WO2019149167A1 - 一种空调散热结构控制方法及系统 - Google Patents

一种空调散热结构控制方法及系统 Download PDF

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Publication number
WO2019149167A1
WO2019149167A1 PCT/CN2019/073368 CN2019073368W WO2019149167A1 WO 2019149167 A1 WO2019149167 A1 WO 2019149167A1 CN 2019073368 W CN2019073368 W CN 2019073368W WO 2019149167 A1 WO2019149167 A1 WO 2019149167A1
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Prior art keywords
deviation
refrigerant
heat
temperature
electronic expansion
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PCT/CN2019/073368
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English (en)
French (fr)
Inventor
刘玉辉
程绍江
贺雪飞
白闻博
冷宇
Original Assignee
青岛海尔空调电子有限公司
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Application filed by 青岛海尔空调电子有限公司 filed Critical 青岛海尔空调电子有限公司
Priority to US16/966,693 priority Critical patent/US11530855B2/en
Priority to EP19747960.3A priority patent/EP3748251A4/en
Publication of WO2019149167A1 publication Critical patent/WO2019149167A1/zh

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F13/00—Details common to, or for air-conditioning, air-humidification, ventilation or use of air currents for screening
    • F24F13/30—Arrangement or mounting of heat-exchangers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/62—Control or safety arrangements characterised by the type of control or by internal processing, e.g. using fuzzy logic, adaptive control or estimation of values
    • F24F11/63—Electronic processing
    • F24F11/64—Electronic processing using pre-stored data
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/70—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
    • 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
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F1/00—Room units for air-conditioning, e.g. separate or self-contained units or units receiving primary air from a central station
    • F24F1/06—Separate outdoor units, e.g. outdoor unit to be linked to a separate room comprising a compressor and a heat exchanger
    • F24F1/20—Electric components for separate outdoor units
    • F24F1/24—Cooling of electric components
    • 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
    • F24F11/50—Control or safety arrangements characterised by user interfaces or communication
    • F24F11/61—Control or safety arrangements characterised by user interfaces or communication using timers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/88—Electrical aspects, e.g. circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F2140/00—Control inputs relating to system states
    • F24F2140/20—Heat-exchange fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/23—Separators
    • 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]
    • Y02B30/70—Efficient control or regulation technologies, e.g. for control of refrigerant flow, motor or heating

Definitions

  • the invention belongs to the technical field of air conditioners, and in particular relates to a method and system for controlling air-conditioning heat dissipation structure.
  • inverter air conditioners are widely used in the market due to their advantages of intelligence, high efficiency, low noise, and high temperature regulation.
  • the inverter air conditioner is a control system that controls and adjusts the compressor speed through the inverter, so that it is always in the optimal speed state.
  • some other power components in the inverter and the electric control box generate a large amount of heat during operation, if these powers The heat of the components can not be dissipated in time.
  • the temperature of the inverter is out of range, which directly affects the control of the operating frequency of the compressor. In severe cases, the compressor will stop working. Second, the temperature inside the electric control cabinet will be very high. The operating temperature range of the device causes damage to components; therefore, the thermal design of the drive is critical.
  • the louver is formed inside the electric control box by designing the louver, and the power device such as the inverter in the box is radiated.
  • This cooling method is limited by the waterproof and dustproof requirements. It is very large, and it is far from meeting the heat dissipation requirements of high-power components.
  • the heat dissipation design of another conventional inverter mostly uses forced convection, that is, the design method of the cooling fan.
  • the cooling fan has poor heat dissipation effect.
  • the cooling fan has a limited service life and high damage rate. Long-term operation is a huge test for the life of the fan. Once the cooling fan fails, it directly affects the working stability of the inverter. If the life of the fan is extended, the cost will increase even more. Not conducive to product cost control.
  • the invention provides a method for controlling a heat dissipation structure of an air conditioner, which solves the problems of poor heat dissipation reliability and high heat dissipation cost in the prior art.
  • the heat dissipation structure includes a refrigerant heat pipe, the refrigerant heat pipe is fixed to an air conditioner heat generating device, and an inlet end of the refrigerant heat pipe is connected between an outdoor heat exchanger and an indoor heat exchanger.
  • the outlet end of the refrigerant heat pipe is connected to the liquid inlet pipe of the gas-liquid separator, and an electronic expansion valve is connected in series on the refrigerant heat pipe;
  • the control method includes:
  • ⁇ T deviation ' is the deviation calculated last time
  • the opening degree of the electronic expansion valve is adjusted based on the deviation ⁇ T deviation and the deviation change rate ⁇ T deviation .
  • the correction value when 90 ° C ⁇ Te ⁇ 100 ° C, the correction value is -3 ° C; when 80 ° C ⁇ Te ⁇ 90 ° C, the correction value is -2 ° C; when 70 ° C ⁇ Te ⁇ 80 ° C, the correction value is -1 °C; when 60 ° C ⁇ Te ⁇ 70 ° C, the correction value is 0; when 50 ° C ⁇ Te ⁇ 60 ° C, the correction value is 1 ° C; when 40 ° C ⁇ Te ⁇ 50 ° C, the correction value is 2 ° C.
  • the adjusting the opening degree of the electronic expansion valve according to the deviation ⁇ T deviation and the deviation change rate ⁇ T deviation includes:
  • Tmax Te d +5.
  • the initial opening degree is 40% to 60% of the full opening degree.
  • a solenoid valve is connected in series to the refrigerant heat pipe for controlling the on and off of the refrigerant heat pipe.
  • the refrigerant heat pipe is fixed by the heat dissipation substrate and the air conditioning heat generating device, and the heat transfer medium is coated on the contact surface of the heat dissipation substrate and the heat sink heat pipe, and the heat transfer medium is also coated on the contact surface of the heat dissipation substrate and the air conditioner heat generating device.
  • An air conditioning heat dissipation structure control system includes a heat dissipation structure and a control system;
  • the heat dissipation structure includes a refrigerant heat dissipation tube and a heat dissipation substrate, the air conditioning heat generation device is fixed to the heat dissipation substrate, and the refrigerant heat dissipation tube is embedded in the heat dissipation substrate;
  • the contact surface of the substrate and the refrigerant heat pipe is coated with a heat conductive medium, and the heat transfer medium is also coated on the contact surface of the heat dissipation substrate and the air conditioner heat generating device;
  • the inlet end of the refrigerant heat pipe is connected to the outdoor heat exchanger and the indoor heat exchanger On the liquid pipe, the outlet end of the refrigerant heat pipe is connected to the liquid inlet pipe of the gas-liquid separator, and the electronic expansion valve and the electromagnetic valve are connected in series on the refrigerant heat pipe;
  • the advantages and positive effects of the present invention are: the air conditioning heat dissipation structure control method and system of the present invention, obtaining the actual temperature Te of the air conditioning heating device, and adjusting when the Te> preset optimal temperature Te d
  • the refrigerant is used to heat the device. Cooling heat dissipation, low cooling costs, improve thermal stability and reliability, thereby improving the reliability and stability of operation of the air conditioning, the prior art to solve the heat dissipation poor reliability, high cooling costs.
  • FIG. 1 is a flow chart of an embodiment of a method for controlling an air-conditioning heat dissipation structure according to the present invention
  • Figure 2 is a front view of the heat dissipation structure
  • Figure 3 is a left side view of Figure 2;
  • FIG. 4 is a schematic view showing the structure of an air conditioner connected to the refrigerant heat pipe of FIG. 2;
  • FIG. 5 is a structural block diagram of an embodiment of an air conditioning heat dissipation structure control system according to the present invention.
  • the invention provides a method and a system for controlling the heat dissipation structure of an air conditioner, which solves the problems of low heat dissipation reliability, poor heat dissipation effect and high heat dissipation cost of the air conditioner heating device in the prior art, improves the reliability and stability of heat dissipation, and ensures air conditioning. Runs reliably and reliably.
  • the following describes the air conditioning heat dissipation structure control method and system.
  • Refrigerant circuit in air conditioning and refrigeration conditions compressor ⁇ oil separator ⁇ four-way valve (DC channel) ⁇ outdoor heat exchanger 11 (fin fin condenser) ⁇ check valve 15 ⁇ liquid storage tank ⁇ drying filter 13 ⁇ Electronic expansion valve 14 ⁇ check valve 18 ⁇ indoor heat exchanger 12 (dry evaporator) ⁇ four-way valve (ES channel) ⁇ gas-liquid separator ⁇ compressor.
  • Refrigerant circuit in air conditioning heating condition compressor ⁇ oil separator ⁇ four-way valve (DE channel) ⁇ indoor heat exchanger 12 (dry evaporator) ⁇ check valve 17 ⁇ liquid storage tank ⁇ drying filter 13 ⁇ Electronic expansion valve 14 ⁇ check valve 16 ⁇ outdoor heat exchanger 11 (fin fin condenser) ⁇ four-way valve (CS passage) ⁇ gas-liquid separator ⁇ compressor.
  • the heat dissipation structure mainly comprises a refrigerant heat pipe 2, the refrigerant heat pipe 2 is fixed with the air conditioner heat generating device 3, and the inlet end of the refrigerant heat pipe 2 is connected to the liquid pipe between the outdoor heat exchanger and the indoor heat exchanger, and the refrigerant heat pipe 2
  • the outlet end is connected to the inlet pipe of the gas-liquid separator, and an electronic expansion valve 4 is connected in series to the refrigerant heat pipe 2 for adjusting the flow rate of the refrigerant in the refrigerant heat pipe 2, as shown in FIG. 2 to FIG.
  • the inlet end of the refrigerant heat pipe 2 is specifically connected to the outlet end of the liquid storage tank, that is, the pipeline before the electronic expansion valve 14 is throttled, and four check valves (check valves 15, 16, 17, 18) are provided. That is, under the cooling and heating conditions, the temperature of the refrigerant in the refrigerant heat pipe 2 can be maintained within a certain range.
  • the refrigerant flowing out from the liquid storage tank is divided into two paths: one passage of the refrigerant flows to the drying filter 13 ⁇ the electronic expansion valve 14 to perform a normal cooling and heating cycle, and the other refrigerant enters the refrigerant heat exchange tube 2, and the air conditioning heating device The heat exchange is performed, and then flows into the gas-liquid separator through the refrigerant heat pipe 2, and then flows into the compressor.
  • the air conditioning heating device includes various heating devices in the electric control box, such as a frequency converter.
  • the heat of the air-conditioning heat generating device 3 is transferred to the refrigerant in the refrigerant heat pipe 2 by the principle of heat conduction.
  • a solenoid valve SV2 is also connected in series on the refrigerant heat pipe 2, and the solenoid valve SV2 is opened or closed.
  • the refrigerant heat pipe 3 is turned on or off.
  • the solenoid valve SV2 and the electronic expansion valve 4 are connected in series at the inlet end of the refrigerant heat pipe 2, so as to facilitate Timely control of the refrigerant heat pipe, and timely adjust the refrigerant flow.
  • the refrigerant heat pipe 2 is fixed to the air conditioning heat generating device 3 through the heat dissipation substrate 1 to facilitate the fixing of the refrigerant heat pipe 2 and the air conditioning heat generating device 3.
  • the air-conditioning heat generating device 3 is fixedly connected to the heat-dissipating substrate 1 by bolts, and the refrigerant heat-dissipating tube 2 is embedded in the heat-dissipating substrate 1.
  • the heat transfer medium is coated on the contact surface of the heat dissipation substrate 1 and the refrigerant heat pipe 2, and the heat transfer medium is also coated on the contact surface of the heat dissipation substrate 1 and the air conditioner heat generating device 3 to facilitate heat conduction and accelerate heat dissipation.
  • the thermal medium can be selected from silica gel for good thermal conductivity.
  • the heat generated by the air-conditioning heat generating device 3 is transmitted to the heat-dissipating substrate 1, and the heat of the heat-dissipating substrate 1 exchanges heat with the refrigerant in the refrigerant heat-dissipating tube 2.
  • the heat of the heat generating device 3 is transferred to the refrigerant system by the principle of heat conduction to ensure heat dissipation of the heat generating device.
  • the heat conduction direction of the heat generating device is: heat generating device ⁇ heat sink substrate 1 ⁇ refrigerant heat pipe 2 .
  • the air conditioning heat dissipation structure control method of this embodiment specifically includes the following steps, as shown in FIG. 1 .
  • Step S11 The air conditioner is powered on.
  • Step S12 Acquire the actual temperature Te of the air conditioning heating device.
  • Step S13 It is judged whether Te is > the preset optimal temperature Te d .
  • step S14 If not, that is, Te ⁇ Te d , the temperature of the heat generating device is low, and the refrigerant of the refrigerant heat pipe is not required to dissipate heat, and therefore step S14 is performed.
  • step S15 is performed.
  • Step S14 The solenoid valve SV2 is closed, the electronic expansion valve 4 is closed, and the process returns to step S12.
  • Step S15 The solenoid valve SV2 is opened, and the electronic expansion valve 4 is adjusted to be opened to the initial opening degree.
  • the solenoid valve SV2 is opened, the electronic expansion valve 4 is opened to the initial opening degree, the refrigerant flows into the refrigerant heat pipe, and then flows to the gas-liquid separator, and then flows into the compressor.
  • the refrigerant in the refrigerant heat pipe exchanges heat with the heat generating device to cool the heat generating device.
  • the initial opening degree of the electronic expansion valve 4 is 40% to 60% of the full opening degree.
  • the initial opening range is selected to avoid the refrigerant flow in the refrigerant heat pipe being too small due to the initial opening degree being too small, the heat exchange effect is not obvious, the heat dissipation effect is not obtained, and the refrigerant flow in the refrigerant heat pipe caused by the excessive initial opening is avoided.
  • the initial opening degree is 50% of the full opening degree, which not only ensures a certain heat dissipation effect, but also avoids affecting the normal refrigerant circulation.
  • the initial opening degree is 560 steps - 840 steps.
  • the initial opening is 700 steps.
  • Step S16 After setting the time, the actual temperature Te of the air-conditioning heating device is re-acquired.
  • the electronic expansion valve 4 is opened to the initial opening degree. After the set time, it is necessary to determine the heat dissipation effect of the refrigerant in the refrigerant heat pipe to the heat generating device, and it is necessary to reacquire the actual temperature of the air conditioning heat generating device.
  • Step S17 It is judged whether or not the actual temperature Te at this time is > the preset upper limit value Tmax. Where Tmax>Te d .
  • Tmax Te d + 5, that is, the upper limit value Tmax is 5 ° C above the optimum temperature Te d . If the Tmax is too small, the actual temperature Te is relatively easy to be greater than Tmax, that is, it is easy to enter S18-S22 frequently, which causes the heat dissipation method to be too complicated and cumbersome; if the Tmax is too large, the actual temperature Te is not easy to exceed Tmax, which tends to cause the temperature of the heating device to be high. The opening adjustment is still not performed, resulting in the opening adjustment not being timely, so that the heating device continues to operate at high temperatures and burns.
  • Tmax Te d +5
  • the value of Tmax is reasonable, which ensures that the opening degree of the electronic expansion valve 4 is adjusted in time when the temperature of the heat generating device is high, and the control is simple, and the frequent entry into the S18 is avoided.
  • steps S18 to S22 are performed every set time (for example, 10 minutes).
  • Step S18 obtaining the refrigerant temperature T in at the inlet end of the refrigerant heat pipe and the refrigerant temperature T out at the outlet end.
  • the target temperature difference is more accurate.
  • the correction value is determined according to the current actual temperature Te of the heat generating device, and specifically includes:
  • the above-mentioned correction of the preset target temperature difference according to the actual temperature Te of the heat generating device can determine a more accurate target temperature difference, thereby determining a more accurate deviation, thereby improving the accuracy of the opening adjustment of the electronic expansion valve 4.
  • the rate of change of deviation indicates the trend of variation, such as increase, decrease, and constant.
  • the ⁇ T deviation ' is the deviation calculated last time.
  • Step S22 The opening degree of the electronic expansion valve is adjusted based on the deviation ⁇ T deviation and the deviation change rate ⁇ T deviation .
  • the actual temperature Te of the air conditioning heating device is obtained, and when the Te> preset optimal temperature Te d , the electronic expansion valve is adjusted to be opened to the initial opening degree; after the set time, the air conditioning is regained.
  • the refrigerant is used to cool and heat the heat-generating device, the heat dissipation cost is low, and the heat dissipation reliability and stability are improved.
  • the prior art to solve the heat dissipation poor reliability, high cooling costs.
  • the opening degree of the electronic expansion valve 4 is adjusted according to the deviation, so that the temperature difference between the outlet end of the refrigerant heat pipe and the inlet end reaches the target temperature difference, thereby achieving good heat dissipation of the air conditioning heating device and having good heat dissipation effect.
  • Adjusting the opening degree of the electronic expansion valve 4 according to the deviation change rate that is, taking into account the variation trend of the deviation in the opening degree adjustment, thereby avoiding frequent adjustment of the opening degree of the electronic expansion valve 4, avoiding large fluctuation of the refrigerant flow rate, and avoiding influence of the refrigerant
  • the normal cooling and heating cycle improves the stability of air conditioning operation.
  • the heat of the heat generating device is transferred to the refrigerant, and the heat is dissipated by the refrigerant for the heat generating device, the energy saving is reliable, the cost is low, and the normal operation of the heat generating device is ensured.
  • Adjusting the opening degree of the electronic expansion valve 4 according to the deviation ⁇ T deviation and the deviation change rate ⁇ T deviation specifically includes:
  • the ⁇ T deviation is >3 ° C, that is, the refrigerant temperature difference > the target temperature difference, and the difference between the two is large, it is necessary to increase the opening degree of the electronic expansion valve 4 .
  • the opening degree of the electronic expansion valve 4 is increased or decreased according to the specific value range of the deviation and the rate of change of the deviation, so that the temperature difference between the outlet end of the refrigerant heat pipe and the refrigerant at the inlet end is reached.
  • the target temperature difference ensures the heat dissipation effect, and avoids frequently adjusting the opening degree of the electronic expansion valve 4 to ensure the running stability.
  • the electronic expansion valve 4 is reduced by 32 steps.
  • the electronic expansion valve 4 is increased by 36 steps.
  • the opening of the electronic expansion valve 4 can be adjusted according to the two factors of the deviation and the rate of change of the deviation, so that the stable adjustment of the electronic expansion valve 4 can be achieved, that is, it can be increased or decreased based on the previous opening degree. If the opening degree is not adjusted according to the deviation and the rate of change, the electronic expansion valve 4 needs to repeatedly open or close the initial opening degree, and then adjusts from the initial opening degree, the adjustment is slow, and the effect is poor.
  • the embodiment further provides an air conditioning heat dissipation structure control system, including a heat dissipation structure and a control system.
  • the heat dissipation structure includes a refrigerant heat pipe 2 and a heat dissipation substrate 1.
  • the air conditioning heat generating device 3 is fixed to the heat dissipation substrate 1, and the refrigerant heat pipe 2 is embedded in the heat dissipation substrate 1; on the contact surface of the heat dissipation substrate 1 and the refrigerant heat pipe 2 The heat transfer medium is coated, and a heat transfer medium is also applied to the contact surface of the heat dissipation substrate 1 and the air conditioner heat generating device 3.
  • the inlet end of the refrigerant heat pipe 2 is connected to the liquid pipe between the outdoor heat exchanger and the indoor heat exchanger, and the outlet end of the refrigerant heat pipe 2 is connected to the liquid inlet pipe of the gas-liquid separator, and the refrigerant heat pipe 2 is connected in series.
  • the control system includes an air conditioning heating device temperature acquisition module, a determination module, a refrigerant temperature acquisition module, a temperature difference calculation module, a correction module, a deviation calculation module, a deviation change rate calculation module, an opening adjustment module, and the like, as shown in FIG. 5 .
  • the air conditioning heating device temperature acquisition module is used to obtain the actual temperature Te of the air conditioning heating device.
  • the determining module is configured to determine whether the actual temperature Te is > the preset optimal temperature Te d ; and is also used to determine whether the actual temperature Te is > a preset upper limit value Tmax; wherein Tmax>Te d .
  • the refrigerant temperature obtaining module is configured to obtain a refrigerant temperature T in at the inlet end of the refrigerant heat pipe and a refrigerant temperature T out at the outlet end.
  • the correction module is configured to determine a correction value according to the actual temperature Te of the air-conditioning heating device, and correct the target temperature difference.
  • the opening adjustment module is configured to adjust the opening of the electronic expansion valve to the initial opening degree, and is also used for adjusting the opening degree of the electronic expansion valve according to the deviation ⁇ T deviation and the deviation change rate ⁇ T deviation .
  • the refrigerant is used to cool and heat the heat-generating device, the heat dissipation cost is low, and the heat dissipation reliability and stability are improved.
  • the prior art to solve the heat dissipation poor reliability, high cooling costs.

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Abstract

本发明公开了一种空调散热结构控制方法及系统，获取空调发热器件的实际温度Te，在Te＞预设的最佳温度Te d时，调整电子膨胀阀开启至初始开度；设定时间后，重新获取空调发热器件的实际温度Te；在实际温度Te＞预设的上限值Tmax时，获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；计算温差△T 实际＝Tout-T in；计算偏差△T 偏差＝△T 实际-△T 目标；计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差'；根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度，使得冷媒散热管的出口端与进口端的冷媒温差达到目标温差，实现空调发热器件的良好散热，具有较好散热效果，散热成本低，可靠性高。

Description

一种空调散热结构控制方法及系统 技术领域
本发明属于空调技术领域，具体地说，是涉及一种空调散热结构控制方法及系统。
背景技术
目前变频空调以其智能化、高效节能、低噪音、调温速度快等优点在市场上得到广泛使用。变频空调是通过变频器控制和调整压缩机转速的控制系统，使之始终处于最佳的转速状态，然而变频器和电控箱体内一些其他功率元件，在工作时会产生大量热量，如果这些功率元器件的热量不能及时散出，一则变频器温度超出范围，直接影响压缩机运行频率的控制，严重时会导致压缩机停止工作；二则电控箱体内部的温度会非常高，超出元器件的工作温度范围，导致元器件的损坏；因此，变频器的散热设计至关重要。
传统散热方式有两种类型，一种是自然冷却，即通过设计百叶窗的形式使电控箱体内部形成对流，给箱体内变频器等功率器件散热，此种冷却方式结合防水防尘要求受局限很大，且已远远不能满足高功率元器件的散热需求；另一种传统变频器的散热设计大部分采用强制对流，即冷却风扇的设计方法，其缺点一方面是冷却风扇散热效果差，其次，冷却风扇的使用寿命有限，损坏率高，长期运转对于风扇寿命是一种巨大考验，冷却风扇一旦失效则直接影响变频器的工作稳定性，如果延长风扇的寿命则成本会增加更大，不利于产品成本控制。
发明内容
本发明提供了一种空调散热结构控制方法，解决了现有技术中散热可靠性差、散热成本高的问题。
为解决上述技术问题，本发明采用下述技术方案予以实现：
一种空调散热结构控制方法，所述散热结构包括冷媒散热管，所述冷媒散热管与空调发热器件固定，所述冷媒散热管的进口端连接在室外换热器和室内换热器之间的液管上，所述冷媒散热管的出口端连接气液分离器的进液管，在所述冷媒散热管上串联有电子膨胀阀；
所述控制方法包括：
获取空调发热器件的实际温度Te，判断Te是否＞预设的最佳温度Te d；
若是，则调整电子膨胀阀开启至初始开度；
设定时间后，重新获取空调发热器件的实际温度Te；
判断此时的实际温度Te是否＞预设的上限值Tmax；其中，Tmax＞Te d；
若是，则每隔设定时间执行下述步骤：
(1)获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；
(2)计算温差△T 实际＝T out-T in；
(3)获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实际-△T 目标；
(4)计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；
其中，△T 偏差′为上一次计算出的偏差；
(5)根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
进一步的，在步骤(3)中，获取预设的目标温差△T 目标之后，先根据空调发热器件的实际温度Te确定修正值，对目标温差进行修正，修正后的目标温差＝预设的目标温差△T 目标+修正值，然后根据修正后的目标温差计算偏差△T 偏差＝△T 实际-(△T 目标+修正值)。
又进一步的，空调发热器件的实际温度Te越大，修正值越小，而且，
当Te≥第二设定温度时，修正值＜0；
当第一设定温度≤Te＜第二设定温度时，修正值＝0；
当Te＜第一设定温度时，修正值＞0。
更进一步的，当90℃≤Te＜100℃，修正值为-3℃；当80℃≤Te＜90℃，修正值为-2℃；当70℃≤Te＜80℃，修正值为-1℃；当60℃≤Te＜70℃，修正 值为0；当50℃≤Te＜60℃，修正值为1℃；当40℃≤Te＜50℃，修正值为2℃。
进一步的，所述根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度，具体包括：
(1)当△T 偏差＜0，且△△T 偏差＜0时，则减小电子膨胀阀开度；
(2)当△T 偏差＝0，且△△T 偏差＝0时，则保持电子膨胀阀开度不变；
(3)当△T 偏差＞0，且△△T 偏差＞0时，则增大电子膨胀阀开度；
(4)当△T 偏差＜0，且△△T 偏差＞0时：
若-2℃＜△T 偏差＜0，则增大电子膨胀阀开度；
若△T 偏差≤-2℃，则减小电子膨胀阀开度；
(5)当△T 偏差＞0，且△△T 偏差＜0时：
若0＜△T 偏差≤3℃，且△△T 偏差≤-2℃，则减小电子膨胀阀开度；
若0＜△T 偏差≤3℃，且-2℃＜△△T 偏差＜0，则增大电子膨胀阀开度；
若△T 偏差＞3℃，则增大电子膨胀阀开度。
优选的，Tmax＝Te d+5。
优选的，所述初始开度为满开度的40％～60％。
进一步的，在所述冷媒散热管上还串联有电磁阀，用于控制冷媒散热管的通断。
又进一步的，所述冷媒散热管通过散热基板与空调发热器件固定，在散热基板与冷媒散热管的接触面上涂有导热介质，在散热基板与空调发热器件的接触面上也涂有导热介质。
一种空调散热结构控制系统，包括散热结构和控制系统；所述散热结构包括冷媒散热管和散热基板，所述空调发热器件与散热基板固定，所述冷媒散热管嵌入到散热基板中；在散热基板与冷媒散热管的接触面上涂有导热介质，在散热基板与空调发热器件的接触面上也涂有导热介质；所述冷媒散热管的进口端连接在室外换热器和室内换热器之间的液管上，所述冷媒散热管的出口端连接气液分离器的进液管，在所述冷媒散热管上串联有电子膨胀阀和电磁阀；
所述控制系统包括：空调发热器件温度获取模块，用于获取空调发热器件的实际温度Te；判断模块，用于判断实际温度Te是否＞预设的最佳温度Te d；还用于判断实际温度Te是否＞预设的上限值Tmax；其中，Tmax＞Te d；冷媒温度获取模块，用于获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；温差计算模块，用于计算温差△T 实际＝T out-T in；修正模块，用于根据空调发热器件的实际温度Te确定修正值，对目标温差进行修正；偏差计算模块，用于计算偏差△T 偏差＝△T 实际-△T 目标；偏差变化率计算模块，用于计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；其中，△T 偏差′为上一周期计算出的偏差；开度调整模块，用于调整电子膨胀阀开启至初始开度，还用于根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
与现有技术相比，本发明的优点和积极效果是：本发明的空调散热结构控制方法及系统，获取空调发热器件的实际温度Te，在Te＞预设的最佳温度Te d时，调整电子膨胀阀开启至初始开度；设定时间后，重新获取空调发热器件的实际温度Te；在实际温度Te＞预设的上限值Tmax时，每隔设定时间执行下述步骤：获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；计算温差△T 实际＝T out-T in；获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实 际-△T 目标；计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀4的开度，使得冷媒散热管的出口端与进口端的冷媒温差达到目标温差，实现空调发热器件的良好散热，具有较好散热效果，保证空调发热器件的良好运行；而且，利用冷媒来对发热器件进行降温散热，散热成本低，提高了散热可靠性和稳定性，从而提高空调运转的可靠性和稳定性，解决了现有技术中散热可靠性差、散热成本高的问题。
结合附图阅读本发明的具体实施方式后，本发明的其他特点和优点将变得更加清楚。
附图说明
图1是本发明提出的空调散热结构控制方法的一个实施例的流程图；
图2是散热结构的主视图；
图3是图2的左视图；
图4是图2中的冷媒散热管连接的空调结构示意图；
图5是本发明提出的空调散热结构控制系统的一个实施例的结构框图。
附图标记：
1、散热基板；2、冷媒散热管；3、发热器件；4、电子膨胀阀；
11、室外换热器；12、室内换热器；13、干燥过滤器；14、电子膨胀阀；15、单向阀；16、单向阀；17、单向阀；18、单向阀。
具体实施方式
为了使本发明的目的、技术方案及优点更加清楚明白，以下将结合附图和实施例，对本发明作进一步详细说明。
本发明提出了一种空调散热结构控制方法及系统，解决了现有技术中空调发热器件散热可靠性低、散热效果差、散热成本高的问题，提高了散热的可靠性和稳定性，保证空调稳定可靠地运行。下面对空调散热结构控制方法及系统进行说明。
空调的结构参见图4所示。
空调制冷工况时的冷媒回路：压缩机→油分离器→四通阀(DC通道)→室外换热器11(翅片冷凝器)→单向阀15→储液罐→干燥过滤器13→电子膨胀阀14→单向阀18→室内换热器12(干式蒸发器)→四通阀(ES通道)→气液分离器→压缩机。
空调制热工况时的冷媒回路：压缩机→油分离器→四通阀(DE通道)→室内换热器12(干式蒸发器)→单向阀17→储液罐→干燥过滤器13→电子膨胀阀14→单向阀16→室外换热器11(翅片冷凝器)→四通阀(CS通道)→气液分离器→压缩机。
散热结构主要包括冷媒散热管2，冷媒散热管2与空调发热器件3固定， 冷媒散热管2的进口端连接在室外换热器和室内换热器之间的液管上，冷媒散热管2的出口端连接气液分离器的进液管，在冷媒散热管2上串联有电子膨胀阀4，用于调节冷媒散热管2内的冷媒流量，参见图2至图4所示。
冷媒散热管2的进口端具体连接在储液罐的出口端，即电子膨胀阀14节流前的管路中，通过设置四个单向阀(单向阀15、16、17、18)，即可以实现在制冷和制热工况下，冷媒散热管2中的冷媒温度维持在一定范围内。
因此，从储液罐流出的冷媒分流为两路：一路冷媒流至干燥过滤器13→电子膨胀阀14，进行正常的制冷制热循环，另一路冷媒进入冷媒换热管2，与空调发热器件进行热交换，然后经冷媒散热管2流入气液分离器，再流入压缩机。
空调发热器件包括电控箱内的各个发热器件，如变频器等。通过热传导的原理，将空调发热器件3的热量传递到冷媒散热管2内的冷媒中。
由于有的电子膨胀阀无法起到完全关断管路的作用，因此，为了实现冷媒散热管2的完全关断，在冷媒散热管2上还串联有电磁阀SV2，电磁阀SV2开启或关闭实现冷媒散热管3的导通或关断。
为了实现冷媒散热管2的快速通断以及流量的快速调节，避免浪费冷媒，避免影响正常的制冷制热循环，电磁阀SV2和电子膨胀阀4均串联在冷媒散热管2的进口端，以便于及时对冷媒散热管进行通断控制，以及及时调节冷媒流量。
在本实施例中，冷媒散热管2通过散热基板1与空调发热器件3固定，以便于冷媒散热管2和空调发热器件3的固定。空调发热器件3与散热基板1通过螺栓固定连接，冷媒散热管2嵌入到散热基板1内。在散热基板1与冷媒散热管2的接触面上涂有导热介质，在散热基板1与空调发热器件3的接触面上也涂有导热介质，以便于热量的传导，加快散热。导热介质可选择硅胶，导热效果好。
空调发热器件3发出的热量传递到散热基板1上，散热基板1的热量与冷媒散热管2中的冷媒发生热交换。利用热传导原理将发热器件3的热量传递到 冷媒系统中，保证发热器件的散热。发热器件热量的传导方向为：发热器件→散热基板1→冷媒散热管2。
本实施例的空调散热结构控制方法具体包括下述步骤，参见图1所示。
步骤S11：空调上电开机。
步骤S12：获取空调发热器件的实际温度Te。
步骤S13：判断Te是否＞预设的最佳温度Te d。
若否，即Te≤Te d，发热器件的温度较低，无需冷媒散热管的冷媒进行散热，因此执行步骤S14。
若是，即Te＞Te d，发热器件的温度较高，需要冷媒散热管的冷媒进行散热，因此执行步骤S15。
步骤S14：关闭电磁阀SV2，关闭电子膨胀阀4，返回步骤S12。
电磁阀SV2和电子膨胀阀4关闭后，从储液罐流出的冷媒不进入冷媒散热管。
步骤S15：打开电磁阀SV2，调整电子膨胀阀4开启至初始开度。
电磁阀SV2打开，电子膨胀阀4开启至初始开度，冷媒流入冷媒散热管，然后流至气液分离器，再流入压缩机。冷媒散热管中的冷媒与发热器件进行热交换，为发热器件降温。
在本实施例中，电子膨胀阀4的初始开度为满开度的40％～60％。选择该初始开度范围，既避免初始开度过小导致的冷媒散热管内冷媒流量过小、热交换效果不明显、无法起到散热作用，又避免初始开度过大导致的冷媒散热管内冷媒流量过大、影响正常的冷媒循环且导致后续步骤S22中开度调节范围过小；因此，选择该初始开度范围，既保证电子膨胀阀4在开启到初始开度时，能够对发热器件起到散热作用，又保证正常的冷媒循环以及后续步骤S22中具有较大的开度调节范围。作为本实施例的一种优选设计方案，初始开度为满开度的50％，既保证具有一定的散热作用，又避免影响正常的冷媒循环。
例如，电子膨胀阀4满开度为1400步，则初始开度为560步～840步。优 选的，初始开度为700步。
步骤S16：设定时间后，重新获取空调发热器件的实际温度Te。
电子膨胀阀4开启至初始开度，设定时间后，需要判断冷媒散热管内的冷媒对发热器件的散热效果，需要重新获取空调发热器件的实际温度。
步骤S17：判断此时的实际温度Te是否＞预设的上限值Tmax。其中，Tmax＞Te d。
若否，即此时Te≤Tmax，发热器件的温度还在允许的范围内，电子膨胀阀4初始开度即可满足散热需求，不需调节电子膨胀阀4的开度，返回步骤S12。
若是，即此时Te＞Tmax，发热器件的温度较高，电子膨胀阀4初始开度不能满足散热需求，需要调节电子膨胀阀4的开度，则每隔设定时间执行步骤S18～S22。
在本实施例中，Tmax＝Te d+5，即上限值Tmax为最佳温度Te d上浮5℃。如果Tmax过小，则实际温度Te比较容易大于Tmax，即易于频繁进入S18～S22，导致散热方法过于复杂繁琐；如果Tmax过大，则实际温度Te不易超过Tmax，容易导致发热器件温度较高时仍然不再进行开度调节，导致开度调节不及时，使得发热器件在高温下持续运转而烧毁。因此，Tmax＝Te d+5，Tmax取值合理，既保证了在发热器件温度较高时及时调节电子膨胀阀4的开度，又控制简单，避免频繁进入S18。
当电子膨胀阀4处于初始开度无法满足散热需求时，每隔设定时间(如10分钟)执行步骤S18～S22。
步骤S18：获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out。
步骤S19：计算冷媒散热管出口端和进口端的冷媒温差△T 实际＝T out-T in。
步骤S20：获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实际-△T 目标。
在本实施例中，为了使得目标温差更加精确，需要对预设的目标温差进行修正。
在本步骤中，获取预设的目标温差△T 目标之后，先根据空调发热器件的当 前实际温度Te确定修正值，对目标温差进行修正，修正后的目标温差＝预设的目标温差△T 目标+修正值，然后根据修正后的目标温差计算偏差△T 偏差＝△T 实 际-(△T 目标+修正值)。偏差计算出来后，进行记录，保存下来。
通过根据当前实际温度Te对目标温差进行修正，使得目标温差更加精确。
在本实施例中，空调发热器件的实际温度Te越大，修正值越小，而且，
(1)当Te≥第二设定温度(如70℃)时，由于发热器件的实际温度过高，需要降低预设的目标温差，因此，修正值＜0。
(2)当第一设定温度≤Te＜第二设定温度时，无需改变预设的目标温差，因此，修正值＝0。
(3)当Te＜第一设定温度(如60℃)时，由于发热器件的实际温度较低，需要提高预设的目标温差，因此，修正值＞0。
根据发热器件的当前实际温度Te确定修正值，具体包括：
a、当90℃≤Te＜100℃，修正值为-3℃；修正后的目标温差＝△T 目标-3℃；
b、当80℃≤Te＜90℃，修正值为-2℃；修正后的目标温差＝△T 目标-2℃；
c、当70℃≤Te＜80℃，修正值为-1℃；修正后的目标温差＝△T 目标-1℃；
d、当60℃≤Te＜70℃，修正值为0；修正后的目标温差＝△T 目标；
e、当50℃≤Te＜60℃，修正值为1℃；修正后的目标温差＝△T 目标+1℃；
f、当40℃≤Te＜50℃，修正值为2℃；修正后的目标温差＝△T 目标+2℃。
上述根据发热器件的实际温度Te对预设的目标温差进行修正，可以确定更加精确的目标温差，从而可以确定更加精确的偏差，进而提高了电子膨胀阀4开度调节的准确性。
步骤S21：计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′。
偏差变化率表示偏差的变化趋势，如增大、减小、不变。
其中，△T 偏差′为上一次计算出的偏差。
步骤S22：根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
根据偏差、偏差变化率对电子膨胀阀4的开度进行调整，进而对流入冷媒 散热管的冷媒流量进行调整，从而保证具有足够流量的冷媒与空调发热器件进行热交换，对发热器件进行降温，实现较好的散热效果。
本实施例的空调散热结构控制方法，获取空调发热器件的实际温度Te，在Te＞预设的最佳温度Te d时，调整电子膨胀阀开启至初始开度；设定时间后，重新获取空调发热器件的实际温度Te；在实际温度Te＞预设的上限值Tmax时，每隔设定时间执行下述步骤：获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；计算温差△T 实际＝T out-T in；获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实际-△T 目标；计算偏差变化率△△T 偏差＝△T 偏差-△T 偏 差′；根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀4的开度，使得冷媒散热管的出口端与进口端的冷媒温差达到目标温差，实现空调发热器件的良好散热，具有较好散热效果，保证空调发热器件的良好运行；而且，利用冷媒来对发热器件进行降温散热，散热成本低，提高了散热可靠性和稳定性，从而提高空调运转的可靠性和稳定性，解决了现有技术中散热可靠性差、散热成本高的问题。
本实施例的空调散热结构控制方法，根据偏差调整电子膨胀阀4的开度，使得冷媒散热管的出口端与进口端的冷媒温差达到目标温差，实现空调发热器件的良好散热，具有良好的散热效果；根据偏差变化率调整电子膨胀阀4的开度，即在开度调节中考虑到偏差的变化趋势，从而避免频繁调节电子膨胀阀4的开度，避免冷媒流量有较大波动，避免影响冷媒的正常制冷制热循环，提高空调运行的稳定性。
本实施例的方法，将发热器件的热量传递到冷媒中，利用冷媒为发热器件散热，节能可靠，成本低，保证发热器件的正常运行。
根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀4的开度，具体包括：
(1)当△T 偏差＜0，且△△T 偏差＜0时，即冷媒散热管出口端和进口端的冷媒温差＜目标温差，发热器件温度过低；而且，偏差在减小；因此，冷媒散 热管内的冷媒流量过大，需要减小电子膨胀阀4开度。
(2)当△T 偏差＝0，且△△T 偏差＝0时，即冷媒散热管出口端和进口端的冷媒温差＝目标温差，发热器件温度合适；而且，偏差较为稳定，保持不变；因此，冷媒散热管内的冷媒流量恰当，需要保持电子膨胀阀4开度不变。
(3)当△T 偏差＞0，且△△T 偏差＞0时，即冷媒散热管出口端和进口端的冷媒温差＞目标温差，发热器件温度较高；而且，偏差在增大，因此，冷媒散热管内的冷媒流量不足，需要增大电子膨胀阀4开度。
(4)当△T 偏差＜0，且△△T 偏差＞0时，即冷媒散热管出口端和进口端的冷媒温差＜目标温差，发热器件温度过低；但是偏差在增大。
若-2℃＜△T 偏差＜0，即虽然冷媒温差＜目标温差，但是二者相差较小，而且，偏差在增大，因此，需要增大电子膨胀阀4开度。
若△T 偏差≤-2℃，即冷媒温差与目标温差，二者相差较大，即使偏差在增大，但是还是需要减小电子膨胀阀4开度。
(5)当△T 偏差＞0，且△△T 偏差＜0时，即冷媒散热管出口端和进口端的冷媒温差＞目标温差，发热器件温度较高；但是偏差在减小。
若0＜△T 偏差≤3℃，且△△T 偏差≤-2℃，即冷媒温差＞目标温差，但是二者相差不大，而且，偏差减小明显，因此，需要减小电子膨胀阀4开度。
若0＜△T 偏差≤3℃，且-2℃＜△△T 偏差＜0，即冷媒温差＞目标温差，而且，偏差减小不明显，因此，需要增大电子膨胀阀4开度。
若△T 偏差＞3℃，即冷媒温差＞目标温差，而且二者差距较大，因此，需要增大电子膨胀阀4开度。
因此，本实施例的方法，根据偏差、偏差变化率的具体取值范围，对电子膨胀阀4的开度进行增大或减小控制，既使得冷媒散热管的出口端与进口端的冷媒温差达到目标温差，保证散热效果，又避免频繁调节电子膨胀阀4的开度，保证运行稳定性。
下表中，以电子膨胀阀4满开度为1400步为例，举例说明了在偏差、偏差 变化率取不同值时，电子膨胀阀4开度增加或减小的步数。
Figure PCTCN2019073368-appb-000001
例如，当△T 偏差≤-5，且△△T 偏差≤-3时，电子膨胀阀4开度减小32步。当△T 偏差≥5，且△△T 偏差≥3时，电子膨胀阀4开度增加36步。
根据偏差及偏差变化率这两个因素调整电子膨胀阀4的开度，可以达到电子膨胀阀4的稳定调节，即可以在上次开度基础上增加或减少即可。如果不根据偏差和变化率调整开度，则电子膨胀阀4需要反复开启或关闭初始开度，再从初始开度调整，调节慢，效果差。
在空调运行过程中，还需要获取压缩机频率f，若f＝0，则控制电子膨胀阀4关闭、电磁阀SV2关闭。
基于上述空调散热结构控制方法的设计，本实施例还提出了一种空调散热结构控制系统，包括散热结构和控制系统。
所述散热结构包括冷媒散热管2和散热基板1，空调发热器件3与散热基板1固定，所述冷媒散热管2嵌入到散热基板1中；在散热基板1与冷媒散热管2的接触面上涂有导热介质，在散热基板1与空调发热器件3的接触面上也涂有导热介质。冷媒散热管2的进口端连接在室外换热器和室内换热器之间的液管上，冷媒散热管2的出口端连接气液分离器的进液管，在冷媒散热管2上 串联有电子膨胀阀4和电磁阀SV2。
所述控制系统包括空调发热器件温度获取模块、判断模块、冷媒温度获取模块、温差计算模块、修正模块、偏差计算模块、偏差变化率计算模块、开度调整模块等，参见图5所示。
空调发热器件温度获取模块，用于获取空调发热器件的实际温度Te。
判断模块，用于判断实际温度Te是否＞预设的最佳温度Te d；还用于判断实际温度Te是否＞预设的上限值Tmax；其中，Tmax＞Te d。
冷媒温度获取模块，用于获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out。
温差计算模块，用于计算温差△T 实际＝T out-T in。
修正模块，用于根据空调发热器件的实际温度Te确定修正值，对目标温差进行修正。
偏差计算模块，用于计算偏差△T 偏差＝△T 实际-△T 目标。
偏差变化率计算模块，用于计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；其中，△T 偏差′为上一周期计算出的偏差。
开度调整模块，用于调整电子膨胀阀开启至初始开度，还用于根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
具体的空调散热结构控制系统的工作过程，已经在上述空调散热结构控制方法中详述，此处不予赘述。
本实施例的空调散热结构控制系统，获取空调发热器件的实际温度Te，在Te＞预设的最佳温度Te d时，调整电子膨胀阀开启至初始开度；设定时间后，重新获取空调发热器件的实际温度Te；在实际温度Te＞预设的上限值Tmax时，每隔设定时间执行下述步骤：获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；计算温差△T 实际＝T out-T in；获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实际-△T 目标；计算偏差变化率△△T 偏差＝△T 偏差-△T 偏 差′；根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀4的开度，使得 冷媒散热管的出口端与进口端的冷媒温差达到目标温差，实现空调发热器件的良好散热，具有较好散热效果，保证空调发热器件的良好运行；而且，利用冷媒来对发热器件进行降温散热，散热成本低，提高了散热可靠性和稳定性，从而提高空调运转的可靠性和稳定性，解决了现有技术中散热可靠性差、散热成本高的问题。
以上实施例仅用以说明本发明的技术方案，而非对其进行限制；尽管参照前述实施例对本发明进行了详细的说明，对于本领域的普通技术人员来说，依然可以对前述实施例所记载的技术方案进行修改，或者对其中部分技术特征进行等同替换；而这些修改或替换，并不使相应技术方案的本质脱离本发明所要求保护的技术方案的精神和范围。

Claims (10)

  1. 一种空调散热结构控制方法，其特征在于：所述散热结构包括冷媒散热管，所述冷媒散热管与空调发热器件固定，所述冷媒散热管的进口端连接在室外换热器和室内换热器之间的液管上，所述冷媒散热管的出口端连接气液分离器的进液管，在所述冷媒散热管上串联有电子膨胀阀；
    所述控制方法包括：
    获取空调发热器件的实际温度Te，判断Te是否＞预设的最佳温度Te d；
    若是，则调整电子膨胀阀开启至初始开度；
    设定时间后，重新获取空调发热器件的实际温度Te；
    判断此时的实际温度Te是否＞预设的上限值Tmax；其中，Tmax＞Te d；
    若是，则每隔设定时间执行下述步骤：
    (1)获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；
    (2)计算温差△T 实际＝T out-T in；
    (3)获取预设的目标温差△T 目标，计算偏差△T 偏差＝△T 实际-△T 目标；
    (4)计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；
    其中，△T 偏差′为上一次计算出的偏差；
    (5)根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
  2. 根据权利要求1所述的方法，其特征在于：在步骤(3)中，获取预设的目标温差△T 目标之后，先根据空调发热器件的实际温度Te确定修正值，对目标温差进行修正，修正后的目标温差＝预设的目标温差△T 目标+修正值，然后根据修正后的目标温差计算偏差△T 偏差＝△T 实际-(△T 目标+修正值)。
  3. 根据权利要求2所述的方法，其特征在于：空调发热器件的实际温度Te越大，修正值越小，而且，
    当Te≥第二设定温度时，修正值＜0；
    当第一设定温度≤Te＜第二设定温度时，修正值＝0；
    当Te＜第一设定温度时，修正值＞0。
  4. 根据权利要求3所述的方法，其特征在于：
    当90℃≤Te＜100℃，修正值为-3℃；
    当80℃≤Te＜90℃，修正值为-2℃；
    当70℃≤Te＜80℃，修正值为-1℃；
    当60℃≤Te＜70℃，修正值为0；
    当50℃≤Te＜60℃，修正值为1℃；
    当40℃≤Te＜50℃，修正值为2℃。
  5. 根据权利要求1所述的方法，其特征在于：所述根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度，具体包括：
    (1)当△T 偏差＜0，且△△T 偏差＜0时，则减小电子膨胀阀开度；
    (2)当△T 偏差＝0，且△△T 偏差＝0时，则保持电子膨胀阀开度不变；
    (3)当△T 偏差＞0，且△△T 偏差＞0时，则增大电子膨胀阀开度；
    (4)当△T 偏差＜0，且△△T 偏差＞0时：
    若-2℃＜△T 偏差＜0，则增大电子膨胀阀开度；
    若△T 偏差≤-2℃，则减小电子膨胀阀开度；
    (5)当△T 偏差＞0，且△△T 偏差＜0时：
    若0＜△T 偏差≤3℃，且△△T 偏差≤-2℃，则减小电子膨胀阀开度；
    若0＜△T 偏差≤3℃，且-2℃＜△△T 偏差＜0，则增大电子膨胀阀开度；
    若△T 偏差＞3℃，则增大电子膨胀阀开度。
  6. 根据权利要求1所述的方法，其特征在于：Tmax＝Te d+5。
  7. 根据权利要求1所述的方法，其特征在于：所述初始开度为满开度的40％～60％。
  8. 根据权利要求1所述的方法，其特征在于：在所述冷媒散热管上还串联有电磁阀，用于控制冷媒散热管的通断。
  9. 根据权利要求1所述的方法，其特征在于：所述冷媒散热管通过散热基 板与空调发热器件固定，在散热基板与冷媒散热管的接触面上涂有导热介质，在散热基板与空调发热器件的接触面上也涂有导热介质。
  10. 一种空调散热结构控制系统，其特征在于：包括散热结构和控制系统；
    所述散热结构包括冷媒散热管和散热基板，所述空调发热器件与散热基板固定，所述冷媒散热管嵌入到散热基板中；在散热基板与冷媒散热管的接触面上涂有导热介质，在散热基板与空调发热器件的接触面上也涂有导热介质；
    所述冷媒散热管的进口端连接在室外换热器和室内换热器之间的液管上，所述冷媒散热管的出口端连接气液分离器的进液管，在所述冷媒散热管上串联有电子膨胀阀和电磁阀；
    所述控制系统包括：
    空调发热器件温度获取模块，用于获取空调发热器件的实际温度Te；
    判断模块，用于判断实际温度Te是否＞预设的最佳温度Te d；还用于判断实际温度Te是否＞预设的上限值Tmax；其中，Tmax＞Te d；
    冷媒温度获取模块，用于获取冷媒散热管进口端的冷媒温度T in和出口端的冷媒温度T out；
    温差计算模块，用于计算温差△T 实际＝T out-T in；
    修正模块，用于根据空调发热器件的实际温度Te确定修正值，对目标温差进行修正；
    偏差计算模块，用于计算偏差△T 偏差＝△T 实际-△T 目标；
    偏差变化率计算模块，用于计算偏差变化率△△T 偏差＝△T 偏差-△T 偏差′；其中，△T 偏差′为上一周期计算出的偏差；
    开度调整模块，用于调整电子膨胀阀开启至初始开度，还用于根据偏差△T 偏差、偏差变化率△△T 偏差调整电子膨胀阀的开度。
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