CN114608181B - Control method and device for electronic expansion valve, medium and air source heat pump unit - Google Patents

Control method and device for electronic expansion valve, medium and air source heat pump unit Download PDF

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Publication number
CN114608181B
CN114608181B CN202210304549.4A CN202210304549A CN114608181B CN 114608181 B CN114608181 B CN 114608181B CN 202210304549 A CN202210304549 A CN 202210304549A CN 114608181 B CN114608181 B CN 114608181B
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China
Prior art keywords
expansion valve
electronic expansion
value
opening degree
tth1
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CN202210304549.4A
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CN114608181A (en
Inventor
张宝库
任滔
张义
韩伟涛
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Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
Original Assignee
Qingdao Haier Air Conditioner Gen Corp Ltd
Qingdao Haier Air Conditioning Electric Co Ltd
Haier Smart Home Co Ltd
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Priority to CN202210304549.4A priority Critical patent/CN114608181B/en
Publication of CN114608181A publication Critical patent/CN114608181A/en
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Classifications

    • 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
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F25B41/34—Expansion valves with the valve member being actuated by electric means, e.g. by piezoelectric actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2110/00—Control inputs relating to air properties
    • F24F2110/10—Temperature
    • F24F2110/12—Temperature of the outside air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/10—Pressure
    • F24F2140/12—Heat-exchange fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature

Abstract

The invention relates to the technical field of air source heat pump units, in particular to a control method and device of an electronic expansion valve, a medium and the air source heat pump unit, and aims to solve the problem of how to control the electronic expansion valve to enable a compressor to continuously operate in the highest energy efficiency state. For this purpose, the method of the invention comprises the steps of respectively determining the upper limit value and the lower limit value of the temperature difference between the actual exhaust temperature of the compressor and the target exhaust temperature in the highest energy efficiency state according to the air suction dryness when the unit compressor operates in the highest energy efficiency state, and further increasing or decreasing the opening of the electronic expansion valve according to the comparison result of the temperature difference delta T between the actual exhaust temperature and the target exhaust temperature and the upper limit value and the lower limit value of the temperature difference. Based on the method, the actual air suction dryness of the unit compressor is always in the air suction dryness range when the unit compressor operates in the highest energy efficiency state, so that the unit compressor continuously operates in the highest energy efficiency state, and the unit is ensured to continuously exert the maximum adjusting capacity.

Description

Control method and device for electronic expansion valve, medium and air source heat pump unit
Technical Field
The invention relates to the technical field of air source heat pump units, and particularly provides a control method and device of an electronic expansion valve, a storage medium and an air source heat pump unit.
Background
The electronic expansion valve is used as a key component for air conditioning of the air source heat pump unit, and the opening degree of the electronic expansion valve can have an important influence on the air conditioning capacity of the air source heat pump unit. At present, the opening control method of the electronic expansion valve mainly comprises a method for controlling according to the superheat degree of the heat exchanger and a method for controlling according to the ambient temperature and the water temperature, but the two methods can not enable the air source heat pump unit to continuously exert the maximum air regulating capability under the condition of no-use areas and use.
Accordingly, there is a need in the art for a new electronic expansion valve control scheme to address the above-described problems.
Disclosure of Invention
In order to overcome the above-mentioned drawbacks, the present invention provides a control method and device for an electronic expansion valve, a storage medium and an air source heat pump unit, which solve or at least partially solve the technical problem of how to control the electronic expansion valve to enable a unit compressor of the air source heat pump unit to continuously operate in a most energy efficient state, so that the air source heat pump unit continuously exerts the maximum air conditioning capacity.
In a first aspect, the present invention provides a control method of an electronic expansion valve, applied to an air source heat pump unit, the method comprising:
according to the air suction dryness when the unit compressor operates in the highest energy efficiency state, respectively determining a temperature difference upper limit value Tth1 and a temperature difference lower limit value-Tth 1 of the actual exhaust temperature and the target exhaust temperature when the unit compressor operates in the highest energy efficiency state, wherein Tth >0;
acquiring a temperature difference delta T between the actual exhaust temperature of the unit compressor and the target exhaust temperature;
if the Tth1 is less than or equal to delta T and less than or equal to Tth1, the opening degree of the electronic expansion valve is kept unchanged;
if delta T is larger than Tth1, determining an opening degree increasing value according to the temperature difference value, and gradually increasing the opening degree of the electronic expansion valve according to the opening degree increasing value and the exhaust temperature variation of the unit compressor until the condition that delta T is smaller than or equal to Tth1 is met;
if delta T < -Tth1, determining an opening degree reduction value according to the temperature difference value, and gradually reducing the opening degree of the electronic expansion valve according to the opening degree reduction value and according to the exhaust temperature variation of the unit compressor until the condition that delta T is less than or equal to Tth1 is met; wherein the opening degree increase value and the opening degree decrease value are in positive correlation with the absolute value of the temperature difference value.
In one technical scheme of the control method of the electronic expansion valve, the method further comprises the step of obtaining the target exhaust gas temperature of the unit compressor through the following formula:
Tdcal＝A×Pdd 3 +B×Pdd 2 +C×Pdd+
D×Pss 3 +E×Pss 2 +F×Pss+H
where Tdcal denotes the target discharge temperature of the unit compressor, pdd denotes the high pressure on the refrigerant input side of the condenser in the air source heat pump unit, ps denotes the low pressure on the refrigerant input side of the evaporator in the air source heat pump unit, and A, B, C, D, E, F and H each denote a preset constant coefficient.
In one aspect of the control method of the electronic expansion valve described above, the method further includes calculating the low pressure ps by the following formula:
wherein Tao represents an ambient temperature of an environment where the evaporator is located, ps represents a low pressure actual value of a refrigerant input side of the evaporator, ps_t represents a saturation temperature corresponding to the low pressure actual value Ps, Δt1 represents a first temperature threshold, and M1, N1 and P1 all represent preset constant coefficients;
the method further includes calculating the high pressure Pdd by the following formula:
wherein Two represents the coolant water temperature of the coolant output side of the condenser, pd represents the high pressure actual value of the coolant input side of the condenser, pd_t represents the saturation temperature corresponding to the high pressure actual value, Δt2 represents the second temperature threshold, and M2, N2 and P2 all represent preset constant coefficients.
In one technical scheme of the control method of the electronic expansion valve, if Δt > Tth1, determining an opening increase value according to the temperature difference, and gradually increasing the opening of the electronic expansion valve according to the opening increase value and according to an exhaust temperature variation of the unit compressor until the condition that-tth1 is equal to or less than Δt is equal to or less than Tth1 is satisfied, the method specifically includes:
step S11: increasing the opening of the electronic expansion valve according to the opening increasing value;
step S12: judging whether the temperature difference value delta T after increasing the opening degree meets the condition that delta T is less than or equal to Tth1 and less than or equal to Tth 1;
if yes, maintaining the current opening of the electronic expansion valve unchanged;
if not, go to step S13;
step S13: obtaining exhaust temperature variation DeltaTd of unit compressor after increasing opening degree 1 Comparing the exhaust temperature variation Δtd 1 And a first variation threshold DeltaTd 1 th；
If |DeltaTd 1 |≥|ΔTd 1 th|, increasing the opening of the electronic expansion valve according to the opening increasing value again after delaying the first time period, and then turning to step S12;
if 0 is<|ΔTd 1 |<|ΔTd 1 th| delayAfter a second period of time, increasing the opening of the electronic expansion valve again according to the opening increasing value, and then turning to step S12;
wherein the second duration is less than the first duration.
In one aspect of the control method of the electronic expansion valve described above, the method further includes determining the opening degree increase value by:
if Tth1<ΔT is less than or equal to Tth2, the opening degree increase value is O 1 And O is 1 >0, tth2 represents a temperature difference threshold and Tth2>Tth1>0；
If DeltaT>Tth2, the opening degree increase value is 2O 1 。
In one technical scheme of the control method of the electronic expansion valve, if Δt < -Tth1, determining an opening degree reduction value according to the temperature difference, and gradually reducing the opening degree of the electronic expansion valve according to the opening degree reduction value and according to the exhaust temperature variation of the unit compressor until the condition that Δt1 is less than or equal to Δt is less than or equal to Tth1 is satisfied, the method specifically includes:
step S21: reducing the opening of the electronic expansion valve according to the opening reduction value;
step S22: judging whether the temperature difference value delta T after the opening degree is reduced meets the condition that delta T is less than or equal to Tth1 and less than or equal to Tth 1;
if yes, maintaining the current opening of the electronic expansion valve unchanged;
if not, go to step S23;
step S23: obtaining exhaust temperature variation DeltaTd of unit compressor after opening degree is reduced 2 Comparing the exhaust temperature variation Δtd 2 And a second variation threshold DeltaTd 2 th；
If |DeltaTd 2 |≥|ΔTd 2 th|, reducing the opening of the electronic expansion valve according to the opening reduction value again after delaying the third time period, and then turning to step S22;
if 0 is<|ΔTd 2 |<|ΔTd 2 th, delaying the fourth time period, and then carrying out opening degree of the electronic expansion valve according to the opening degree reduction value againDecrease, then go to step S22;
wherein the fourth duration is less than the third duration.
In one aspect of the control method of the electronic expansion valve described above, the method further includes determining the opening degree reduction value by:
if-Tth 2 is less than or equal to DeltaT is less than or equal to-Tth 1, the opening degree reduction value is O 2 And O is 2 >0, tth2 represents a temperature difference threshold and Tth2>Tth1>0；
If DeltaT<-Tth2, the opening degree reduction value is 2O 2 。
In a second aspect, a control device is provided, which comprises a processor and a storage device, the storage device being adapted to store a plurality of program codes, the program codes being adapted to be loaded and executed by the processor to perform the control method of the electronic expansion valve as set forth in any one of the technical aspects of the control method of the electronic expansion valve.
In a third aspect, a computer readable storage medium is provided, in which a plurality of program codes are stored, the program codes being adapted to be loaded and executed by a processor to perform the control method of an electronic expansion valve as set forth in any one of the above-mentioned technical aspects of the control method of an electronic expansion valve.
In a fourth aspect, an air source heat pump unit is provided, where the air source heat pump unit includes a control device for an electronic expansion valve according to the above-mentioned technical scheme of the control device for the electronic expansion valve.
The technical scheme provided by the invention has at least one or more of the following beneficial effects:
as will be appreciated by those skilled in the art, an air source heat pump unit generally includes an indoor unit including an indoor heat exchanger and an indoor electronic expansion valve, and an outdoor unit including an outdoor heat exchanger, an outdoor electronic expansion valve, and a compressor. As shown in fig. 1, the low-temperature low-pressure liquid refrigerant output by the indoor electronic expansion valve flows into the outdoor heat exchanger for evaporation heat exchange during heating of the air source heat pump unit (the outdoor heat exchanger is an evaporator during heating of the air source heat pump unit, the indoor heat exchanger is a condenser), and the outdoor heat exchanger outputs the low-temperature low-pressure gaseous refrigerant to the compressor. As shown in fig. 2, the low-temperature low-pressure liquid refrigerant output by the outdoor electronic expansion valve flows into the indoor heat exchanger for evaporation heat exchange when the air source heat pump unit is in refrigeration (the indoor heat exchanger is an evaporator when the air source heat pump unit is in refrigeration, and the outdoor heat exchanger is a condenser), and the indoor heat exchanger outputs the low-temperature low-pressure gaseous refrigerant to the compressor. According to fig. 1 and 2, it can be determined that, no matter heating or cooling of the air source heat pump unit, the evaporator (outdoor or indoor heat exchanger) can perform evaporation heat exchange on the low-temperature low-pressure liquid refrigerant output by the electronic expansion valve (indoor or outdoor electronic expansion valve), and then the low-temperature low-pressure gaseous refrigerant after heat exchange is output to the compressor. Because the heat exchange area of the evaporator is fixed, if excessive refrigerant enters the evaporator, a part of refrigerant can not be completely evaporated, and the evaporator can output a part of liquid refrigerant, so that the refrigerant dryness of the refrigerant output by the evaporator is reduced, and therefore, the flow of the low-temperature low-pressure liquid refrigerant output by the electronic expansion valve can influence the refrigerant dryness of the low-temperature low-pressure liquid refrigerant output by the evaporator, namely, the air suction dryness of the compressor. Specifically, the larger the flow rate of the low-temperature low-pressure liquid refrigerant is, the smaller the suction dryness is; the smaller the flow rate of the low-temperature low-pressure liquid refrigerant is, the larger the suction dryness is. It can be seen that the suction dryness of the compressor can be changed by adjusting the opening of the electronic expansion valve.
In the technical scheme of implementing the invention, the control method of the electronic expansion valve can respectively determine the upper temperature difference value Tth1 and the lower temperature difference value-Tth 1 of the actual exhaust temperature and the target exhaust temperature when the unit compressor operates in the highest energy efficiency state according to the air suction dryness when the unit compressor operates in the highest energy efficiency state, and then adjusts (increases or reduces) the opening of the electronic expansion valve in different modes according to the comparison result of the temperature difference value delta T of the actual exhaust temperature and the target exhaust temperature, the upper temperature difference value Tth1 and the lower temperature difference value-Tth 1. By the method, the actual air suction dryness of the unit compressor is always in the air suction dryness range (for simplicity in description, hereinafter referred to as the high-energy efficiency range) when the unit compressor operates in the highest energy efficiency state, so that the unit compressor continuously operates in the highest energy efficiency state, and the air source heat pump unit is ensured to continuously exert the maximum air conditioning capacity (refrigerating or heating capacity).
Specifically, if-Tth 1 is less than or equal to DeltaT and less than or equal to Tth1, the actual air suction dryness of the unit compressor is in a high energy efficiency range, the opening of the electronic expansion valve is not required to be regulated, and the opening of the electronic expansion valve is maintained unchanged.
If DeltaT > Tth1, the actual air suction dryness of the unit compressor is larger than the maximum value of the high-energy efficiency range, and the air suction dryness of the compressor can be reduced by increasing the opening of the electronic expansion valve, so that the unit compressor is operated in the highest-energy efficiency state. Specifically, the opening degree increasing value may be determined according to the temperature difference Δt, and the opening degree of the electronic expansion valve may be gradually increased according to the opening degree increasing value and according to the exhaust temperature variation amount of the unit compressor until the condition that-tth1 is equal to or less than Δt equal to or less than Tth1 is satisfied. The opening degree increase value and the absolute value of the temperature difference Δt are in positive correlation (the larger the absolute value of the temperature difference Δt is, the larger the opening degree increase value is, whereas the smaller the opening degree increase value is). The opening of the electronic expansion valve is gradually increased according to the exhaust temperature variation of the unit compressor, so that the problem that the compressor cannot be operated in the highest energy efficiency state rapidly and stably due to too high adjustment speed can be avoided.
If DeltaT < -Tth1 shows that the actual air suction dryness of the unit compressor is smaller than the minimum value of the high-energy efficiency range, the air suction dryness of the compressor can be improved by reducing the opening of the electronic expansion valve, and the unit compressor is operated in the highest-energy efficiency state. Specifically, an opening degree reduction value is determined according to the temperature difference value delta T, and the opening degree of the electronic expansion valve is gradually reduced according to the opening degree reduction value and according to the exhaust temperature variation of the unit compressor until the condition that-Tth 1 is less than or equal to delta T is less than or equal to Tth1 is satisfied. The opening degree decrease value has a positive correlation with the absolute value of the temperature difference Δt (the larger the absolute value of the temperature difference Δt, the larger the opening degree decrease value, and conversely, the smaller the opening degree decrease value). The opening degree of the electronic expansion valve is gradually reduced according to the exhaust temperature variation of the unit compressor, so that the problem that the compressor cannot be operated in the highest energy efficiency state rapidly and stably due to too high adjustment speed can be avoided.
Drawings
The present disclosure will become more readily understood with reference to the accompanying drawings. As will be readily appreciated by those skilled in the art: the drawings are for illustrative purposes only and are not intended to limit the scope of the present invention. Wherein:
FIG. 1 is a schematic diagram of a refrigerant flow path during heating of an air source heat pump unit;
FIG. 2 is a schematic diagram of a refrigerant flow path during cooling of an air source heat pump unit;
FIG. 3 is a flow chart of the main steps of a control method of an electronic expansion valve according to an embodiment of the present invention;
FIG. 4 is a flow chart of the main steps of a method for increasing the opening of an electronic expansion valve according to one embodiment of the present invention;
fig. 5 is a flow chart illustrating main steps of a method for reducing the opening of an electronic expansion valve according to an embodiment of the present invention.
Detailed Description
Some embodiments of the invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are merely for explaining the technical principles of the present invention, and are not intended to limit the scope of the present invention.
In the description of the present invention, a "processor" may include hardware, software, or a combination of both. The processor may be a central processor, a microprocessor, a digital signal processor, or any other suitable processor. The processor has data and/or signal processing functions. The processor may be implemented in software, hardware, or a combination of both.
Referring to fig. 3, fig. 3 is a schematic flow chart of main steps of a control method of an electronic expansion valve applied to an air source heat pump unit according to an embodiment of the present invention. As shown in fig. 3, the control method of the electronic expansion valve in the embodiment of the invention mainly includes the following steps S101 to S106.
Step S101: and respectively determining a temperature difference upper limit value Tth1 and a temperature difference lower limit value-Tth 1, tth >0 of the actual exhaust temperature and the target exhaust temperature when the unit compressor operates in the highest energy efficiency state according to the air suction dryness when the unit compressor operates in the highest energy efficiency state.
In this embodiment, the temperature difference upper limit value Tth1 and the temperature difference lower limit value-Tth 1 may be determined according to the maximum value and the minimum value of the suction dryness range (hereinafter, simply referred to as the high energy efficiency range for brevity of description) when the unit compressor is operated in the highest energy efficiency state. Specifically, if the temperature difference ΔT between the actual exhaust gas temperature and the target exhaust gas temperature satisfies the condition that ΔTt1 is equal to or less than ΔT is equal to or less than Tth1, then the actual suction dryness of the unit compressor is determined to be within the high energy efficiency range. If the temperature difference DeltaT meets the condition that DeltaT > Tth1, the actual suction dryness of the compressor of the unit is determined to be larger than the maximum value of the high energy efficiency range. If the temperature difference delta T meets the condition of delta T < -Tth1, determining that the actual suction dryness of the compressor of the unit is smaller than the minimum value of the high-energy efficiency range.
In some embodiments, the range of air intake dryness when the unit compressor is operated in the most energy efficient state is 0.95 to 0.98, and the upper temperature difference value Tth1=2 ℃ and the lower temperature difference value-Tth1= -2 ℃ are determined according to the range of air intake dryness.
Step S102: a temperature difference deltat between the actual discharge temperature of the unit compressor and the target discharge temperature is obtained.
Step S103: the temperature difference Δt, the temperature difference upper limit value Tth1, and the temperature difference lower limit value-Tth 1 are compared.
If Δt > Tth1, it indicates that the actual air intake dryness of the unit compressor is greater than the maximum value of the high energy efficiency range, at this time, the air intake dryness of the compressor may be reduced by increasing the opening of the electronic expansion valve, so that the unit compressor is operated in the highest energy efficiency state, that is, the step S104 is performed.
if-Tth 1 is less than or equal to DeltaT is less than or equal to Tth1, the actual air suction dryness of the unit compressor is in a high energy efficiency range, the opening of the electronic expansion valve is not required to be regulated, and the opening of the electronic expansion valve is maintained unchanged, namely, the step S105 is performed.
If DeltaT < -Tth1 indicates that the actual air suction dryness of the unit compressor is smaller than the minimum value of the high-energy efficiency range, the air suction dryness of the compressor can be improved by reducing the opening of the electronic expansion valve, so that the unit compressor is operated in the highest-energy efficiency state, namely, the step S106 is performed.
Step S104: and determining an opening degree increasing value according to the temperature difference, and gradually increasing the opening degree of the electronic expansion valve according to the opening degree increasing value and the exhaust temperature variation of the unit compressor until the condition that Tth1 is less than or equal to delta T is less than or equal to Tth1 is met.
The opening degree increase value and the absolute value of the temperature difference value are in positive correlation, namely, the opening degree increase value is larger as the absolute value of the temperature difference value is larger, and the opening degree increase value is smaller as the absolute value of the temperature difference value is smaller.
Step S105: the opening degree of the electronic expansion valve is kept unchanged.
Step S106: determining an opening degree reduction value according to the temperature difference, and gradually reducing the opening degree of the electronic expansion valve according to the opening degree reduction value and the exhaust temperature variation of the unit compressor until the condition that-Tth 1 is less than or equal to delta T is less than or equal to Tth1 is met.
The opening degree decrease value and the absolute value of the temperature difference value are in positive correlation, namely, the larger the absolute value of the temperature difference value is, the larger the opening degree decrease value is, and the smaller the absolute value of the temperature difference value is, the smaller the opening degree decrease value is.
Based on the methods described in the steps S101 to S106, the actual air intake dryness of the unit compressor can be always in the air intake dryness range when the unit compressor is operated in the highest energy efficiency state under the condition of no use and use, so that the unit compressor is continuously operated in the highest energy efficiency state, and the unit can be ensured to continuously exert the maximum adjusting capability. In addition, according to the exhaust temperature variation of the unit compressor, the opening degree of the electronic expansion valve is gradually increased or reduced, so that the problem that the compressor cannot be quickly and stably operated in the highest energy efficiency state due to too high adjustment speed can be avoided.
The following describes the above steps S102, S104 and S106 in detail.
In one embodiment of the above step S102, the target discharge temperature of the unit compressor may be determined according to the pressure of the refrigerant input side of the evaporator and the condenser in the air source heat pump unit at the same time. Specifically, in the present embodiment, the target discharge gas temperature Tdcal of the unit compressor may be obtained by the following equation (1).
Tdcal＝A×Pdd 3 +B×Pdd 2 +C×Pdd+D×Pss 3 +E×Pss 2 +F×Pss+H (1)
The meaning of each parameter in the formula (1) is as follows:
pdd the high pressure on the refrigerant input side of the condenser in the air-source heat pump unit, ps the low pressure on the refrigerant input side of the evaporator in the air-source heat pump unit, A, B, C, D, E, F and H each represent a preset constant coefficient.
The outdoor heat exchanger is an evaporator when the air source heat pump unit heats, the indoor heat exchanger is a condenser, and the indoor heat exchanger is an evaporator when the air source heat pump unit refrigerates, and the outdoor heat exchanger is a condenser. According to the refrigerant flow paths shown in fig. 1 and 2, whether the air source heat pump unit heats or cools, the low-temperature low-pressure liquid refrigerant is input to the refrigerant input side of the evaporator, and the high-temperature high-pressure gas refrigerant is input to the refrigerant input side of the condenser. Therefore, the low pressure of the low pressure refrigerant at the refrigerant input side of the evaporator and the high pressure of the high pressure refrigerant at the refrigerant input side of the condenser can be obtained regardless of heating or cooling of the air source heat pump unit, and the target discharge temperature Tdcal can be obtained by substituting the above formula (1).
In this embodiment, the air source heat pump unit may be tested to obtain a plurality of sets of test data, each set of test data including the target exhaust gas temperature Tdcal, the high pressure Pdd, and the low pressure Pss. Then, polynomial fitting is performed on the multiple sets of test data by using the target exhaust temperature Tdcal as a dependent variable and simultaneously using the high pressure Pdd and the low pressure Pss as independent variables, so as to obtain a calculation formula of the target exhaust temperature Tdcal shown in the formula (1), and the preset constant coefficients A, B, C, D, E, F and H are coefficients obtained after polynomial fitting.
Further, in the embodiment of the present invention, the low pressure Pss may be calculated according to the temperature of the evaporator and the ambient temperature, in addition to the actual low pressure value of the refrigerant input side of the evaporator being directly used as the low pressure Pss.
Specifically, in one embodiment, the low pressure Pss of the refrigerant input side of the evaporator can be calculated by the following equation (2).
The meaning of each parameter in the formula (2) is as follows:
tao represents the ambient temperature of the environment in which the evaporator is located, ps represents the actual low pressure value of the refrigerant input side of the evaporator, ps_t represents the saturation temperature corresponding to the actual low pressure value Ps, Δt1 represents the first temperature threshold, and M1, N1 and P1 each represent a preset constant coefficient.
According to the formula (2), when the difference between the ambient temperature Tao and the saturation temperature ps_t is greater than or equal to the first temperature threshold Δt1, calculating the low pressure Ps according to the ambient temperature Tao and the saturation temperature ps_t; when the difference between the ambient temperature Tao and the saturation temperature ps_t is smaller than the first temperature threshold Δt1, the low-pressure actual value Ps of the refrigerant input side of the evaporator is directly used as the low-pressure Pss.
In this embodiment, a table lookup method may be used to query the data sets preset with the correspondence between different saturation temperatures and different low pressure pressures, so as to obtain the saturation temperature corresponding to the actual low pressure value Ps. In addition, in the present embodiment, the air source heat pump unit may be tested to obtain a plurality of sets of test data, each set of test data including the low pressure ps and the difference (Tao- Δt1) between the ambient temperature Tao and the first temperature threshold Δt1. Then, the calculation formula pss=m1× (Tao- Δt1) in the above formula (2) can be obtained by performing polynomial fitting on the plurality of sets of test data using the low pressure Pss as a dependent variable and the difference (Tao- Δt1) as an independent variable 2 +n1× (Tao- Δt1) +p1, and the preset constant coefficients M1, N1 and P1 are coefficients obtained after polynomial fitting.
Further, in the embodiment of the present invention, the actual high pressure value of the refrigerant input side of the condenser may be directly used as the high pressure Pdd, and the high pressure Pdd may be calculated according to the temperature of the condenser.
Specifically, in one embodiment, the high pressure Pdd on the refrigerant input side of the condenser can be calculated by the following equation (3).
The meaning of each parameter in the formula (3) is as follows:
two represents the coolant water temperature at the coolant output side of the condenser, pd represents the actual high pressure value at the coolant input side of the condenser, pd—t represents the saturation temperature corresponding to the actual high pressure value, Δt2 represents the second temperature threshold, and M2, N2, and P2 each represent a preset constant coefficient.
According to the formula (3), when the difference between the temperature Two and the saturation temperature pd_t is greater than or equal to the second temperature threshold Δt2, calculating the high pressure Pdd according to the temperature Two and the saturation temperature pd_t; when the difference between the temperature Two and the saturation temperature pd_t is smaller than the second temperature threshold Δt2, the high-pressure actual value Pd on the refrigerant input side of the condenser is directly used as the high-pressure Pdd.
In this embodiment, a table lookup method may be used to query the data sets preset with the correspondence between different saturation temperatures and different high-pressure pressures, so as to obtain the saturation temperature corresponding to the actual high-pressure value Pd. In addition, in the present embodiment, the air source heat pump unit may be tested to obtain a plurality of sets of test data, each set of test data including the high pressure Pdd and the sum (two+Δt2) of the temperature Two and the second temperature threshold Δt2. Then, the polynomial fitting is performed on the plurality of sets of test data using the high pressure Pdd as a dependent variable and the sum (two+Δt2) as an independent variable, thereby obtaining a calculation equation Pdd =m2× (two+Δt2) in the above formula (3) 2 +N2× (two+ΔT2) +P2, two-Pd_t is greater than or equal to ΔT2, and the predetermined constant coefficients M2, N2 and P2 are the coefficients obtained after polynomial fitting.
The above is a specific description of step S102, and the following continues to describe step S104 and step S106.
Referring to fig. 4, in an embodiment of the above step S104, in the case where Δt > Tth1, the opening degree of the electronic expansion valve may be gradually increased by the method described in the following steps S201 to S206 until the condition that-Tth 1 is equal to or less than Δt is equal to or less than Tth1 is satisfied.
Step S201: the opening degree of the electronic expansion valve is increased according to the opening degree increasing value.
Step S202: judging whether the temperature difference value delta T after the opening degree is increased meets the condition that delta T is less than or equal to Tth1 and is less than or equal to Tth1.
If yes, go to step S203; if not, go to step S204.
Step S203: the current opening degree of the electronic expansion valve is maintained unchanged.
Step S204: obtaining exhaust temperature variation DeltaTd of unit compressor after increasing opening degree 1 Comparing the exhaust temperature variation Δtd 1 And a first variation threshold DeltaTd 1 th。
If the exhaust temperature variation ΔTd 1 Satisfy |DeltaTd 1 |≥|ΔTd 1 th| then go to step S205; if the exhaust temperature variation ΔTd 1 Satisfy 0<|ΔTd 1 |<|ΔTd 1 th|, the process proceeds to step S206.
Step S205: after the first period of time is delayed, the opening degree of the electronic expansion valve is increased again according to the opening degree increasing value, and then the process goes to step S202.
Step S206: and after the second time period is delayed, the opening of the electronic expansion valve is increased again according to the opening increasing value, and then the step S202 is carried out, wherein the second time period is smaller than the first time period.
Further, according to the foregoing embodiment, the opening degree increase value is in positive correlation with the absolute value of the temperature difference value, that is, the larger the absolute value of the temperature difference value is, the larger the opening degree increase value is, and the smaller the absolute value of the temperature difference value is, the smaller the opening degree increase value is. In a preferred embodiment, when DeltaT>Tth1 may be used to determine whether ΔT is further greater than a temperature difference threshold Tth2 (Tth 2>Tth1>0) If Tth1<If DeltaT is less than or equal to Tth2, the opening degree is increasedThe value is set to O 1 And O is 1 >0, if DeltaT>Tth2 sets the opening degree increase value to 2O 1 。
In one example, the range of air intake dryness when the unit compressor is operating in the most energy efficient state is 0.95 to 0.98, the upper temperature difference value tth1=2 ℃, the temperature difference threshold value tth2=5 ℃, the first variation threshold value Δtd 1 th=3 ℃, the first time period is 2min, and the second time period is 1min. When the temperature is 2 DEG C<When delta T is less than or equal to 5 ℃, the actual air suction dryness of the unit compressor is judged to be between 0.98 and 1, and when delta T is less than or equal to 5 DEG C>And judging that the actual air suction dryness of the compressor of the unit reaches 1 at the temperature of 5 ℃.
When the temperature is 2 DEG C<Increasing the value O according to the opening degree when the delta T is less than or equal to 5 DEG C 1 Increasing the opening of the electronic expansion valve, and if the opening is increased, changing the exhaust gas temperature by an amount DeltaTd 1 The temperature difference delta T is not smaller than minus 2 ℃ and is larger than or equal to 3 ℃ and is smaller than or equal to 2 ℃ below zero, the opening degree is increased by the value O after delaying for 2min 1 The opening degree of the electronic expansion valve is increased. If the exhaust gas temperature variation after the opening degree is increased for the 2 nd time is 0 DEG C<ΔTd 1 <The temperature difference delta T at 3 ℃ still does not meet the condition that delta T is less than or equal to minus 2 ℃ and less than or equal to 2 ℃, and the opening degree is increased by the value O after delaying for 1min 1 The opening degree of the electronic expansion valve is increased.
When DeltaT>Increasing the value by 2O according to the opening at 5 DEG C 1 Increasing the opening of the electronic expansion valve, and if the opening is increased, changing the exhaust gas temperature by an amount DeltaTd 1 The temperature difference delta T is less than or equal to minus 3 ℃ and less than or equal to minus 2 ℃ and less than or equal to 2 ℃, and the opening is increased by 2O after delaying for 2min 1 The opening degree of the electronic expansion valve is increased. If the exhaust temperature variation after the opening degree is increased for the 2 nd time is-3 DEG C<ΔTd 1 <The temperature difference delta T still does not meet the condition that delta T is less than or equal to minus 2 ℃ and less than or equal to 2 ℃ at the temperature of 0 ℃, and the opening is increased by 2O after delaying for 1min 1 The opening degree of the electronic expansion valve is increased.
The above is a specific description of step S104, and the following continues to describe step S106.
Referring to fig. 5, in an embodiment of the above step S106, in the case of Δt < -Tth1, the opening degree of the electronic expansion valve may be gradually reduced by the method described in the following steps S301 to S306 until the condition that-Tth 1 is equal to or less than Δt equal to or less than Tth1 is satisfied.
Step S301: the opening degree of the electronic expansion valve is reduced according to the opening degree reduction value.
Step S302: judging whether the temperature difference value delta T meets the condition that the delta T is less than or equal to minus Tth1.
If the condition is satisfied, go to step S303; if the condition is not satisfied, the process goes to step S304.
Step S303: the current opening degree of the electronic expansion valve is maintained unchanged.
Step S304: obtaining exhaust temperature variation DeltaTd of unit compressor after opening degree is reduced 2 Comparing the exhaust temperature variation Δtd 2 And a second variation threshold DeltaTd 2 th。
If the exhaust temperature variation ΔTd 2 Satisfy |DeltaTd 2 |≥|ΔTd 2 th| then go to step S305; if the exhaust temperature variation ΔTd 2 Satisfy 0<|ΔTd 2 |<|ΔTd 2 th|, the process proceeds to step S306.
Step S305: and after the third time period is delayed, the opening degree of the electronic expansion valve is reduced again according to the opening degree reduction value, and then the step S302 is carried out.
Step S306: and reducing the opening of the electronic expansion valve according to the opening reduction value again after delaying the fourth time period, and then turning to the step S302, wherein the fourth time period is smaller than the third time period.
Further, according to the foregoing embodiment, the opening degree decrease value is in positive correlation with the absolute value of the temperature difference value, that is, the larger the absolute value of the temperature difference value is, the larger the opening degree decrease value is, and the smaller the absolute value of the temperature difference value is, the smaller the opening degree decrease value is. In a preferred embodiment, when DeltaT<-Tth1 can be used to determine if Δt is further smaller than the temperature difference threshold value-Tth 2 (Tth 2>Tth1>0) Setting the opening degree reduction value to O if-Tth 2 is equal to or less than deltaT is equal to or less than-Tth 1 2 And O is 2 >0, if DeltaT<Tth2 sets the opening degree reduction value to 2O 2 。
In one example, the unit compressor is operated at a maximum energy efficiency stateThe air intake dryness ranges from 0.95 to 0.98, the temperature difference lower limit value-Tth 1= -2 ℃, the temperature difference threshold value-Tth 2= -5 ℃, and the second variation threshold value delta Td 2 th=3 ℃, the third time period is 2min, and the fourth time period is 1min. When delta T is less than or equal to minus 5 ℃ and less than or equal to minus 2 ℃, the actual air suction dryness of the unit compressor is judged to be between 0.90 and 0.95, and when delta T is less than or equal to minus 2 DEG C<And judging that the actual air suction dryness of the compressor of the unit is less than 0.90 at the temperature of minus 5 ℃.
When the temperature is less than or equal to minus 5 ℃ and delta T<According to opening degree reduction value O at-2 DEG C 2 Reducing the opening of the electronic expansion valve, and if the opening is reduced, changing the exhaust temperature delta Td 2 Not less than 3 ℃ and the temperature difference delta T not meeting the condition that delta T is not less than minus 2 ℃ and not more than 2 ℃, delaying for 2 minutes and then reducing the value O according to the opening 2 The opening degree of the electronic expansion valve is reduced. If the exhaust gas temperature variation after the opening degree is reduced for the 2 nd time is 0 DEG C<ΔTd 2 <The temperature difference delta T at 3 ℃ still does not meet the condition that delta T is less than or equal to minus 2 ℃ and less than or equal to 2 ℃, and the opening degree is reduced by O after delaying for 1min 2 The opening degree of the electronic expansion valve is reduced.
When DeltaT<According to opening degree reduction value 2O at-5 DEG C 2 Reducing the opening of the electronic expansion valve, and if the opening is reduced, changing the exhaust temperature delta Td 2 The temperature difference delta T is less than or equal to minus 3 ℃ and does not meet the condition that delta T is less than or equal to minus 2 ℃ and less than or equal to 2 ℃, and the opening is reduced by 2O after delaying for 2min 2 The opening degree of the electronic expansion valve is reduced. If the exhaust gas temperature variation after the opening degree is reduced for the 2 nd time is-3 DEG C<ΔTd 2 <The temperature difference delta T still does not meet the condition that delta T is less than or equal to minus 2 ℃ and less than or equal to minus 2 ℃ at 0 ℃, and the opening is reduced by 2O after delaying for 1min 2 The opening degree of the electronic expansion valve is reduced.
It should be noted that, although the foregoing embodiments describe the steps in a specific order, it will be understood by those skilled in the art that, in order to achieve the effects of the present invention, the steps are not necessarily performed in such an order, and may be performed simultaneously (in parallel) or in other orders, and these variations are within the scope of the present invention.
It will be appreciated by those skilled in the art that the present invention may implement all or part of the above-described methods according to the above-described embodiments, or may be implemented by means of a computer program for instructing relevant hardware, where the computer program may be stored in a computer readable storage medium, and where the computer program may implement the steps of the above-described embodiments of the method when executed by a processor. Wherein the computer program comprises computer program code which may be in source code form, object code form, executable file or some intermediate form etc. The computer readable storage medium may include: any entity or device, medium, usb disk, removable hard disk, magnetic disk, optical disk, computer memory, read-only memory, random access memory, electrical carrier wave signals, telecommunications signals, software distribution media, and the like capable of carrying the computer program code. It should be noted that the computer readable storage medium may include content that is subject to appropriate increases and decreases as required by jurisdictions and by jurisdictions in which such computer readable storage medium does not include electrical carrier signals and telecommunications signals.
The invention further provides a control device of the electronic expansion valve. In a control device embodiment of an electronic expansion valve according to the present invention, the control device of the electronic expansion valve includes a processor and a storage device, the storage device may be configured to store a program for executing the control method of the electronic expansion valve of the above-described method embodiment, and the processor may be configured to execute the program in the storage device, including, but not limited to, the program for executing the control method of the electronic expansion valve of the above-described method embodiment. For convenience of explanation, only those portions of the embodiments of the present invention that are relevant to the embodiments of the present invention are shown, and specific technical details are not disclosed, please refer to the method portions of the embodiments of the present invention. The control means of the electronic expansion valve may be a control means device formed by including various electronic devices.
Further, the invention also provides a computer readable storage medium. In one embodiment of the computer readable storage medium according to the present invention, the computer readable storage medium may be configured to store a program for executing the control method of the electronic expansion valve of the above-described method embodiment, which may be loaded and executed by a processor to implement the control method of the electronic expansion valve described above. For convenience of explanation, only those portions of the embodiments of the present invention that are relevant to the embodiments of the present invention are shown, and specific technical details are not disclosed, please refer to the method portions of the embodiments of the present invention. The computer readable storage medium may be a storage device including various electronic devices, and optionally, the computer readable storage medium in the embodiments of the present invention is a non-transitory computer readable storage medium.
Further, the invention also provides an air source heat pump unit. In an embodiment of the air source heat pump unit according to the invention, the air source heat pump unit may comprise control means of the electronic expansion valve according to the previous embodiment of the device. For convenience of explanation, only those parts related to the embodiments of the present invention are shown, and specific technical details are not disclosed, please refer to the device parts of the embodiments of the present invention.
Thus far, the technical solution of the present invention has been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of protection of the present invention is not limited to these specific embodiments. Equivalent modifications and substitutions for related technical features may be made by those skilled in the art without departing from the principles of the present invention, and such modifications and substitutions will fall within the scope of the present invention.

Claims (8)

1. A control method of an electronic expansion valve, characterized by being applied to an air source heat pump unit, the method comprising:
according to the air suction dryness when the unit compressor operates in the highest energy efficiency state, respectively determining a temperature difference upper limit value Tth1 and a temperature difference lower limit value-Tth 1 of the actual exhaust temperature and the target exhaust temperature when the unit compressor operates in the highest energy efficiency state, wherein Tth >0;
acquiring a temperature difference delta T between the actual exhaust temperature of the unit compressor and the target exhaust temperature;
if the Tth1 is less than or equal to delta T and less than or equal to Tth1, the opening degree of the electronic expansion valve is kept unchanged;
if delta T is larger than Tth1, determining an opening degree increasing value according to the temperature difference value, and gradually increasing the opening degree of the electronic expansion valve according to the opening degree increasing value and the exhaust temperature variation of the unit compressor until the condition that delta T is smaller than or equal to Tth1 is met;
if delta T < -Tth1, determining an opening degree reduction value according to the temperature difference value, and gradually reducing the opening degree of the electronic expansion valve according to the opening degree reduction value and according to the exhaust temperature variation of the unit compressor until the condition that delta T is less than or equal to Tth1 is met; wherein the opening degree increasing value and the opening degree decreasing value are in positive correlation with the absolute value of the temperature difference value;
the target exhaust temperature of the unit compressor is obtained by the following formula: tdcal=a× Pdd 3 +B×Pdd 2 +C×Pdd+D×Pss 3 +E×Pss 2 +F×Pss+H
Tdcal denotes a target discharge temperature of a unit compressor, pdd denotes a high pressure of a refrigerant input side of a condenser in the air source heat pump unit, ps denotes a low pressure of a refrigerant input side of an evaporator in the air source heat pump unit, and A, B, C, D, E, F and H each denote a preset constant coefficient;
the low pressure Pss is calculated by the following formula:
tao represents the ambient temperature of the environment where the evaporator is located, ps represents the actual low pressure value of the refrigerant input side of the evaporator, ps_t represents the saturated temperature corresponding to the actual low pressure value Ps, Δt1 represents the first temperature threshold, and M1, N1 and P1 all represent preset constant coefficients;
the high pressure Pdd is calculated by the following formula:
two represents the coolant water temperature of the coolant output side of the condenser, pd represents the high-pressure actual value of the coolant input side of the condenser, pd_t represents the saturation temperature corresponding to the high-pressure actual value, deltaT 2 represents the second temperature threshold, and M2, N2 and P2 all represent preset constant coefficients;
when the air source heat pump unit heats, the condenser and the evaporator are respectively an indoor heat exchanger and an outdoor heat exchanger, and the electronic expansion valve is an indoor electronic expansion valve; when the air source heat pump unit is used for refrigerating, the condenser and the evaporator are respectively an outdoor heat exchanger and an indoor heat exchanger, and the electronic expansion valve is an outdoor electronic expansion valve.
2. The control method of an electronic expansion valve according to claim 1, wherein the step of determining an opening degree increase value based on the temperature difference value if Δt > Tth1, and gradually increasing the opening degree of the electronic expansion valve according to the opening degree increase value and according to an exhaust temperature variation amount of the set compressor until the condition that-Tth 1 is equal to or less than Δt is equal to or less than Tth1 is satisfied specifically includes:
step S11: increasing the opening of the electronic expansion valve according to the opening increasing value;
step S12: judging whether the temperature difference value delta T after increasing the opening degree meets the condition that delta T is less than or equal to Tth1 and less than or equal to Tth 1;
if yes, maintaining the current opening of the electronic expansion valve unchanged;
if not, go to step S13;
step S13: obtaining exhaust temperature variation DeltaTd of unit compressor after increasing opening degree 1 Comparing the exhaust temperature variation Δtd 1 And a first variation threshold DeltaTd 1 th；
If |DeltaTd 1 |≥|ΔTd 1 th|, increasing the opening of the electronic expansion valve according to the opening increasing value again after delaying the first time period, and then turning to step S12;
if 0 is<|ΔTd 1 |<|ΔTd 1 th|, delaying the second time period and then performing the electronic expansion valve according to the opening degree increasing valueThe opening degree is increased, and then the process proceeds to step S12;
wherein the second duration is less than the first duration.
3. The control method of an electronic expansion valve according to claim 2, characterized in that the method further comprises determining the opening degree increase value by:
if Tth1<ΔT is less than or equal to Tth2, the opening degree increase value is O 1 And O is 1 >0, tth2 represents a temperature difference threshold and Tth2>Tth1>0；
If DeltaT>Tth2, the opening degree increase value is 2O 1 。
4. The control method of an electronic expansion valve according to claim 1, wherein the step of determining an opening degree reduction value from the temperature difference value if Δt < -Tth1, and gradually reducing the opening degree of the electronic expansion valve according to the opening degree reduction value and according to an exhaust temperature variation amount of a unit compressor until a condition that Δt is equal to or less than-Tth 1 is satisfied, specifically comprises:
step S21: reducing the opening of the electronic expansion valve according to the opening reduction value;
step S22: judging whether the temperature difference value delta T after the opening degree is reduced meets the condition that delta T is less than or equal to Tth1 and less than or equal to Tth 1;
if yes, maintaining the current opening of the electronic expansion valve unchanged;
if not, go to step S23;
step S23: obtaining exhaust temperature variation DeltaTd of unit compressor after opening degree is reduced 2 Comparing the exhaust temperature variation Δtd 2 And a second variation threshold DeltaTd 2 th；
If |DeltaTd 2 |≥|ΔTd 2 th|, reducing the opening of the electronic expansion valve according to the opening reduction value again after delaying the third time period, and then turning to step S22;
if 0 is<|ΔTd 2 |<|ΔTd 2 th|, delaying the fourth time period and then reducing again according to the opening degreeThe value decreases the opening of the electronic expansion valve, and then goes to step S22;
wherein the fourth duration is less than the third duration.
5. The control method of an electronic expansion valve according to claim 4, characterized in that the method further comprises determining the opening degree reduction value by:
if-Tth 2 is less than or equal to DeltaT is less than or equal to-Tth 1, the opening degree reduction value is O 2 And O is 2 >0, tth2 represents a temperature difference threshold and Tth2>Tth1>0；
If DeltaT<-Tth2, the opening degree reduction value is 2O 2 。
6. Control device for an electronic expansion valve, comprising a processor and storage means adapted to store a plurality of program code, characterized in that the program code is adapted to be loaded and executed by the processor to perform the control method for an electronic expansion valve according to any of claims 1 to 5.
7. A computer readable storage medium, in which a plurality of program codes are stored, characterized in that the program codes are adapted to be loaded and executed by a processor to perform the control method of an electronic expansion valve according to any one of claims 1 to 5.
8. An air source heat pump unit, characterized in that it comprises the control device of the electronic expansion valve of claim 6.
CN202210304549.4A 2022-03-21 2022-03-21 Control method and device for electronic expansion valve, medium and air source heat pump unit Active CN114608181B (en)

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