WO2018107982A1 - 一种电子膨胀阀的控制方法和装置以及制冷系统 - Google Patents

一种电子膨胀阀的控制方法和装置以及制冷系统 Download PDF

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Publication number
WO2018107982A1
WO2018107982A1 PCT/CN2017/114315 CN2017114315W WO2018107982A1 WO 2018107982 A1 WO2018107982 A1 WO 2018107982A1 CN 2017114315 W CN2017114315 W CN 2017114315W WO 2018107982 A1 WO2018107982 A1 WO 2018107982A1
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WIPO (PCT)
Prior art keywords
electronic expansion
expansion valve
value
opening
evaporator
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/CN2017/114315
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English (en)
French (fr)
Inventor
谷彦涛
王靖
张永
杨海涛
李峰
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Midea Group Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
Original Assignee
Midea Group Co Ltd
Chongqing Midea General Refrigeration Equipment Co Ltd
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Application filed by Midea Group Co Ltd, Chongqing Midea General Refrigeration Equipment Co Ltd filed Critical Midea Group Co Ltd
Priority to RU2019120164A priority Critical patent/RU2744305C2/ru
Priority to MYPI2019003296A priority patent/MY201322A/en
Publication of WO2018107982A1 publication Critical patent/WO2018107982A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion valves
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/25—Control of valves
    • F25B2600/2513—Expansion valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2115—Temperatures of a compressor or the drive means therefor
    • F25B2700/21151—Temperatures of a compressor or the drive means therefor at the suction side of the compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • 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 relates to the technical field of air conditioners, and in particular to a method and a device for controlling an electronic expansion valve and a refrigeration system.
  • the throttling structure commonly used in refrigeration systems includes orifice plates, thermal expansion valves, electronic expansion valves, etc. Due to the working principle, orifice plates and thermal expansion valves are not suitable for use in full-liquid and falling-film evaporators.
  • the electronic expansion valve is usually used as the throttling structure, which can realize the high precision and nearly linear refrigerant supply control.
  • the control method is generally to control the exhaust of the compressor. The degree of superheat is within a certain range.
  • exhaust superheat as a control target is that the operating conditions are different, the compressor load is different, and the most reasonable target value of the compressor superheat is greatly changed, resulting in the optimal supply of refrigerant into the evaporator.
  • the evaporator capacity cannot be fully utilized.
  • the technical problem to be solved by the present invention is to provide a control method and device for an electronic expansion valve and a refrigeration system by adjusting the opening degree of the electronic expansion valve to provide the most suitable liquid supply amount for the evaporator.
  • the temperature difference Tp of the heat exchange end of the evaporator is minimized to ensure that the heat transfer performance of the evaporator is fully exerted.
  • a control method of an electronic expansion valve Includes the following steps:
  • Step 1 obtaining the evaporator end temperature difference Tp;
  • Step 2 comparing the control target value Ts of the temperature difference between the Tp and the evaporator end to obtain a difference ⁇ Tp between the two;
  • Step 3 Determine the opening value of the electronic expansion valve according to the magnitude relationship between ⁇ Tp and the preset deviation value
  • Step 4 Control the opening degree of the electronic expansion valve to be adjusted to the opening value.
  • the beneficial effects of the invention are: by detecting the real-time value of the evaporator end temperature difference Tp, and comparing the Tp real-time value with the control target value Ts of the evaporator end temperature difference, if the difference ⁇ Tp is greater than the allowable deviation, then increasing The opening degree of the large valve, if the difference is less than the allowable deviation, reduce the opening degree of the valve, thereby adjusting the opening change of the electronic expansion valve, providing the most suitable liquid supply amount for the evaporator, and the temperature difference of the heat exchange end of the evaporator The Tp is minimized to ensure that the evaporator heat transfer performance is maximized.
  • the present invention can also be improved as follows.
  • step 1 further comprises: step 5, obtaining the outlet temperature Tout of the evaporator and the evaporation pressure Pe, and converting the evaporation pressure Pe into the evaporation temperature Te, wherein the difference between Tout and Te is Tp.
  • step 3 the method further includes:
  • Step 6 obtaining the suction temperature Tsuc of the compressor
  • Step 7 according to Tsuc and Te, determine the suction superheat degree Sh of the compressor
  • Step 8 When the current opening values of Te, Sh and the electronic expansion valve both meet the respective first preset conditions, the electronic expansion valve is controlled to perform a valve opening operation, and the opening degree of the electronic expansion valve is determined. Value, go to step 4.
  • the beneficial effects of adopting the above further solution are: detecting the subcooling degree of the condenser, and simultaneously using the heat exchange temperature difference and the supercooling degree as the control parameters, and also enabling the evaporator to fully exert its capability without excessively opening the valve.
  • the method further includes:
  • Step 9 Obtain the exhaust gas temperature Tdis of the compressor and the condensing pressure Pc of the condenser, and the cold The condensation pressure Pc is converted to a condensation temperature Tc;
  • Step 10 determining the exhaust superheat degree DSh of the compressor according to Tdis and Pc;
  • Step 11 After the first time of operation of the compressor, when the current opening values of the DSH and the electronic expansion valve both meet the respective second preset conditions, the electronic expansion valve is controlled to perform a valve closing action, and the The opening value of the electronic expansion valve and step 4 is performed.
  • the beneficial effects of adopting the above further solution are: detecting the subcooling degree of the condenser, and simultaneously using the heat exchange temperature difference and the supercooling degree as the control parameters, and also enabling the evaporator to fully exert its capability without excessively opening the valve.
  • the method further includes:
  • Step 12 When the current opening values of Te and the electronic expansion valve meet the respective third preset conditions, the electronic expansion valve is controlled to perform a valve closing action, and the opening degree of the electronic expansion valve is determined. And go to step 4.
  • the beneficial effect of using the above further solution is to prevent the evaporating temperature in the operation of the chiller from being too high, exceeding the operating range of the compressor.
  • the method further includes:
  • Step 13 After the preset time T is detected, when the Tout, Pe, and the load meet the respective fourth preset conditions in the preset time period t, the electronic expansion valve is controlled to perform the valve opening action, and the opening degree is adjusted to a first preset opening value, and simultaneously recording the evaporation pressure Pe1 at this time; or
  • Step 14 When at least one of Tout, Pe, and load does not satisfy the fourth preset condition thereof within the preset time period t, the electronic expansion valve is controlled to perform a valve opening action, and the opening of the electronic expansion valve is controlled.
  • the degree is adjusted to an opening value determined according to Te, Sh, and the current opening value of the electronic expansion valve.
  • the beneficial effect of adopting the above further solution is to prevent the low pressure of the unit from being low and low voltage protection during operation.
  • step 13 the method further includes:
  • Step 15 whether the difference of evaporation pressure before and after opening the valve is greater than the pressure pre-value P, and if so, it will evaporate
  • the dynamic correction value Pdt of the temperature difference at the end of the device is decreased by the first set value; otherwise, it is judged whether ⁇ Tp is greater than 0;
  • Step 16 When ⁇ Tp is greater than 0, increase Pdt by the first set value, and control the electronic expansion valve to perform a valve closing action to adjust the opening degree to a second preset opening value; or
  • Step 17 When ⁇ Tp is less than 0, the electronic expansion valve is controlled to perform a valve closing action, and the opening degree thereof is adjusted to a third preset opening degree value.
  • the advantageous effect of using the above further solution is to control the control target value Ts of the evaporator end temperature difference to the most suitable value by dynamic adjustment of the Pdt.
  • a control device for an electronic expansion valve comprising:
  • a processing module configured to compare a Tp obtained by the acquiring module with a control target value Ts of the evaporator end temperature difference, obtain a difference ⁇ Tp between the two, and determine an electronic expansion according to a magnitude relationship between the ⁇ Tp and the preset deviation value Valve opening value;
  • control module configured to control an opening degree of the electronic expansion valve to be adjusted to the opening value determined by the processing module.
  • the beneficial effects of the invention are: by detecting the real-time value of the evaporator end temperature difference Tp, and comparing the Tp real-time value with the control target value Ts of the evaporator end temperature difference, if the difference ⁇ Tp is greater than the allowable deviation, then increasing The opening degree of the large valve, if the difference is less than the allowable deviation, reduce the opening degree of the valve, thereby adjusting the opening change of the electronic expansion valve, providing the most suitable liquid supply amount for the evaporator, and the temperature difference of the heat exchange end of the evaporator The Tp is minimized to ensure that the evaporator heat transfer performance is maximized.
  • the present invention can also be improved as follows.
  • the obtaining module is further configured to acquire the water outlet temperature Tout and the evaporation pressure Pe of the evaporator, and convert the evaporation pressure Pe into the evaporation temperature Te, and the difference between Tout and Te is Tp.
  • the obtaining module is further configured to acquire an intake air temperature Tsuc of the compressor;
  • the processing module is further configured to determine an intake superheat degree Sh of the compressor according to Tsuc and Te, and determine the electronic expansion a valve opening value;
  • the control module is further configured to control the electronic expansion valve to perform a valve opening action when the current opening values of Te, Sh, and the electronic expansion valve both meet respective first preset conditions, And controlling the opening degree of the electronic expansion valve to be adjusted to the opening value determined by the processing module.
  • the acquisition module is further configured to acquire the exhaust gas temperature Tdis and condensation of the compressor.
  • the processing module is further configured to determine the exhaust superheat degree DSh of the compressor according to Tdis and Pc, and determine the opening of the electronic expansion valve
  • the control module is further configured to control the electronic expansion valve to execute after the first time of operation of the compressor, when the current opening values of the DSH and the electronic expansion valve satisfy the respective second preset conditions The valve acts and controls the opening of the electronic expansion valve to be adjusted to the opening value determined by the processing module.
  • control module is further configured to: when the current opening value of the Te and the electronic expansion valve are both When the respective third preset conditions are met, the electronic expansion valve is controlled to perform a valve closing action, and the opening degree of the electronic expansion valve is controlled to be adjusted to the opening value determined by the processing module.
  • control module is further configured to detect the Tout within the preset time period t every interval preset time T
  • the electronic expansion valve is controlled to perform the valve opening action, and the opening degree is adjusted to the first preset opening degree value, and the evaporation pressure Pe1 at this time is recorded;
  • control module is further configured to: when the at least one of Tout, Pe, and load does not satisfy the fourth preset condition thereof in the preset time period t, control the electronic expansion valve to perform a valve opening action, and control the The opening degree of the electronic expansion valve is adjusted to an opening value determined according to Te, Sh, and the current opening value of the electronic expansion valve.
  • the processing module is further configured to determine whether the difference of the evaporation pressure before and after the valve opening is greater than the pressure pre-value P, and if so, reduce the dynamic correction value Pdt of the evaporator end temperature difference by the first set value; otherwise, Determining whether ⁇ Tp is greater than 0, and when ⁇ Tp is greater than 0, increasing Pdt by the first set value;
  • the control module is further configured to: when ⁇ Tp is greater than 0, control the electronic expansion valve to perform a valve closing action, and adjust an opening degree thereof to a second preset opening degree value; or, when ⁇ Tp is less than 0, control the electron
  • the expansion valve performs a valve closing action to adjust its opening degree to a third preset opening value.
  • a refrigeration system comprising: a compressor 101, a condenser 102, an electronic expansion valve 104, and an evaporator 103 connected in sequence, as described in any of the above embodiments.
  • Control device 100 and a first temperature sensor 105, a first pressure sensor 106, a second pressure sensor 107, a second temperature sensor 108, and a third temperature sensor 109 respectively connected to the control device 100, wherein the compression
  • the machine 101 is also connected to the evaporator 103;
  • the first temperature sensor 105 is disposed on a pipeline connecting the evaporator 103 and the condenser 102, for detecting the exhaust gas temperature Tdis of the compressor 101, and transmitting Tdis to the control device 100;
  • the second temperature sensor 108 is disposed on the pipeline connecting the evaporator 103 and the compressor 101, for detecting the intake air temperature Tsuru of the compressor 101, and transmitting the Tsuuc to the control device 100;
  • the third temperature sensor 109 is disposed on the outlet pipe of the evaporator 103 for detecting the evaporator outlet water temperature Tout, and transmits Tout to the control device 100;
  • the first pressure sensor 106 is disposed on the condenser 102 for detecting the condensation pressure Pc of the condenser 102, and transmitting Pc to the control device 100;
  • the second pressure sensor 107 is disposed on the evaporator 103 for detecting the evaporation pressure Pe of the evaporator 103, and transmitting Pe to the control device 100;
  • the control device 100 is configured to receive Tdis, Tsuc, Tout, Pc, and Pe, and convert Pc and Pe into a saturated condensation temperature Tc and a saturated evaporation temperature Te, respectively, and according to Tdis, Tsuc, Tout, Tc, and Te, and
  • the control target value Ts of the evaporator end temperature difference is obtained as a difference ⁇ Tp between the two, and the opening degree value of the electronic expansion valve is determined according to the magnitude relationship between ⁇ Tp and the preset deviation value, and the electronic expansion valve is controlled.
  • the opening degree of 104 is adjusted to the opening value.
  • FIG. 1 is a schematic flowchart of a method for controlling an electronic expansion valve according to an embodiment of the present invention
  • FIG. 2 is a schematic flowchart of a method for controlling an electronic expansion valve according to another embodiment of the present invention.
  • FIG. 3 is a schematic flowchart of a method for controlling an electronic expansion valve according to another embodiment of the present invention.
  • FIG. 4 is a schematic structural block diagram of a control device for an electronic expansion valve according to an embodiment of the present invention.
  • FIG. 5 is a schematic structural block diagram of a refrigeration system according to an embodiment of the present invention.
  • a control method 200 for an electronic expansion valve as shown in FIG. 1 includes:
  • the preset offset value may be 0.2 or 0.3, and the set value SP16 may be 0.18.
  • the value of the set value needs to consider factors such as whether the system is susceptible to fluctuations and the length of the system stabilization time.
  • the value of the set value is too large to be fluctuating, and when the value is too small, the system is stable. long.
  • Pdt is the dynamic correction value of the end temperature difference. This value is a dynamically changing value. Each period changes once. The latest updated value is taken during calculation. The initial value is 0 to ensure that the control target value Ts matches the current state of the unit.
  • the control method of the electronic expansion valve is to compare the real-time value of the temperature difference Tp of the evaporator end, and compare the real-time value of Tp with the control target value Ts of the temperature difference of the evaporator end, if the difference between the two is ⁇ Tp If the deviation is greater than the allowable deviation, the opening degree of the valve is increased. If the difference is less than the allowable deviation, the opening degree of the valve is decreased, thereby adjusting the opening change of the electronic expansion valve to provide the most suitable liquid supply amount for the evaporator.
  • the temperature difference Tp of the heat exchange end of the evaporator is minimized to ensure that the heat transfer performance of the evaporator is maximized.
  • control method 200 before step 201, the control method 200 further includes:
  • control method 200 further includes:
  • EXV_MOV preset opening value SP13 +2.5.
  • step 212 After the first time of running the compressor, determine whether the current opening value EXV_PCT of the DSh and the electronic expansion valve meets the respective second preset conditions, namely: DSh ⁇ exhaust superheat limit value DSH_LIM+ fourth preset value SP4 And EXV_PCT> fifth preset value SP5, if yes, perform step 213 and step 204; otherwise, when: DSh ⁇ DSH_LIM+SP4 and/or EXV_PCT ⁇ SP5, step 214 is performed.
  • step 214 Determine whether the current opening value EXV_PCT of the Te and the electronic expansion valve meets the respective third preset conditions, that is, Te ⁇ high evaporation temperature protection activation threshold MOP_LIM, and EXV_PCT>the sixth preset value SP6, if yes, Then, step 215 and step 204 are performed; otherwise, when Te ⁇ MOP_LIM and/or EXV_PCT ⁇ SP6, step 216 is performed.
  • step 217 Detecting whether the Tout, Pe, and the load meet the respective fourth preset conditions in the preset time period t, that is, whether the fluctuation of Tout is less than 0.3° C. and Pe in the preset time period t ⁇ seventh preset value SP7, and whether the load fluctuation is less than 5%, and if yes, step 217 is performed; otherwise, that: the fluctuation of Tout is greater than 0.3 ° C, Pe>SP7, load fluctuation greater than 5% in the preset time period t When at least one of them is satisfied, step 218 and step 204 are performed.
  • the preset time T may take 5 minutes, and the preset time period t may take 1 minute, that is, the Tout, Pe, and the load may be inspected once every 5 minutes, and the inspection time is 1 min.
  • the method 200 is controlled. It can also include:
  • step 220 is performed; otherwise, step 221 is performed.
  • the dynamic correction value Pdt of the temperature difference at the end of the evaporator is decreased by the first set value SP10. That is to say, the dynamic correction value Pdt is reduced by SP10 on the original basis, preparing for the subsequent reduction of the control target value Ts and opening the valve, and then entering the next cycle.
  • the second preset opening degree value the first preset opening degree value SP8+the preset opening degree value SP11. That is to say, the dynamic correction value Pdt is increased by SP10 on the original basis, and the valve closing action (SP8+SP11) is performed to prepare for the subsequent increase of the control target value Ts and the closing of the valve, and then proceeds to the next cycle.
  • the third preset opening value the first preset opening value SP8+the preset opening degree value SP12. That is to say, if the current Tp value is not greater than the control target value Ts, only the valve closing action (SP8+SP12) is performed, the control target value is not adjusted, and then the next cycle is entered.
  • the valve in the case that the unit load and the working condition are basically stable, the valve is opened to the first preset opening value SP8 every preset time interval, and the real-time value Tp value of the valve rear end temperature difference is opened. If it is not reduced, the evaporation pressure Pe does not increase, then the current Tp value has reached the minimum value. Continued valve opening can only cause the subcooling degree to decrease, and then Pdt is increased by SP10, and the valve is slowly closed to increase the unit's subcooling degree. .
  • the method for controlling an electronic expansion valve provided in the above embodiment by detecting the degree of subcooling of the condenser, at the same time, using the heat exchange temperature difference and the supercooling degree as the control parameters, the evaporator can fully exert its capabilities, ensure the full design capability of the unit, improve the energy efficiency of the unit and the stability of the operation, and not excessively open the valve, effectively preventing the unit.
  • the low pressure is too low and the low pressure protection is reported.
  • the suction and liquid bring the oil to damage the compressor, and the evaporation temperature is too high, causing the compressor to run oil and the current is too large.
  • the size of the sequence numbers of the foregoing processes does not mean the order of execution sequence, and the execution order of each process should be determined by its function and internal logic, and should not be implemented in the embodiments of the present invention.
  • the process constitutes any limitation.
  • control method of the electronic expansion valve provided by the embodiment of the present invention is described in detail with reference to FIG. 1 to FIG. 3 .
  • the control device of the electronic expansion valve provided by the embodiment of the present invention is described in detail below with reference to FIG. 4 . description.
  • the present invention also provides a control device for an electronic expansion valve.
  • the control device 100 includes an acquisition module 110, a processing module 120, and a control module 130. among them,
  • the acquisition module 110 is configured to obtain an evaporator end temperature difference Tp.
  • the processing module 120 is configured to compare the Tp and the control target value Ts of the evaporator end temperature difference obtained by the obtaining module 110 to obtain a difference ⁇ Tp therebetween, and determine the opening of the electronic expansion valve according to the magnitude relationship between the ⁇ Tp and the preset deviation value. Degree value.
  • the control module 130 is configured to control the opening degree adjustment of the electronic expansion valve to the opening value determined by the processing module 120.
  • control device 100 may correspond to the execution body of the control method 200 according to the embodiment of the present invention, and the above and other operations of the respective modules in the control device 100
  • the details of the respective processes in FIG. 1 to FIG. 3 are not described here.
  • the control device for an electronic expansion valve compares the real-time value of the temperature difference Tp of the evaporator end, and compares the real-time value of Tp with the control target value Ts of the temperature difference of the evaporator end, if the difference between the two is ⁇ If Tp is greater than the allowable deviation, the opening degree of the valve is increased. If the difference is less than the allowable deviation, the opening degree of the valve is reduced, thereby adjusting the opening change of the electronic expansion valve to provide the most suitable liquid supply amount for the evaporator. , The temperature difference Tp of the heat exchange end of the evaporator is minimized to ensure that the heat transfer performance of the evaporator is maximized.
  • the obtaining module 110 is further configured to acquire the water outlet temperature Tout and the evaporation pressure Pe of the evaporator, and convert the evaporation pressure Pe into the evaporation temperature Te, and the difference between Tout and Te is Tp.
  • the acquisition module 110 is further configured to acquire an inspiratory temperature Tsuc of the compressor.
  • the processing module 120 is further configured to determine an intake superheat degree Sh of the compressor according to Tsuc and Te, and determine an opening degree value of the electronic expansion valve.
  • the control module 130 is further configured to control the electronic expansion valve to perform a valve opening action when the current opening values of the Te, Sh, and the electronic expansion valves meet the respective first preset conditions, and control the opening degree of the electronic expansion valve to be adjusted to be processed.
  • the opening value determined by module 120 is further configured to acquire an inspiratory temperature Tsuc of the compressor.
  • the processing module 120 is further configured to determine an intake superheat degree Sh of the compressor according to Tsuc and Te, and determine an opening degree value of the electronic expansion valve.
  • the control module 130 is further configured to control the electronic expansion valve to perform a valve opening action when the current opening values of the Te, Sh, and the electronic expansion valves meet the respective first preset conditions, and control the opening degree of the electronic expansion valve
  • the obtaining module 110 is further configured to acquire the row of the compressor.
  • the gas temperature Tdis and the condenser condensing pressure Pc, and the condensing pressure Pc are converted into the condensing temperature Tc.
  • the processing module 120 is further configured to determine an exhaust superheat degree DSh of the compressor according to Tdis and Pc, and determine an opening degree value of the electronic expansion valve.
  • the control module 130 is further configured to control the electronic expansion valve to perform a valve closing action and control the electronic expansion valve after the first time of operation of the compressor, when the current opening values of the DSH and the electronic expansion valve satisfy the respective second preset conditions.
  • the opening is adjusted to the opening value determined by the processing module 120.
  • control module 130 when the current opening value of the DSh and/or the electronic expansion valve does not satisfy the respective second preset condition, the control module 130 is further configured to open the current of the Te and the electronic expansion valve.
  • the electronic expansion valve is controlled to perform the valve closing action, and the opening degree of the electronic expansion valve is controlled to be adjusted to the opening value determined by the processing module.
  • control module 130 when the current opening value of the Te and/or the electronic expansion valve does not meet the respective third preset condition, the control module 130 is further configured to detect the preset time T every interval. Set time When the Tout, Pe and the load in the segment t satisfy the respective fourth preset conditions, the electronic expansion valve is controlled to perform the valve opening action, and the opening degree is adjusted to the first preset opening degree value, and the evaporation pressure at this time is recorded. Pe1.
  • control module 130 is further configured to control the electronic expansion valve to perform a valve opening action and control the electronic expansion valve when at least one of Tout, Pe, and load does not satisfy the fourth preset condition thereof within the preset time period t
  • the opening degree is adjusted to an opening value determined according to the current opening values of Te, Sh, and the electronic expansion valve.
  • the processing module 120 is further configured to determine whether the difference between the evaporation pressures before and after the valve opening is greater than the pressure pre-value P, and if so, the dynamic correction value Pdt of the evaporator end temperature difference is decreased. A set value. Otherwise, it is judged whether ⁇ Tp is greater than 0, and when ⁇ Tp is greater than 0, Pdt is increased by the first set value.
  • the control module 130 is further configured to control the electronic expansion valve to perform a valve closing action when ⁇ Tp is greater than 0, and adjust the opening degree to a second preset opening value. Alternatively, when ⁇ Tp is less than 0, the electronic expansion valve is controlled to perform a valve closing action, and the opening degree thereof is adjusted to a third preset opening degree value.
  • the present invention also provides a refrigeration system, as shown in FIG. 5, the refrigeration system includes: the control device 100 as described in any of the above embodiments, the compressor 101, the condenser 102, and the electronic expansion valve 104 sequentially connected And the evaporator 103, and the first temperature sensor 105, the first pressure sensor 106, the second pressure sensor 107, the second temperature sensor 108, and the third temperature sensor 109 respectively connected to the control device 100, and the compressor 101 is also evaporated
  • the device 103 is connected.
  • the first temperature sensor 105 is disposed on a line connecting the evaporator 103 and the condenser 102 for detecting the exhaust gas temperature Tdis of the compressor 101 and transmitting the Tdis to the control device 100.
  • the second temperature sensor 108 is disposed on a line connecting the evaporator 103 and the compressor 101 for detecting the intake air temperature Tsuu of the compressor 101 and transmitting the Tsuuc to the control device 100.
  • the third temperature sensor 109 is disposed on the outlet pipe of the evaporator 103 for detecting the evaporator outlet water temperature Tout and transmitting Tout to the control device 100.
  • the first pressure sensor 106 is disposed on the condenser 102 for detecting the condensing pressure Pc of the condenser 102 and transmitting the Pc to the control device 100.
  • the second pressure sensor 107 is disposed at the evaporator 103 Upper, for detecting the evaporation pressure Pe of the evaporator 103, and transmitting Pe to the control device 100.
  • the control device 100 is configured to receive Tdis, Tsuc, Tout, Pc, and Pe, and convert Pc and Pe into a saturated condensation temperature Tc and a saturated evaporation temperature Te, respectively, and according to Tdis, Tsuc, Tout, Tc, and Te, and an evaporator
  • the control target value Ts of the end temperature difference is obtained as the difference ⁇ Tp between the two, and the opening degree of the electronic expansion valve is determined according to the magnitude relationship between ⁇ Tp and the preset deviation value, and the opening degree of the electronic expansion valve 104 is controlled to be adjusted to the opening degree. value.
  • the control device 100 obtains the difference ⁇ Tp between the two according to the control target value Ts according to Tdis, Tsuc, Tout, Tc, and Te, and the temperature difference of the evaporator end, and according to ⁇ Tp and the pre- The magnitude relationship of the deviation values is determined, the opening degree value of the electronic expansion valve is determined, and the process and method for controlling the opening degree of the electronic expansion valve 104 to adjust to the opening degree value adopt the control method 200 described above, and for the sake of simplicity of description, no longer Narration.
  • the disclosed systems, devices, and methods can be implemented in other ways.
  • the device embodiments described above are merely illustrative.
  • the division of cells is only a logical function division.
  • multiple units or components may be combined or integrated. Go to another system, or some features can be ignored or not executed.
  • the mutual coupling or direct coupling or communication connection shown or discussed may be an indirect coupling or communication connection through some interface, device or unit, or an electrical, mechanical or other form of connection.
  • the units described as separate components may or may not be physically separate, and the components displayed as units may or may not be physical units, that is, may be located in one place, or may be distributed to multiple network units. Some or all of the units may be selected according to actual needs to achieve the objectives of the embodiments of the present invention.
  • each functional unit in each embodiment of the present invention may be integrated into one processing unit, or each unit may exist physically separately, or two or more units may be integrated into one unit.
  • the above integrated unit can be implemented in the form of hardware or in the form of a software functional unit.
  • An integrated unit if implemented in the form of a software functional unit and sold or used as a standalone product, can be stored in a computer readable storage medium.
  • the technical solution of the present invention contributes in essence or to the prior art, or all or part of the technical solution may be embodied in the form of a software product stored in a storage medium.
  • a number of instructions are included to cause a computer device (which may be a personal computer, server, or network device, etc.) to perform all or part of the steps of the various embodiments of the present invention.
  • the foregoing storage medium includes: a U disk, a mobile hard disk, a read-only memory (ROM), a random access memory (RAM), a magnetic disk, or an optical disk, and the like. .

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Abstract

一种电子膨胀阀的控制方法、装置以及制冷系统，控制方法包括：获取蒸发器端部温差Tp；比较Tp和蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp；根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值；控制电子膨胀阀的开度调节至确定的开度值。该方法中通过检测蒸发器端温差Tp的实时值，并将Tp实时值与蒸发器端温差的控制目标值Ts相比较，若二者差值△Tp大于允许的偏差，则增大阀的开度，若差值小于允许的偏差，则减小阀的开度，从而调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量，将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥

Description

一种电子膨胀阀的控制方法和装置以及制冷系统
相关申请的交叉引用
本申请基于申请号为201611141505.5，申请日为2016年12月12日的中国专利申请提出，并要求该中国专利申请的优先权，该中国专利申请的全部内容在此引入本申请作为参考。
技术领域
本发明涉及空调技术领域，尤其涉及一种电子膨胀阀的控制方法和装置以及制冷系统。
背景技术
制冷系统常用的节流结构有孔板、热力膨胀阀、电子膨胀阀等，由于工作原理的原因，孔板、热力膨胀阀并不适用用于满液、降膜蒸发器。对于采用满液、降膜蒸发器的制冷循环系统，通常采用电子膨胀阀作为节流结构，可实现较高精度的近似线性的制冷剂供液量控制，控制方法一般为控制压缩机的排气过热度在一定范围内。
而将排气过热度作为控制目标的局限在于：运行工况不同，压缩机负荷不同，压缩机排气过热度最合理的目标值变化很大，导致进入蒸发器冷媒供液量无法达到最佳，蒸发器能力不能充分发挥。
发明内容
本发明所要解决的技术问题是针对现有技术的不足，提供一种电子膨胀阀的控制方法和装置以及制冷系统，通过调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量，将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥。
本发明解决上述技术问题的技术方案如下：一种电子膨胀阀的控制方法， 包括以下步骤：
步骤1、获取蒸发器端部温差Tp；
步骤2、比较Tp和所述蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp；
步骤3、根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值；
步骤4、控制所述电子膨胀阀的开度调节至所述开度值。
本发明的有益效果是：通过检测蒸发器端温差Tp的实时值，并将Tp实时值与蒸发器端温差的控制目标值Ts相比较，若二者差值△Tp大于允许的偏差，则增大阀的开度，若差值小于允许的偏差，则减小阀的开度，从而调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量，将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥。
在上述技术方案的基础上，本发明还可以做如下改进。
进一步地，在步骤1之前，还包括：步骤5、获取蒸发器的出水温度Tout和蒸发压力Pe，并将所述蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp。
进一步地，在步骤3之后，还包括：
步骤6、获取压缩机的吸气温度Tsuc；
步骤7、根据Tsuc和Te，确定压缩机的吸气过热度Sh；
步骤8、当Te、Sh和所述电子膨胀阀的当前开度值均满足各自的第一预设条件时，控制所述电子膨胀阀执行开阀动作，并确定所述电子膨胀阀的开度值，执行步骤4。
采用上述进一步方案的有益效果是：检测冷凝器过冷度，同时使用换热温差、过冷度作为控制参数，也可以使蒸发器充分发挥能力，又不至于过度开阀。
进一步地，当Te、Sh和所述电子膨胀阀的当前开度值中的至少一个不满足其的第一预设条件时，还包括：
步骤9、获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将所述冷 凝压力Pc转换为冷凝温度Tc；
步骤10、根据Tdis和Pc，确定压缩机的排气过热度DSh；
步骤11、压缩机运行第一时间后，当DSh和所述电子膨胀阀的当前开度值均满足各自的第二预设条件时，控制所述电子膨胀阀执行关阀动作，并确定所述电子膨胀阀的开度值，并执行步骤4。
采用上述进一步方案的有益效果是：检测冷凝器过冷度，同时使用换热温差、过冷度作为控制参数，也可以使蒸发器充分发挥能力，又不至于过度开阀。
进一步地，当DSh和/或所述电子膨胀阀的当前开度值不满足各自的第二预设条件时，还包括：
步骤12、当Te和所述电子膨胀阀的当前开度值均满足各自的第三预设条件时，控制所述电子膨胀阀执行关阀动作，并确定所述电子膨胀阀的开度值，并执行步骤4。
采用上述进一步方案的有益效果是：防止冷水机组运行中蒸发温度过高，超出压缩机运行范围。
进一步地，当Te和/或所述电子膨胀阀的当前开度值不满足各自的第三预设条件时，还包括：
步骤13、每间隔预设时间T，检测预设时段t内Tout、Pe和负荷均满足各自的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值，同时记录此时的蒸发压力Pe1；或者，
步骤14、当在预设时段t内Tout、Pe和负荷中的至少一个不满足其的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至根据Te、Sh和所述电子膨胀阀的当前开度值确定的开度值。
采用上述进一步方案的有益效果是：防止机组在运行过程中出现低压过低而报低压保护。
进一步地，在步骤13之后，还包括：
步骤15、开阀前后蒸发压力的差值是否大于压力预值P，若是，则将蒸发 器端部温差的动态修正值Pdt减小第一设定值；否则，判断ΔTp是否大于0；
步骤16、当ΔTp大于0时，将Pdt增加所述第一设定值，并控制所述电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值；或者，
步骤17、当ΔTp小于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。
采用上述进一步方案的有益效果是：通过Pdt的动态调整，将蒸发器端部温差的控制目标值Ts控制在最合适的值。
本发明解决上述技术问题的另一种技术方案如下：一种电子膨胀阀的控制装置，包括：
获取模块，用于获取蒸发器端部温差Tp；
处理模块，用于比较所述获取模块获取的Tp和所述蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值；
控制模块，用于控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
本发明的有益效果是：通过检测蒸发器端温差Tp的实时值，并将Tp实时值与蒸发器端温差的控制目标值Ts相比较，若二者差值△Tp大于允许的偏差，则增大阀的开度，若差值小于允许的偏差，则减小阀的开度，从而调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量，将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥。
在上述技术方案的基础上，本发明还可以做如下改进。
进一步地，所述获取模块还用于获取蒸发器的出水温度Tout和蒸发压力Pe，并将所述蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp。
进一步地，所述获取模块还用于获取压缩机的吸气温度Tsuc；所述处理模块还用于根据Tsuc和Te，确定压缩机的吸气过热度Sh，并确定所述电子膨胀 阀的开度值；所述控制模块还用于当Te、Sh和所述电子膨胀阀的当前开度值均满足各自的第一预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
进一步地，当Te、Sh和所述电子膨胀阀的当前开度值中的至少一个不满足其的第一预设条件时，所述获取模块还用于获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将所述冷凝压力Pc转换为冷凝温度Tc；所述处理模块还用于根据Tdis和Pc，确定压缩机的排气过热度DSh，并确定所述电子膨胀阀的开度值；所述控制模块还用于压缩机运行第一时间后，当DSh和所述电子膨胀阀的当前开度值均满足各自的第二预设条件时，控制所述电子膨胀阀执行关阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
进一步地，当DSh和/或所述电子膨胀阀的当前开度值不满足各自的第二预设条件时，所述控制模块还用于当Te和所述电子膨胀阀的当前开度值均满足各自的第三预设条件时，控制所述电子膨胀阀执行关阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
进一步地，当Te和/或所述电子膨胀阀的当前开度值不满足各自的第三预设条件时，所述控制模块还用于每间隔预设时间T，检测预设时段t内Tout、Pe和负荷均满足各自的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值，同时记录此时的蒸发压力Pe1；
或者，所述控制模块还用于当在预设时段t内Tout、Pe和负荷中的至少一个不满足其的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至根据Te、Sh和所述电子膨胀阀的当前开度值确定的开度值。
进一步地，所述处理模块还用于判断开阀前后蒸发压力的差值是否大于压力预值P，若是，则将蒸发器端部温差的动态修正值Pdt减小第一设定值；否则，判断ΔTp是否大于0，且当ΔTp大于0时，将Pdt增加所述第一设定值； 所述控制模块还用于当ΔTp大于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值；或者，当ΔTp小于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。
本发明解决上述技术问题的另一种技术方案如下：一种制冷系统，包括：依次连接的压缩机101、冷凝器102、电子膨胀阀104和蒸发器103，如上述任一实施例中所述的控制装置100，以及分别与所述控制装置100连接的第一温度传感器105、第一压力传感器106、第二压力传感器107、第二温度传感器108和第三温度传感器109，其中，所述压缩机101还与所述蒸发器103连接；
所述第一温度传感器105设置在连接所述蒸发器103和所述冷凝器102的管路上，用于检测压缩机101的排气温度Tdis，并将Tdis传输至所述控制装置100；
所述第二温度传感器108设置在连接所述蒸发器103和所述压缩机101的管路上，用于检测压缩机101的吸气温度Tsuc，并将Tsuc传输至所述控制装置100；
所述第三温度传感器109设置在所述蒸发器103的出水管路上，用于检测蒸发器出水温度Tout，并将Tout传输至所述控制装置100；
所述第一压力传感器106设置在所述冷凝器102上，用于检测所述冷凝器102的冷凝压力Pc，并将Pc传输至所述控制装置100；
所述第二压力传感器107设置在所述蒸发器103上，用于检测所述蒸发器103的蒸发压力Pe，并将Pe传输至所述控制装置100；
所述控制装置100，用于接收Tdis、Tsuc、Tout、Pc和Pe，并将Pc和Pe分别转换为饱和冷凝温度Tc和饱和蒸发温度Te，且根据Tdis、Tsuc、Tout、Tc和Te，以及所述蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定所述电子膨胀阀的开度值，控制所述电子膨胀阀104的开度调节至所述开度值。
本发明附加的方面的优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本发明实践了解到。
附图说明
为了更清楚地说明本发明实施例的技术方案，下面将对本发明实施例或现有技术描述中所需要使用的附图作简单地介绍，显而易见地，下面所描述的附图仅仅是本发明的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本发明实施例提供的一种电子膨胀阀的控制方法的示意性流程图；
图2为本发明另一实施例提供的一种电子膨胀阀的控制方法的示意性流程图；
图3为本发明另一实施例提供的一种电子膨胀阀的控制方法的示意性流程图；
图4为本发明实施例提供的一种电子膨胀阀的控制装置的示意性结构框图；
图5为本发明实施例提供的一种制冷系统的示意性结构框图。
具体实施方式
下面将结合本发明实施例中的附图，对本发明实施例中的技术方案进行清楚、完整地描述，显然，所描述的实施例是本发明的一部分实施例，而不是全部实施例。基于本发明中的实施例，本领域普通技术人员在没有做出创造性劳动的前提下所获得的所有其他实施例，都应属于本发明保护的范围。
如图1所示的一种电子膨胀阀的控制方法200，包括：
201、获取蒸发器端部温差Tp。
202、比较Tp和蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，即：ΔTp＝Tp-Ts。
203、根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值。
204、控制电子膨胀阀的开度调节至确定的开度值。
具体的，在该实施例中，步骤203中确定电子膨胀阀的开度值的具体过程可以如下所述：当△Tp<预设偏差值时，电子膨胀阀的开度值EXV_MOV＝(△Tp)*设定值SP16；当△Tp>预设偏差值时，电子膨胀阀的开度值EXV_MOV＝(△Tp-预设偏差值)*设定值SP16。例如，在该实施例中，预设偏差值可以取0.2或者0.3，设定值SP16可以取0.18。
需要说明的是，在该实施例中设定值的取值需要考虑对系统是否容易造成波动和系统稳定时间长短等因素，设定值取值过大容易波动，过小则导致系统稳定时间过长。
应理解，在该实施例中，蒸发器端部温差的控制目标值Ts＝Pinch_SP+动态修正值Pdt，其中，Pinch_SP为蒸发器端部温差的设定目标值，通常是针对国标满负荷工况来确定这个值。设定目标值Pinch_SP并不一定是机组当前运行的最合理目标值。若Pinch_SP偏大，电子膨胀阀开度会比较小，蒸发器性能无法充分利用；若Pinch_SP偏小，电子膨胀阀会持续开阀，可能导致蒸发压力无法提升，过冷度却持续下降，也会降低整机性能，过度的开阀也可能导致机组排气温度降低，甚至有带液的风险。Pdt为端部温差的动态修正值，这个值是一个动态变化的值，每个周期变化一次，计算时取最新更新的值，初始值为0，以保证控制目标值Ts匹配机组当前的状态。
上述实施例提供的一种电子膨胀阀的控制方法，通过检测蒸发器端温差Tp的实时值，并将Tp实时值与蒸发器端温差的控制目标值Ts相比较，若二者差值△Tp大于允许的偏差，则增大阀的开度，若差值小于允许的偏差，则减小阀的开度，从而调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量，将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥。
可选地，在一个实施例中，如图2所示，在步骤201之前，控制方法200还包括：
205、获取蒸发器的出水温度Tout和蒸发压力Pe，并将蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp，即：Tp＝Tout-Te。
可选地，在另一个实施例中，如图3所示，在步骤203之后，控制方法200还包括：
206、获取压缩机的吸气温度Tsuc。
207、根据Tsuc和Te，确定压缩机的吸气过热度Sh，即：Sh＝Tsuc－Te。
208、判断Te、Sh和电子膨胀阀的当前开度值EXV_PCT是否均满足各自的第一预设条件，即：Te<第一预设值SP1、且Sh>第二预设值SP2、且EXV_PCT<第三预设值SP3，若是，则执行步骤209和步骤204；否则，即：Te<SP1、Sh>SP2和EXV_PCT<SP3中的至少一个条件不满足时，执行步骤210-212。
209、控制电子膨胀阀执行开阀动作，并重新确定电子膨胀阀的开度值。
具体的，在该实施例中，当蒸发压力偏低且吸气过热度偏大时，需要加快开阀，可以通过以下公式重新确定电子膨胀阀的开度值，EXV_MOV＝预设开度值SP13+2.5。
210、获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将冷凝压力Pc转换为冷凝温度Tc。
211、根据Tdis和Pc，确定压缩机的排气过热度DSh。
212、压缩机运行第一时间后，判断DSh和电子膨胀阀的当前开度值EXV_PCT是否均满足各自的第二预设条件，即：DSh<排气过热度限定值DSH_LIM+第四预设值SP4、且EXV_PCT>第五预设值SP5，若是，则执行步骤213和步骤204；否则，即：DSh≥DSH_LIM+SP4和/或EXV_PCT≤SP5时，执行步骤214。
213、控制电子膨胀阀执行关阀动作，并重新确定电子膨胀阀的开度值。
具体的，在该实施例中，压缩机启动完成后，排气过热度偏低，需要关阀，可以通过以下公式重新确定电子膨胀阀的开度值，EXV_MOV＝(DSH_Err排气 过热度偏差+预设开度值SP14)*0.27，其中，DSH_Err为排气过热度DSH与排气过热度限定值DSH_LIM的差值。
214、判断Te和电子膨胀阀的当前开度值EXV_PCT是否均满足各自的第三预设条件，即：Te≥高蒸发温度保护激活阀值MOP_LIM、且EXV_PCT>第六预设值SP6，若是，则执行步骤215和步骤204；否则，即：Te<MOP_LIM和/或EXV_PCT≤SP6时，执行步骤216。
215、控制电子膨胀阀执行关阀动作，并重新确定电子膨胀阀的开度值。
具体的，在该实施例中，压缩机启动完成后，蒸发温度超出压缩机允许范，需要关阀，可以通过以下公式重新确定电子膨胀阀的开度值，EXV_MOV＝(MOP_LIM-Te)*预设开度值SP15。
216、每间隔预设时间T，检测预设时段t内Tout、Pe和负荷是否均满足各自的第四预设条件，即：在预设时间段t内Tout的波动是否小于0.3℃、且Pe≤第七预设值SP7、且负荷波动是否小于5％，若是，则执行步骤217；否则，即：在预设时间段t内Tout的波动大于0.3℃、Pe>SP7、负荷波动大于5％中的至少一个满足时，执行步骤218和步骤204。
具体的，在该实施例中，预设时间T可以取5min，预设时段t可以取1min，也就是说，可以每间隔5min对Tout、Pe和负荷进行一次检查，检查的时间为1min。
217、控制电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值SP8，同时记录此时的蒸发压力Pe1。也就是说，机组工况、负荷稳定，则执行开阀动作，检测开阀后蒸发压力的变化。
218、控制电子膨胀阀执行开阀动作，并重新确定电子膨胀阀的开度值。
具体的，在该实施例中，可以通过以下公式重新确定电子膨胀阀的开度值，EXV_MOV＝预设开度值SP13+2.5。
可选地，在另一个实施例中，如图3所示，在步骤217之后，控制方法200 还可以包括：
219、开阀前后蒸发压力的差值是否大于压力预值P，即：Pe-Pe1>P，若是，则执行步骤220；否则，执行步骤221。
220、将蒸发器端部温差的动态修正值Pdt减小第一设定值SP10。也就是说，将动态修正值Pdt在原基础上减小SP10，为后续减小控制目标值Ts和开阀做准备，然后进入下一循环周期。
221、如果开阀后蒸发压力变化不大，判断当前的Tp值是否大于控制目标值Ts，即：判断ΔTp是否大于0，即：ΔTp>0，若是，则执行步骤222；否则，执行步骤223。
222、将Pdt增加第一设定值SP10，并控制电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值。其中，第二预设开度值＝第一预设开度值SP8+预设开度值SP11。也就是说，动态修正值Pdt在原基础上增大SP10,并执行关阀动作(SP8+SP11)，为后续增大控制目标值Ts和关阀做准备，然后进入下一循环周期。
223、控制电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。其中，第三预设开度值＝第一预设开度值SP8+预设开度值SP12。也就是说，若当前的Tp值不大于控制目标值Ts时，只执行关阀动作(SP8+SP12)，不调整控制目标值，然后进入下一循环周期。
具体的，在该实施例中，在机组负荷、工况基本稳定的情况下，每间隔预设时间，尝试开阀至第一预设开度值SP8，若开阀后端温差实时值Tp值未减小，蒸发压力Pe没有提升，则认为当前Tp值已达到最小值，继续开阀只能导致过冷度减小，转而将Pdt增大SP10，缓慢关阀以增大机组过冷度。如果尝试开阀SP2后，蒸发压力Pe有明显提升，则认为蒸发器没有完全利用，仍有开阀的空间，将Pdt减小SP10，缓慢开阀以提高蒸发温度，使蒸发器充分利用。通过Pdt的动态调整，将Ts控制在最合适的值。
上述实施例中提供的一种电子膨胀阀的控制方法，通过检测冷凝器过冷度， 同时使用换热温差、过冷度作为控制参数，可以使蒸发器充分发挥能力，保证机组的设计能力充分发挥，提升机组能效和运行的稳定性，又不至于过度开阀，有效的防止了机组在运行过程中出现低压过低而报低压保护，在启动过程中出现吸气带液导致跑油损坏压缩机，以及蒸发温度过高导致压缩机跑油、电流过大等问题。
应理解，在本发明各实施例中，上述各过程的序号的大小并不意味着执行顺序的先后，各过程的执行顺序应以其功能和内在逻辑确定，而不应对本发明实施例的实施过程构成任何限定。
上文结合图1至图3，对本发明实施例提供的一种电子膨胀阀的控制方法进行了详细的描述，下面结合图4对本发明实施例提供的一种电子膨胀阀的控制装置进行详细的描述。
本发明还提供一种电子膨胀阀的控制装置，如图4所示，该控制装置100包括：获取模块110、处理模块120和控制模块130。其中，
获取模块110用于获取蒸发器端部温差Tp。处理模块120用于比较获取模块110获取的Tp和蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值。控制模块130用于控制电子膨胀阀的开度调节至处理模块120确定的开度值。
应理解，在本发明实施例中，根据本发明实施例的控制装置100，可对应于根据本发明实施例的控制方法200的执行主体，并且该控制装置100中的各个模块的上述和其它操作和/或功能分别为了实现图1至图3中的各个方法的相应流程，为了简洁，在此不再赘述。
上述实施例中提供的一种电子膨胀阀的控制装置，通过检测蒸发器端温差Tp的实时值，并将Tp实时值与蒸发器端温差的控制目标值Ts相比较，若二者差值△Tp大于允许的偏差，则增大阀的开度，若差值小于允许的偏差，则减小阀的开度，从而调节电子膨胀阀的开度变化，为蒸发器提供最合适的供液量， 将蒸发器换热端温差Tp降到最小，保证蒸发器换热性能得到最充分发挥。
可选地，在一个实施例中，获取模块110还用于获取蒸发器的出水温度Tout和蒸发压力Pe，并将蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp。
可选地，在另一个实施例中，获取模块110还用于获取压缩机的吸气温度Tsuc。处理模块120还用于根据Tsuc和Te，确定压缩机的吸气过热度Sh，并确定电子膨胀阀的开度值。控制模块130还用于当Te、Sh和电子膨胀阀的当前开度值均满足各自的第一预设条件时，控制电子膨胀阀执行开阀动作，并控制电子膨胀阀的开度调节至处理模块120确定的开度值。
可选地，在另一个实施例中，当Te、Sh和电子膨胀阀的当前开度值中的至少一个不满足其的第一预设条件时，获取模块110还用于获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将冷凝压力Pc转换为冷凝温度Tc。处理模块120还用于根据Tdis和Pc，确定压缩机的排气过热度DSh，并确定电子膨胀阀的开度值。控制模块130还用于压缩机运行第一时间后，当DSh和电子膨胀阀的当前开度值均满足各自的第二预设条件时，控制电子膨胀阀执行关阀动作，并控制电子膨胀阀的开度调节至处理模块120确定的开度值。
可选地，在另一个实施例中，当DSh和/或电子膨胀阀的当前开度值不满足各自的第二预设条件时，控制模块130还用于当Te和电子膨胀阀的当前开度值均满足各自的第三预设条件时，控制电子膨胀阀执行关阀动作，并控制电子膨胀阀的开度调节至处理模块确定的开度值。
可选地，在另一个实施例中，当Te和/或电子膨胀阀的当前开度值不满足各自的第三预设条件时，控制模块130还用于每间隔预设时间T，检测预设时 段t内Tout、Pe和负荷均满足各自的第四预设条件时，控制电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值，同时记录此时的蒸发压力Pe1。
或者，控制模块130还用于当在预设时段t内Tout、Pe和负荷中的至少一个不满足其的第四预设条件时，控制电子膨胀阀执行开阀动作，并控制电子膨胀阀的开度调节至根据Te、Sh和电子膨胀阀的当前开度值确定的开度值。
可选地，在另一个实施例中，处理模块120还用于判断开阀前后蒸发压力的差值是否大于压力预值P，若是，则将蒸发器端部温差的动态修正值Pdt减小第一设定值。否则，判断ΔTp是否大于0，且当ΔTp大于0时，将Pdt增加第一设定值。控制模块130还用于当ΔTp大于0时，控制电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值。或者，当ΔTp小于0时，控制电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。
另外，本发明还提供一种制冷系统，如图5所示，该制冷系统包括：如上述任一实施例中描述的控制装置100，依次连接的压缩机101、冷凝器102、电子膨胀阀104和蒸发器103，以及分别与控制装置100连接的第一温度传感器105、第一压力传感器106、第二压力传感器107、第二温度传感器108和第三温度传感器109，且压缩机101还与蒸发器103连接。
第一温度传感器105设置在连接蒸发器103和冷凝器102的管路上，用于检测压缩机101的排气温度Tdis，并将Tdis传输至控制装置100。第二温度传感器108设置在连接蒸发器103和压缩机101的管路上，用于检测压缩机101的吸气温度Tsuc，并将Tsuc传输至控制装置100。第三温度传感器109设置在蒸发器103的出水管路上，用于检测蒸发器出水温度Tout，并将Tout传输至控制装置100。
第一压力传感器106设置在冷凝器102上，用于检测冷凝器102的冷凝压力Pc，并将Pc传输至控制装置100。第二压力传感器107设置在蒸发器103 上，用于检测蒸发器103的蒸发压力Pe，并将Pe传输至控制装置100。
控制装置100，用于接收Tdis、Tsuc、Tout、Pc和Pe，并将Pc和Pe分别转换为饱和冷凝温度Tc和饱和蒸发温度Te，且根据Tdis、Tsuc、Tout、Tc和Te，以及蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值，控制电子膨胀阀104的开度调节至开度值。
具体的，在该实施例中，控制装置100具体根据根据Tdis、Tsuc、Tout、Tc和Te，以及蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值，控制电子膨胀阀104的开度调节至开度值的过程和方法采用上文中描述的控制方法200，为了描述的简洁，再次不再赘述。
另外，本文中术语“和/或”，仅仅是一种描述关联对象的关联关系，表示可以存在三种关系，例如，A和/或B，可以表示：单独存在A，同时存在A和B，单独存在B这三种情况。另外，本文中字符“/”，一般表示前后关联对象是一种“或”的关系。
本领域普通技术人员可以意识到，结合本文中所公开的实施例描述的各示例的单元及算法步骤，能够以电子硬件、计算机软件或者二者的结合来实现，为了清楚地说明硬件和软件的可互换性，在上述说明中已经按照功能一般性地描述了各示例的组成及步骤。这些功能究竟以硬件还是软件方式来执行，取决于技术方案的特定应用和设计约束条件。专业技术人员可以对每个特定的应用来使用不同方法来实现所描述的功能，但是这种实现不应认为超出本发明的范围。
所属领域的技术人员可以清楚地了解到，为了描述的方便和简洁，上述描述的系统、装置和单元的具体工作过程，可以参考前述方法实施例中的对应过程，在此不再赘述。
在本申请所提供的几个实施例中，应该理解到，所揭露的系统、装置和方 法，可以通过其它的方式实现。例如，以上所描述的装置实施例仅仅是示意性的，例如，单元的划分，仅仅为一种逻辑功能划分，实际实现时可以有另外的划分方式，例如多个单元或组件可以结合或者可以集成到另一个系统，或一些特征可以忽略，或不执行。另外，所显示或讨论的相互之间的耦合或直接耦合或通信连接可以是通过一些接口、装置或单元的间接耦合或通信连接，也可以是电的，机械的或其它的形式连接。
作为分离部件说明的单元可以是或者也可以不是物理上分开的，作为单元显示的部件可以是或者也可以不是物理单元，即可以位于一个地方，或者也可以分布到多个网络单元上。可以根据实际的需要选择其中的部分或者全部单元来实现本发明实施例方案的目的。
另外，在本发明各个实施例中的各功能单元可以集成在一个处理单元中，也可以是各个单元单独物理存在，也可以是两个或两个以上单元集成在一个单元中。上述集成的单元既可以采用硬件的形式实现，也可以采用软件功能单元的形式实现。
集成的单元如果以软件功能单元的形式实现并作为独立的产品销售或使用时，可以存储在一个计算机可读取存储介质中。基于这样的理解，本发明的技术方案本质上或者说对现有技术做出贡献的部分，或者该技术方案的全部或部分可以以软件产品的形式体现出来，该计算机软件产品存储在一个存储介质中，包括若干指令用以使得一台计算机设备(可以是个人计算机，服务器，或者网络设备等)执行本发明各个实施例方法的全部或部分步骤。而前述的存储介质包括：U盘、移动硬盘、只读存储器(ROM，Read-Only Memory)、随机存取存储器(RAM，Random Access Memory)、磁碟或者光盘等各种可以存储程序代码的介质。
以上，仅为本发明的具体实施方式，但本发明的保护范围并不局限于此，任何熟悉本技术领域的技术人员在本发明揭露的技术范围内，可轻易想到各种等效的修改或替换，这些修改或替换都应涵盖在本发明的保护范围之内。因此， 本发明的保护范围应以权利要求的保护范围为准。

Claims (15)

  1. 一种电子膨胀阀的控制方法，其特征在于，包括以下步骤：
    步骤1、获取蒸发器端部温差Tp；
    步骤2、比较Tp和所述蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp；
    步骤3、根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值；
    步骤4、控制所述电子膨胀阀的开度调节至所述开度值。
  2. 根据权利要求1所述的电子膨胀阀的控制方法，其特征在于，在步骤1之前，还包括：
    步骤5、获取蒸发器的出水温度Tout和蒸发压力Pe，并将所述蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp。
  3. 根据权利要求2所述的电子膨胀阀的控制方法，其特征在于，在步骤3之后，还包括：
    步骤6、获取压缩机的吸气温度Tsuc；
    步骤7、根据Tsuc和Te，确定压缩机的吸气过热度Sh；
    步骤8、当Te、Sh和所述电子膨胀阀的当前开度值均满足各自的第一预设条件时，控制所述电子膨胀阀执行开阀动作，并确定所述电子膨胀阀的开度值，执行步骤4。
  4. 根据权利要求3所述的电子膨胀阀的控制方法，其特征在于，当Te、Sh和所述电子膨胀阀的当前开度值中的至少一个不满足其的第一预设条件时，还包括：
    步骤9、获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将所述冷凝压力Pc转换为冷凝温度Tc；
    步骤10、根据Tdis和Pc，确定压缩机的排气过热度DSh；
    步骤11、压缩机运行第一时间后，当DSh和所述电子膨胀阀的当前开度值 均满足各自的第二预设条件时，控制所述电子膨胀阀执行关阀动作，并确定所述电子膨胀阀的开度值，执行步骤4。
  5. 根据权利要求4所述的电子膨胀阀的控制方法，其特征在于，当DSh和/或所述电子膨胀阀的当前开度值不满足各自的第二预设条件时，还包括：
    步骤12、当Te和所述电子膨胀阀的当前开度值均满足各自的第三预设条件时，控制所述电子膨胀阀执行关阀动作，并确定所述电子膨胀阀的开度值，执行步骤4。
  6. 根据权利要求5所述的电子膨胀阀的控制方法，其特征在于，当Te和/或所述电子膨胀阀的当前开度值不满足各自的第三预设条件时，还包括：
    步骤13、每间隔预设时间T，检测预设时段t内Tout、Pe和负荷均满足各自的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值，同时记录此时的蒸发压力Pe1；或者，
    步骤14、当在预设时段t内Tout、Pe和负荷中的至少一个不满足其的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至根据Te、Sh和所述电子膨胀阀的当前开度值确定的开度值。
  7. 根据权利要求6所述的电子膨胀阀的控制方法，其特征在于，在步骤13之后，还包括：
    步骤15、开阀前后蒸发压力的差值是否大于压力预值P，若是，则将蒸发器端部温差的动态修正值Pdt减小第一设定值；否则，判断ΔTp是否大于0；
    步骤16、当ΔTp大于0时，将Pdt增加所述第一设定值，并控制所述电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值；或者，
    步骤17、当ΔTp小于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。
  8. 一种电子膨胀阀的控制装置，其特征在于，包括：
    获取模块，用于获取蒸发器端部温差Tp；
    处理模块，用于比较所述获取模块获取的Tp和所述蒸发器端部温差的控 制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定电子膨胀阀的开度值；
    控制模块，用于控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
  9. 根据权利要求8所述的电子膨胀阀的控制装置，其特征在于，所述获取模块还用于获取蒸发器的出水温度Tout和蒸发压力Pe，并将所述蒸发压力Pe转换为蒸发温度Te，则Tout与Te的差值为Tp。
  10. 根据权利要求9所述的电子膨胀阀的控制装置，其特征在于，
    所述获取模块还用于获取压缩机的吸气温度Tsuc；
    所述处理模块还用于根据Tsuc和Te，确定压缩机的吸气过热度Sh，并确定所述电子膨胀阀的开度值；
    所述控制模块还用于当Te、Sh和所述电子膨胀阀的当前开度值均满足各自的第一预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
  11. 根据权利要求10所述的电子膨胀阀的控制装置，其特征在于，当Te、Sh和所述电子膨胀阀的当前开度值中的至少一个不满足其的第一预设条件时，
    所述获取模块还用于获取压缩机的排气温度Tdis和冷凝器的冷凝压力Pc，并将所述冷凝压力Pc转换为冷凝温度Tc；
    所述处理模块还用于根据Tdis和Pc，确定压缩机的排气过热度DSh，并确定所述电子膨胀阀的开度值；
    所述控制模块还用于压缩机运行第一时间后，当DSh和所述电子膨胀阀的当前开度值均满足各自的第二预设条件时，控制所述电子膨胀阀执行关阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
  12. 根据权利要求11所述的电子膨胀阀的控制装置，其特征在于，当DSh和/或所述电子膨胀阀的当前开度值不满足各自的第二预设条件时，所述控制模块还用于当Te和所述电子膨胀阀的当前开度值均满足各自的第三预设条件时， 控制所述电子膨胀阀执行关阀动作，并控制所述电子膨胀阀的开度调节至所述处理模块确定的所述开度值。
  13. 根据权利要求12所述的电子膨胀阀的控制装置，其特征在于，当Te和/或所述电子膨胀阀的当前开度值不满足各自的第三预设条件时，所述控制模块还用于每间隔预设时间T，检测预设时段t内Tout、Pe和负荷均满足各自的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并将其开度调节至第一预设开度值，同时记录此时的蒸发压力Pe1；
    或者，所述控制模块还用于当在预设时段t内Tout、Pe和负荷中的至少一个不满足其的第四预设条件时，控制所述电子膨胀阀执行开阀动作，并控制所述电子膨胀阀的开度调节至根据Te、Sh和所述电子膨胀阀的当前开度值确定的开度值。
  14. 根据权利要求13所述的电子膨胀阀的控制装置，其特征在于，所述处理模块还用于判断开阀前后蒸发压力的差值是否大于压力预值P，若是，则将蒸发器端部温差的动态修正值Pdt减小第一设定值；否则，判断ΔTp是否大于0，且当ΔTp大于0时，将Pdt增加所述第一设定值；
    所述控制模块还用于当ΔTp大于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第二预设开度值；或者，当ΔTp小于0时，控制所述电子膨胀阀执行关阀动作，将其开度调节至第三预设开度值。
  15. 一种制冷系统，其特征在于，包括：依次连接的压缩机(101)、冷凝器(102)、电子膨胀阀(104)和蒸发器(103)，如权利要求8-14中任一项所述的控制装置(100)，以及分别与所述控制装置(100)连接的第一温度传感器(105)、第一压力传感器(106)、第二压力传感器(107)、第二温度传感器(108)和第三温度传感器(109)，其中，所述压缩机(101)还与所述蒸发器(103)连接；
    所述第一温度传感器(105)设置在连接所述蒸发器(103)和所述冷凝器(102)的管路上，用于检测压缩机(101)的排气温度Tdis，并将Tdis传输至 所述控制装置(100)；
    所述第二温度传感器(108)设置在连接所述蒸发器(103)和所述压缩机(101)的管路上，用于检测压缩机(101)的吸气温度Tsuc，并将Tsuc传输至所述控制装置(100)；
    所述第三温度传感器(109)设置在所述蒸发器(103)的出水管路上，用于检测蒸发器出水温度Tout，并将Tout传输至所述控制装置(100)；
    所述第一压力传感器(106)设置在所述冷凝器(102)上，用于检测所述冷凝器(102)的冷凝压力Pc，并将Pc传输至所述控制装置(100)；
    所述第二压力传感器(107)设置在所述蒸发器(103)上，用于检测所述蒸发器(103)的蒸发压力Pe，并将Pe传输至所述控制装置(100)；
    所述控制装置(100)，用于接收Tdis、Tsuc、Tout、Pc和Pe，并将Pc和Pe分别转换为饱和冷凝温度Tc和饱和蒸发温度Te，且根据Tdis、Tsuc、Tout、Tc和Te，以及所述蒸发器端部温差的控制目标值Ts，得到二者的差值ΔTp，并根据ΔTp与预设偏差值的大小关系，确定所述电子膨胀阀(104)的开度值，控制所述电子膨胀阀(104)的开度调节至所述开度值。
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CN115585565A (zh) * 2022-12-12 2023-01-10 顿汉布什(中国)工业有限公司 一种大冷量离心机组电动节流机构的精确控制方法
WO2025007305A1 (zh) * 2023-07-05 2025-01-09 中建环能科技股份有限公司 热泵低温干化设备低能耗控制方法、电子设备及存储介质
CN118912763B (zh) * 2024-08-19 2025-04-11 无锡冠亚恒温制冷技术有限公司 一种温控设备及其电子膨胀阀的控制方法和控制装置
CN119665508B (zh) * 2024-12-20 2026-01-23 珠海格力电器股份有限公司 制冷设备的制冷方法、制冷设备、制冷系统以及喷淋装置

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1683848A (zh) * 2004-04-12 2005-10-19 Lg电子株式会社 冷却循环设备和用于控制其线性膨胀阀的方法
CN101408355A (zh) * 2007-10-09 2009-04-15 株式会社神户制钢所 冷冻装置及冷冻装置的运转方法
CN101901017A (zh) * 2009-05-27 2010-12-01 江森自控楼宇设备科技(无锡)有限公司 节流机构的模糊控制系统及方法
CN104913459A (zh) * 2015-06-25 2015-09-16 山东格瑞德集团有限公司 制冷空调冷媒流量实时控制方法及装置
CN106595141A (zh) * 2016-12-12 2017-04-26 重庆美的通用制冷设备有限公司 一种电子膨胀阀的控制方法和装置以及制冷系统

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05106922A (ja) * 1991-10-18 1993-04-27 Hitachi Ltd 冷凍装置の制御方式
US6318101B1 (en) * 2000-03-15 2001-11-20 Carrier Corporation Method for controlling an electronic expansion valve based on cooler pinch and discharge superheat
US7878014B2 (en) * 2005-12-09 2011-02-01 Emerson Climate Technologies, Inc. Parallel condensing unit control system and method
JP2007255738A (ja) * 2006-03-20 2007-10-04 Daikin Ind Ltd 空気調和装置
CN101311851B (zh) * 2007-05-25 2013-05-22 开利公司 用于冷却器电子膨胀阀的修改的模糊控制
KR20110139283A (ko) * 2009-03-19 2011-12-28 다이킨 고교 가부시키가이샤 공기 조화 장치
JP4968373B2 (ja) * 2010-08-02 2012-07-04 ダイキン工業株式会社 空気調和装置
JP2014085048A (ja) * 2012-10-23 2014-05-12 Ebara Refrigeration Equipment & Systems Co Ltd ターボ冷凍機
CN104990294B (zh) * 2015-05-29 2017-10-31 重庆美的通用制冷设备有限公司 空调器及其控制方法、控制装置

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1683848A (zh) * 2004-04-12 2005-10-19 Lg电子株式会社 冷却循环设备和用于控制其线性膨胀阀的方法
CN101408355A (zh) * 2007-10-09 2009-04-15 株式会社神户制钢所 冷冻装置及冷冻装置的运转方法
CN101901017A (zh) * 2009-05-27 2010-12-01 江森自控楼宇设备科技(无锡)有限公司 节流机构的模糊控制系统及方法
CN104913459A (zh) * 2015-06-25 2015-09-16 山东格瑞德集团有限公司 制冷空调冷媒流量实时控制方法及装置
CN106595141A (zh) * 2016-12-12 2017-04-26 重庆美的通用制冷设备有限公司 一种电子膨胀阀的控制方法和装置以及制冷系统

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3719418A1 (en) * 2019-04-02 2020-10-07 Carrier Corporation Electronic expansion valve, heat exchange system and method for controlling electronic expansion valve
US11499766B2 (en) 2019-04-02 2022-11-15 Carrier Corporation Electric expansion valve, a heat exchange system and a method of controlling the electric expansion valve
CN114353288B (zh) * 2020-09-29 2023-09-01 广东美的制冷设备有限公司 空调器及其控制方法和计算机可读存储介质
CN114353288A (zh) * 2020-09-29 2022-04-15 广东美的制冷设备有限公司 空调器及其控制方法和计算机可读存储介质
WO2022127332A1 (zh) * 2020-12-17 2022-06-23 青岛海尔新能源电器有限公司 热泵热水器及热泵热水器的控制方法
CN115355637B (zh) * 2021-06-29 2023-09-15 江苏拓米洛高端装备股份有限公司 制冷系统多间室电子膨胀阀的控制方法、装置及制冷系统
CN115355637A (zh) * 2021-06-29 2022-11-18 江苏拓米洛环境试验设备有限公司 制冷系统多间室电子膨胀阀的控制方法、装置及制冷系统
CN114594810A (zh) * 2022-03-03 2022-06-07 北京半导体专用设备研究所（中国电子科技集团公司第四十五研究所） 一种温度控制方法、装置及电子设备
CN114484954A (zh) * 2022-03-09 2022-05-13 广东开利暖通空调股份有限公司 电子膨胀阀的控制方法、控制装置及空气源热泵系统
CN114484954B (zh) * 2022-03-09 2023-09-22 广东开利暖通空调股份有限公司 电子膨胀阀的控制方法、控制装置及空气源热泵系统
CN114873674A (zh) * 2022-05-24 2022-08-09 深圳市家家分类科技有限公司 一种低温蒸发系统、方法及装置
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CN114992943A (zh) * 2022-05-30 2022-09-02 海信（山东）冰箱有限公司 冰箱及制冷系统控制方法
CN115289621A (zh) * 2022-06-30 2022-11-04 南京久鼎环境科技股份有限公司 一种用于中央空调系统主机的控制方法
CN115289621B (zh) * 2022-06-30 2023-10-03 南京久鼎环境科技股份有限公司 一种用于中央空调系统主机的控制方法
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