Y、Z四个温度区间，假设除霜位于Z区间，间隔T秒检测，当室外环境温度To高于或等于-8℃进入Y区间，否则保持在Z区间运行。进入Y区间后，间隔T秒进行检测，当室外环境低于或等于-10℃时回到Z区间，当室外环境温度高于或等于7℃，进入X区间，否则保持在Y区间。进入X区间后，间隔T秒进行判断，如果室外环境低于或等于5℃，进入Y区间；如果室外环境温度升高到高于或等于18℃，进入W区间，否则保持X区间不变。进入W区间后，如果室外环境温度低于或等于16℃，进入X区间，否则保持W区间运行。
在不同工况下使用不同的搭配组合进行验证，通过大量试验得出三者的逻辑关系表，确定修正系数β的数值，详见表1。
表1：内电子膨胀阀5的开度修正系数β的对应数值表
Figure PCTCN2021111805-appb-000001
在表1中，aa-dd为修正系数β在不同频率区间和外部环境温度区间对应的具体数值，修正系数β数值位于0和1之间。
在本申请的方案中，制热循环过程为：低温低压气体由气液分离器16出口进入压缩机1吸气口，经过压缩成高温高压气体经四通阀2进入截止阀14后经过内机换热器11、13换热后，形成高温高压液体，分别经过内机电子膨胀阀10、12后，汇合经过截止阀9，其中一部分经过补气电子膨胀阀8进行节流降温进入板式换热器7，从板式换热器7出来后的低温低压气体进入压缩机1的补气增焓管，另一大部分高温液态冷媒经主路进入板式换热器7进一步过冷后，分两路，一路经内电子膨胀阀5进行节流后进入内排微通道换热器3进行换热，另一路经外电子膨胀阀6进行节流后进入外排微通道换热器4进行换热，从集气管出来的低温低压气体汇合后，经过四通阀2再进入气液分离器16。从气液分离器16出来的低温低压气体经吸气管进入压缩机 1吸气口，完成一个制热循环。
图5为本申请的并联双排微通道换热器空调系统的一实施例的双电子膨胀阀的开度控制流程示意图。如图5所示，制热运行过程中，通过吸气管路的低压传感器17检测系统低压，通过空调系统内置换算软件得出此压力对应的吸气饱和温度Tb，通过吸气管路上的感温包检测吸气温度T1，实际吸气过热度ΔT＝吸气温度T1-吸气饱和温度Tb。实际吸气过热度ΔT与给定的目标过热度ΔTt比较，通过PI调节确定外电子膨胀阀6的开度。检测压缩机频率，室外环境温度等参数，查表1得到内电子膨胀阀5的修正系数β。内电子膨胀阀5的开度EKV 内＝β*EKV 外。内电子膨胀阀5(即内排微通道换热器电子膨胀阀5)与外电子膨胀阀6同步调节，保证内外排微通道换热器冷媒合理分配，提高换热效率。低温工况下还可以防止冷媒分配不合理造成管温过低，引起换热器结霜，从而起到低温工况延长制热周期的效果。
内电子膨胀阀的开度EKV 内和外电子膨胀阀的开度EKV 外调整后，间隔时间T秒，再次计算实际吸气过热度ΔT与目标过热度ΔTt的差值，循环调节，保证空调系统运行的稳定性。
经验证，本申请的方案中，通过双电子膨胀阀调节冷媒流量，两个电子膨胀阀连接的管路分别连接内外排微通道换热器。针对不同工况，不同压缩机频率时，前后排微通道换热器之间冷媒需求量不同的问题，通过合理的控制逻辑实现前后排冷媒精准分配，换热效率提升10％；同时通过合理的冷媒分配策略，延缓了低温工况下换热器的结霜速度，延长了制热周期。
在上述实施方式中，微通道换热器可以为三排或多排，每排微通道换热器对应设置一个电子膨胀阀，进行冷媒流量控制。
在上述实施方式中，图3、图4和表1中划分压缩机频率和室外环境温度区间的参数可以是其他数值。
由于本实施例的空调系统所执行的操作及所实现的功能与前述图1所示的装置的实施例、原理和实例对应，故本实施例的描述中未详尽之处，可以参见前述实施例中的相关说明，在此不做赘述。
经大量的试验验证，采用本申请的技术方案，通过对双排微通道换热器中前后排微通道换热器分别接电子膨胀阀，实现对冷媒流量的精准控制。通过双电子膨胀阀调节冷媒流量，解决了不同工况、不同压缩机频率时，前后排微通道换热器之间冷媒需求量不同的问题，通过合理分配前后排微通道换热器中的冷媒，提升了换热效率。
根据本申请的实施例，还提供了对应于空调系统的一种空调系统的制热控制方法，如图6所示本申请的方法的一实施例的流程示意图。所述空调系统的室外换热器包括微通道换热器，所述微通道换热器的数量为两排以上，两排以上所述微通道换热器并联设置。在每排所述微通 道换热器与所述空调系统的板式换热器7之间的管路上，均设置有一个节流单元。所述空调系统的制热控制方法，包括：步骤S110和步骤S120。
步骤S110，获取所述空调系统的压缩机的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度。
步骤S120，在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，以对两排以上所述微通道换热器中每排所述微通道换热器的冷媒流量进行控制。
具体地，采用双电子膨胀阀控制，前后排微通道换热器分别对应设置一个电子膨胀阀，通过双电子膨胀阀对双排微通道换热器中前后排微通道换热器中的冷媒的流量进行精准控制，使双排微通道换热器中前后排微通道换热器中的冷媒根据换热器换热能力合理分配。空调系统中压缩机的吸气过热度与双排微通道换热器的外电子膨胀阀开度关联调节，双排微通道换热器的内电子膨胀阀开度通过开度修正系数β与外电子膨胀阀开度关联调节。其中，开度修正系数β与压缩机频率和室外环境温度关联，通过大量试验数据给出。
由此，通过对内外排微通道换热器中的冷媒流量精准分配，实现高效换热；实现延缓微通道换热器结霜时间，延长制热周期，提升制热量的目的。
在一些实施方式中，两排以上所述微通道换热器，包括：内排微通道换热器3和外排微通道换热器4。所述内排微通道换热器3所对应的节流单元包括内电子膨胀阀5，所述外排微通道换热器4所对应的节流单元包括外电子膨胀阀6。
具体地，制热循环过程为：低温低压气体由气液分离器16出口进入压缩机1吸气口，经过压缩成高温高压气体经四通阀2进入截止阀14后经过内机换热器11、13换热后，形成高温高压液体，分别经过内机电子膨胀阀10、12后，汇合经过截止阀9，其中一部分经过补气电子膨胀阀8进行节流降温进入板式换热器7，从板式换热器7出来后的低温低压气体进入压缩机1的补气增焓管，另一大部分高温液态冷媒经主路进入板式换热器7进一步过冷后，分两路，一路经内电子膨胀阀5进行节流后进入内排微通道换热器3进行换热，另一路经外电子膨胀阀6进行节流后进入外排微通道换热器4进行换热，从集气管出来的低温低压气体汇合后，经过四通阀2再进入气液分离器16。从气液分离器16出来的低温低压气体经吸气管进入压缩机1吸气口，完成一个制热循环。
其中，步骤S120中，在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度的具体过程，可以参见以下示例性说明。
下面结合图7所示本申请的方法中控制两排以上所述微通道换热器中每排所述微通道换热器所对应的电子膨胀阀的开度的一实施例流程示意图，进一步说明步骤S120中控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度的具体过程，包括：步骤S210和步骤S220。
步骤S210，根据所述吸气温度确定所述外电子膨胀阀6的当前开度，并根据确定的所述外电子膨胀阀6的当前开度调节所述外电子膨胀阀6的开度。
在一些实施方式中，可以结合图8所示本申请的方法中根据所述吸气温度确定所述外电子膨胀阀的当前开度的一实施例流程示意图，进一步说明步骤S210中根据所述吸气温度确定所述外电子膨胀阀的当前开度的具体过程，可以包括：步骤S310和步骤S320。
步骤S310，所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度。所述吸气饱和温度，是在所述吸气温度下所述压缩机1的吸气压力所对应的饱和温度。
步骤S320，根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀6的当前开度。
具体地，制热运行过程中，通过吸气管路的低压传感器17检测系统低压，通过空调系统内置换算软件得出此压力对应的吸气饱和温度Tb，通过吸气管路上的感温包检测吸气温度T1，实际吸气过热度ΔT＝吸气温度T1-吸气饱和温度Tb。实际吸气过热度ΔT与给定的目标过热度ΔTt比较，通过PI调节确定外电子膨胀阀6的开度。
步骤S220，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀6的当前开度，确定所述内电子膨胀阀5的当前开度，并根据确定的所述内电子膨胀阀5的当前开度调节所述内电子膨胀阀5的开度。
具体地，制热运行过程中，内电子膨胀阀5与外电子膨胀阀6同步调节，保证内外排微通道换热器中的冷媒合理分配，提高换热效率；低温工况还可以防止冷媒分配不合理造成管温过低，引起换热器结霜，从而起到低温工况延长制热周期的效果。
在一些实施方式中，步骤S220中根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀的当前开度，确定所述内电子膨胀阀的当前开度的具体过程，可以参见以下示例性说明。
下面结合图9所示本申请的方法中确定所述内电子膨胀阀的当前开度的一实施例流程示意图，进一步说明步骤S220中确定所述内电子膨胀阀的当前开度的具体过程，可以包括：步骤S410和步骤S420。
步骤S410，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正 系数。
在一些实施方式中，步骤S410中根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数的具体过程，可以参见以下示例性说明。
下面结合图10所示本申请的方法中确定所述内电子膨胀阀的开度修正系数的一实施例流程示意图，进一步说明步骤S410中确定所述内电子膨胀阀的开度修正系数的具体过程，可以包括：步骤S510至步骤S530。
步骤S510，根据所述压缩机频率，确定当前频率区间。
具体地，将压缩机频率划分为A、B、C、D四个区间，启动时频率低于30Hz，位于D区间，间隔T秒进行判断，如果频率高于或等于30Hz，则进入C区间，否则保持在D区间运行。进入C区间后，间隔T秒进行判断，如果频率低于或等于25Hz则回到D区间，如果频率高于或等于60Hz，则进入B区间，否则保持在C区间。进入B区间后，间隔T秒进行判断，如果频率高于或等于90Hz则进入A区间，如果频率低于或等于55Hz则降低到C区间，否则保持在B区间。进入A区间后，间隔T秒进行判断，频率低于或等于85Hz进入B区间，否则保持在A区间不变。
步骤S520，根据所述室外环境温度，确定当前温度区间。
具体地，将室外环境温度划分为W、X、Y、Z四个温度区间，假设除霜位于Z区间，间隔T秒检测，当室外环境温度To高于或等于-8℃进入Y区间，否则保持在Z区间运行。进入Y区间后，间隔T秒进行检测，当室外环境低于或等于-10℃时回到Z区间，当室外环境温度高于或等于7℃，进入X区间，否则保持在Y区间。进入X区间后，间隔T秒进行判断，如果室外环境低于或等于5℃，进入Y区间；如果室外环境温度升高到高于或等于18℃，进入W区间，否则保持X区间不变。进入W区间后，如果室外环境温度低于或等于16℃，进入X区间，否则保持W区间运行。
步骤S530，根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀5的开度修正系数。
具体地，在不同工况下使用不同的搭配组合进行验证，通过大量试验得出三者的逻辑关系表，确定修正系数β的数值，详见表1。在表1中，aa-dd为修正系数β在不同压缩机频率区间和外部环境温度区间对应的具体数值，修正系数β数值位于0和1之间。
步骤S420，将所述外电子膨胀阀6的当前开度和所述内电子膨胀阀5的开度修正系数的乘积，确定为所述内电子膨胀阀的当前开度。
具体地，制热运行过程中，检测压缩机频率，室外环境温度等参数，查表1得到内电子膨胀阀5的修正系数β。内电子膨胀阀5的开度EKV 内＝β*EKV 外。
在一些实施方式中，步骤S120中，在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，还包括：循环控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度的过程。
下面结合图11所示本申请的方法中循环控制两排以上所述微通道换热器中每排所述微通道换热器所对应的电子膨胀阀的开度的一实施例流程示意图，进一步说明循环控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度的具体过程，可以包括：步骤S610和步骤S620。
步骤S610，在根据确定的所述外电子膨胀阀6的当前开度对所述外电子膨胀阀6进行开度调节之后，间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀6的当前开度。
步骤S620，在根据确定的所述内电子膨胀阀5的当前开度对所述内电子膨胀阀5进行开度调节之后，间隔设定时长，重新根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀6的当前开度，并重新确定所述内电子膨胀阀5的当前开度。
具体地，内电子膨胀阀的开度EKV 内和外电子膨胀阀的开度EKV 外调整后，间隔时间T秒，再次计算实际吸气过热度ΔT与目标过热度ΔTt的差值，循环调节，保证空调系统运行的稳定性。
由于本实施例的方法所执行的操作及所实现的功能与前述空调系统的实施例、原理和实例相对应，故本实施例的描述中未详尽之处，可以参见前述实施例中的相关说明，在此不做赘述。
综上，本领域技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上所述仅为本申请的实施例而已，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种更改和变化。凡在本申请的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本申请的权利要求范围之内。

Claims (13)

  1. 一种空调系统的制热控制装置，其特征在于，所述空调系统的室外换热器包括两排以上微通道换热器，所述两排以上微通道换热器并联设置；在每排所述微通道换热器与所述空调系统的板式换热器(7)之间的管路上，均设置有节流单元；所述空调系统的制热控制装置，包括：获取单元和控制单元；其中，
    所述获取单元，被配置为获取所述空调系统的压缩机(1)的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度；
    所述控制单元，被配置为在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器(3,4)中每排所述微通道换热器所对应的节流单元的开度。
  2. 根据权利要求1所述的空调系统的制热控制装置，其特征在于，所述两排以上微通道换热器，包括：内微通道换热器(3)和外微通道换热器(4)；所述内微通道换热器(3)所对应的节流单元包括内电子膨胀阀(5)，所述外排微通道换热器(4)所对应的节流单元包括外电子膨胀阀(6)；
    其中，所述控制单元，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度，包括：
    根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度，并根据确定的所述外电子膨胀阀(6)的当前开度调节所述外电子膨胀阀的开度；
    根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，确定所述内电子膨胀阀(5)的当前开度，并根据确定的所述内电子膨胀阀(5)的当前开度调节所述内电子膨胀阀(5)的开度。
  3. 根据权利要求2所述的空调系统的制热控制装置，其特征在于，所述控制单元，根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度，包括：
    将所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度，所述吸气饱和温度，是在所述吸气温度下所述压缩机(1)的吸气压力所对应的饱和温度；
    根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀(6)的当前开度。
  4. 根据权利要求2所述的空调系统的制热控制装置，其特征在于，所述控制单元，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，确定所述内电子膨胀阀(5)的当前开度，包括：
    根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数；
    将所述外电子膨胀阀(6)的当前开度和所述内电子膨胀阀(5)的开度修正系数的乘积，确定为所述内电子膨胀阀(5)的当前开度。
  5. 根据权利要求4所述的空调系统的制热控制装置，其特征在于，所述控制单元，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀(5)的开度修正系数，包括：
    根据所述压缩机频率，确定当前频率区间；
    根据所述室外环境温度，确定当前温度区间；
    根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀(5)的开度修正系数。
  6. 根据权利要求2至5中任一项所述的空调系统的制热控制装置，其特征在于，所述控制单元，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，还包括：
    在根据确定的所述外电子膨胀阀(6)的当前开度对所述外电子膨胀阀(6)进行开度调节之后间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度；
    在根据确定的所述内电子膨胀阀(5)的当前开度对所述内电子膨胀阀(5)进行开度调节之后，间隔设定时长，重新根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，并重新确定所述内电子膨胀阀(5)的当前开度。
  7. 一种空调系统，其特征在于，包括：如权利要求1至6中任一项所述的空调系统的制热控制装置。
  8. 一种空调系统的制热控制方法，其特征在于，所述空调系统的室外换热器包括两排以上微通道换热器，所述两排以上微通道换热器并联设置；在每排所述微通道换热器与所述空调系统的板式换热器(7)之间的管路上，均设置有节流单元；所述空调系统的制热控制方法包括：
    获取所述空调系统的压缩机(1)的吸气温度和压缩机频率，并获取所述空调系统的室外环境温度；
    在制热模式下，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度。
  9. 根据权利要求8所述的空调系统的制热控制方法，其特征在于，所述两排以上微通道换热器，包括：内微通道换热器(3)和外微通道换热器(4)；所述内微通道换热器(3)所对应的节流单元包括内电子膨胀阀(5)，所述外排微通道换热器(4)所对应的节流单元包括外电子膨胀阀(6)；
    其中，所述控制单元，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制所述两排以上微通道换热器中每排所述微通道换热器所对应的节流单元的开度，包括：
    根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度，并根据确定的所述外电子膨胀阀(6)的当前开度调节所述外电子膨胀阀(6)的开度；
    根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，确定所述内电子膨胀阀(5)的当前开度，并根据确定的所述内电子膨胀阀(5)的当前开度调节所述内电子膨胀阀(5)的开度。
  10. 根据权利要求9所述的空调系统的制热控制方法，其特征在于，所述根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度，包括：
    将所述吸气温度与吸气饱和温度之间的温度差值作为吸气过热度，所述吸气饱和温度，是在所述吸气温度下所述压缩机(1)的吸气压力所对应的饱和温度；
    根据所述吸气过热度与目标过热度的差值，确定所述外电子膨胀阀(6)的当前开度。
  11. 根据权利要求9所述的空调系统的制热控制方法，其特征在于，根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，确定所述内电子膨胀阀(5)的当前开度，包括：
    根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀的开度修正系数；
    将所述外电子膨胀阀(6)的当前开度和所述内电子膨胀阀(5)的开度修正系数的乘积，确定为所述内电子膨胀阀(5)的当前开度。
  12. 根据权利要求11所述的空调系统的制热控制方法，其特征在于，根据所述压缩机频率和所述室外环境温度，确定所述内电子膨胀阀(5)的开度修正系数，包括：
    根据所述压缩机频率，确定当前频率区间；
    根据所述室外环境温度，确定当前温度区间；
    根据设定频率区间、设定温度区间与设定修正系数之间的对应关系，将该对应关系中与所述当前频率区间相同的设定频率区间、以及与所述当前温度区间相同的设定温度区间所对应的设定修正系数确定为所述内电子膨胀阀(5)的开度修正系数。
  13. 根据权利要求9至12中任一项所述的空调系统的制热控制方法，其特征在于，根据所述吸气温度、所述压缩机频率和所述室外环境温度，控制两排以上所述微通道换热器中每排所述微通道换热器所对应的节流单元的开度，还包括：
    在根据确定的所述外电子膨胀阀(6)的当前开度对所述外电子膨胀阀(6)进行开度调节之后，间隔设定时长，重新根据所述吸气温度确定所述外电子膨胀阀(6)的当前开度；
    在根据确定的所述内电子膨胀阀(5)的当前开度对所述内电子膨胀阀(5)进行开度调节之后，间隔设定时长，重新根据所述压缩机频率、所述室外环境温度、以及所述外电子膨胀阀(6)的当前开度，并重新确定所述内电子膨胀阀(5)的当前开度。
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