WO2021022766A1 - 用于空调机组的压缩机冷却控制方法 - Google Patents

用于空调机组的压缩机冷却控制方法 Download PDF

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Publication number
WO2021022766A1
WO2021022766A1 PCT/CN2019/127938 CN2019127938W WO2021022766A1 WO 2021022766 A1 WO2021022766 A1 WO 2021022766A1 CN 2019127938 W CN2019127938 W CN 2019127938W WO 2021022766 A1 WO2021022766 A1 WO 2021022766A1
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Prior art keywords
compressor
temperature
preset
pressure ratio
pressure
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PCT/CN2019/127938
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English (en)
French (fr)
Inventor
武传志
隋杰磊
张捷
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青岛海尔空调电子有限公司
海尔智家股份有限公司
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Publication of WO2021022766A1 publication Critical patent/WO2021022766A1/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
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • 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
    • F24F11/62—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
    • 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
    • F24F11/86—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling compressors within refrigeration or heat pump circuits
    • 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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • 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
    • F25B31/00—Compressor 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
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid

Definitions

  • the invention belongs to the technical field of air conditioners, and specifically relates to a compressor cooling control method for an air conditioner unit.
  • air conditioning units have become an essential equipment in people's lives.
  • the various designs of air-conditioning units have become more and more mature in recent years, there are still some problems with existing air-conditioning units; for example, as an essential component of each air-conditioning unit, the compressor can use its own compression function. To change the state of the refrigerant, so the compressor is prone to heat generation during the working process.
  • the inverter compressor is prone to overheating during the speed increase process, which leads to the problem of excessive compressor temperature; at the same time, if the compressor temperature cannot be lowered in time, it is easy to cause the compressor to be damaged. Burn out, which in turn causes the problem that the entire air conditioning unit cannot continue to work normally. It can be seen that the spray cooling operation of the compressor cannot be ignored.
  • the existing air-conditioning units usually achieve the effect of cooling the compressor by installing liquid spray pipes, that is, by directly cooling the refrigerant after the condenser has been cooled. Introduced into the compressor to achieve cooling.
  • existing compressors are usually provided with cooling ports, and the liquid spray pipeline is connected to the cooling port, so that the refrigerant in the liquid spray pipeline can enter the compressor through the cooling port, and the liquid refrigerant entering the compressor can pass through
  • the evaporation effect realizes the heat absorption effect to reduce the temperature of the compressor
  • a solenoid valve is also provided at the cooling port to control the on and off of the liquid spray pipeline.
  • the compressor will generate a lot of heat.
  • this pressure difference is not enough to provide enough refrigerant to cool the compressor. Therefore, it is easy to cause the problem of insufficient cooling of the compressor, and even affect the normal use of the unit in severe cases.
  • some existing air conditioning units also add refrigerant pumps to the liquid injection pipeline to ensure the supply of refrigerant.
  • the solenoid valves installed at the refrigerant pump and the cooling port cannot achieve synchronous control, the technicians also need to install the two refrigerant pumps.
  • An additional one-way valve is installed at the end to achieve bypass.
  • the refrigerant pump can directly supply refrigerant to the compressor for cooling; when the solenoid valve is closed, the refrigerant in the refrigerant pump can self-circulate through the bypass pipeline; It can be seen that the control method of this kind of cooling structure is very complicated, so it is prone to error control. In addition, the refrigerant can easily cause cavitation to the internal structure of the refrigerant pump, resulting in a significant reduction in the reliability and service life of the refrigerant pump.
  • the art needs a new compressor cooling control method for an air conditioning unit to solve the above-mentioned problems.
  • the present invention provides a compressor cooling control method for the air-conditioning unit. It includes a liquid spray pipeline, a main circulation circuit, and a compressor, a condenser, an electronic expansion valve, and an evaporator arranged on the main circulation circuit, wherein the liquid spray pipeline can spray and cool the compressor ,
  • the electronic expansion valve is arranged between the condenser and the evaporator, and the compressor cooling control method includes: obtaining the temperature of the compressor; obtaining the pressure ratio of the compressor; If the temperature of the engine is greater than the preset temperature and the pressure ratio of the compressor is less than the preset pressure ratio, the opening degree of the electronic expansion valve is controlled according to the temperature and the pressure ratio of the compressor.
  • the step of controlling the opening degree of the electronic expansion valve by the temperature and pressure ratio includes: if the temperature of the compressor continues to be greater than the preset temperature for a first preset time and the first preset time If the pressure ratio of the compressor is less than the preset pressure ratio within a period of time, the opening degree of the electronic expansion valve is controlled according to the temperature and pressure ratio of the compressor.
  • the step of controlling the opening degree of the electronic expansion valve by the temperature and the pressure ratio includes: if the temperature of the compressor continues to be greater than the preset temperature for a second preset time and reaches the second preset time When the pressure ratio of the compressor is continuously lower than the preset pressure ratio within the time, the opening degree of the electronic expansion valve is controlled according to the temperature and the pressure ratio of the compressor.
  • the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” specifically includes: making the electronic expansion valve The opening degree of the compressor reduces the preset opening degree, wherein the preset opening degree is based on the difference between the temperature of the compressor and the preset temperature and/or the pressure ratio of the compressor and the preset The difference in pressure ratio is determined.
  • the step of "decreasing the opening of the electronic expansion valve by a preset opening” further includes: every third preset time, so that all The opening degree of the electronic expansion valve is reduced by the preset opening degree.
  • the compressor cooling control method for an air conditioning unit, after the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” is performed, the compressor is cooled
  • the control method further includes: obtaining the temperature of the compressor again; if the temperature of the compressor is less than or equal to the preset temperature, no longer controlling the electronic expansion valve according to the temperature and pressure ratio of the compressor Opening.
  • the compressor cooling control method for an air conditioning unit, after the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” is performed, the compressor is cooled
  • the control method further includes: obtaining the pressure ratio of the compressor again; if the pressure ratio of the compressor is greater than or equal to the preset pressure ratio, no longer controlling the electronic device according to the temperature and pressure ratio of the compressor The opening of the expansion valve.
  • the compressor cooling control method for an air conditioning unit, after the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” is performed, the compressor is cooled
  • the control method further includes: obtaining the high-pressure pressure of the compressor; if the high-pressure pressure of the compressor continues to be greater than the preset high-pressure pressure for a fourth preset time, no longer according to the temperature and pressure ratio of the compressor Control the opening degree of the electronic expansion valve.
  • the compressor cooling control method for an air conditioning unit, after the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” is performed, the compressor is cooled
  • the control method further includes: obtaining the low-pressure pressure of the compressor; if the low-pressure pressure of the compressor continues to be less than the preset low-pressure pressure for a fifth preset time, no longer according to the temperature and pressure ratio of the compressor Control the opening degree of the electronic expansion valve.
  • the compressor cooling control method for an air conditioning unit, after the step of "controlling the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor” is performed, the compressor is cooled
  • the control method further includes: if the target load of the compressor is less than a preset load, operating the compressor at the preset load; if the target load of the compressor is greater than or equal to the preset load, then The compressor is operated at the target load.
  • the air conditioning unit of the present invention includes a liquid injection pipe, a main circulation circuit, and a compressor, a condenser, and an electronic expansion valve arranged on the main circulation circuit. And an evaporator, wherein the liquid spray pipeline can spray and cool the compressor, the electronic expansion valve is arranged between the condenser and the evaporator, the compressor cooling control method of the present invention Including: obtaining the temperature of the compressor; obtaining the pressure ratio of the compressor; if the temperature of the compressor is greater than a preset temperature and the pressure ratio of the compressor is less than the preset pressure ratio, according to the compressor The temperature and pressure ratio control the opening of the electronic expansion valve.
  • the air-conditioning unit can change the pressure in the condenser by changing the opening of the electronic expansion valve, thereby changing the pressure difference between the condenser and the liquid spray pipe, so that the refrigerant in the condenser can pass through the liquid spray.
  • the pipeline enters the compressor smoothly.
  • the air conditioning unit can control the opening of the electronic expansion valve according to the temperature and pressure ratio of the compressor, so that the air conditioning unit can change the The opening degree of the electronic expansion valve can change the pressure difference between the condenser and the liquid injection pipe, so as to effectively ensure that the liquid injection pipe can supply enough cooling medium to the compressor, thereby effectively Ensure the cooling effect of the compressor.
  • the temperature of the compressor continues to be greater than the preset temperature for a period of time that reaches the first preset time and the first preset time occurs within the first preset time
  • the pressure ratio of the compressor is less than the preset pressure ratio, it is determined that the compressor is overheated and the pressure difference between the condenser and the liquid injection pipe is insufficient, so as to effectively improve the accuracy of the judgment result Sex.
  • the temperature of the compressor continues to be greater than the preset temperature for a time that reaches the second preset time and the compressor is within the second preset time If the pressure ratio is continuously smaller than the preset pressure ratio, it is determined that the compressor has overheating phenomenon and the pressure difference between the condenser and the liquid injection pipe is insufficient, so as to effectively improve the accuracy of the judgment result.
  • the air-conditioning unit when the compressor is overheated and the pressure difference between the condenser and the liquid injection pipe is insufficient, the air-conditioning unit can be used every other
  • the third preset time reduces the opening of the electronic expansion valve by the preset opening, so that the opening of the electronic expansion valve can be gradually reduced; it is understandable that the electronic expansion valve In the process of decreasing the opening degree, a large amount of refrigerant will gradually accumulate in the condenser, so that the pressure in the condenser will continue to increase, thereby effectively improving the relationship between the condenser and the liquid spray pipeline.
  • the pressure difference between the two thereby effectively increasing the refrigerant supply speed of the liquid spray pipeline.
  • the present invention can also determine the preset opening degree according to the difference between the temperature of the compressor and the preset temperature and/or the difference between the pressure ratio of the compressor and the preset pressure ratio Specifically, the greater the difference between the temperature of the compressor and the preset temperature and/or the smaller the difference between the pressure ratio of the compressor and the preset pressure ratio, the preset opening The greater the degree; that is, the stronger the cooling demand of the compressor or the smaller the pressure difference between the condenser and the liquid injection pipe, the electronic expansion valve is closed at a faster speed, so that The pressure difference between the condenser and the liquid spray pipe can be increased more quickly, so that the liquid spray pipe can supply refrigerant as soon as required.
  • the temperature of the compressor is less than or equal to the preset temperature, it means that the temperature of the compressor has been lowered to a sufficiently low level that there is no need to continue cooling, so no longer
  • the opening degree of the electronic expansion valve is controlled according to the temperature and pressure ratio of the compressor, so as to effectively ensure the heat exchange effect of the air conditioning unit.
  • the pressure ratio of the compressor is greater than or equal to the preset pressure ratio, it means that the pressure difference between the condenser and the liquid injection pipe is sufficient. Large, that is, the refrigerant supply speed of the liquid injection pipeline is fast enough, so the opening of the electronic expansion valve is no longer controlled according to the temperature and pressure ratio of the compressor, so as to effectively ensure the heat exchange of the air conditioning unit effect.
  • the compressor has a high-pressure warning.
  • the opening degree of the electronic expansion valve is no longer controlled according to the temperature and pressure ratio of the compressor, so as to effectively ensure the normal operation of the compressor.
  • the opening degree of the electronic expansion valve is no longer controlled according to the temperature and pressure ratio of the compressor, so as to effectively ensure the normal operation of the compressor.
  • the compressor is operated at the preset load; it is understandable that when the compressor When the operating load of the compressor is too small, it is easy to cause various failures of the compressor during operation, including the problem that the compressor heats up too quickly and easily leads to excessive temperature. Therefore, when the target load of the compressor is less than all When the preset load is used, the air conditioning unit controls the compressor to operate at the preset load, so as to effectively ensure that the compressor can work efficiently. At the same time, if the target load of the compressor is greater than or equal to the preset load, the compressor is directly operated at the target load, so as to effectively ensure the working demand of the compressor.
  • Figure 1 is a schematic diagram of the overall structure of the air conditioning unit of the present invention.
  • FIG. 2 is a flowchart of the main steps of the compressor cooling control method of the present invention.
  • Fig. 3 is a step flow chart of a preferred embodiment of the compressor cooling control method of the present invention.
  • Figure 1 is a schematic diagram of the overall structure of the air conditioning unit of the present invention.
  • the air conditioning unit of the present invention includes a main circulation loop and a compressor 1, a condenser 2, an electronic expansion valve 3, and an evaporator 4 which are sequentially arranged on the main circulation loop.
  • the refrigerant in the air conditioning unit The heat exchange is realized through the main circulation loop; of course, for the convenience of description, only the main components of the air conditioning unit are shown in FIG. 1, and the technician can set the specific air conditioning unit according to actual needs.
  • Structure The present invention does not impose any restriction on the specific structure of the air conditioning unit. The change of this specific structure does not deviate from the basic principle of the present invention and belongs to the protection scope of the present invention.
  • the air conditioning unit also includes a liquid spray pipe 5, a cooling port is provided on the compressor 1, and a solenoid valve is provided at the cooling port.
  • a liquid spray pipe 5 is connected to the lower end of the condenser 2, and the other end is connected to the cooling port.
  • the cooling ports are connected so that the refrigerant in the condenser 2 can directly enter the compressor 1 through the cooling ports, and the solenoid valve provided at the cooling port can control the on and off of the liquid spray pipeline 5.
  • the present invention does not impose any restriction on the specific setting method of the liquid spray pipe 5, and the technician can set it according to actual use requirements; for example, one end of the liquid spray pipe 5 can also be connected to the condenser 2 and the electronic Between the expansion valves 3 and the specific setting positions of the cooling ports can also be changed, as long as the liquid spray pipe 5 can directly introduce the cooled refrigerant into the compressor 1.
  • the air conditioning unit also includes a touch screen, through which the user can control the operation of the air conditioning unit; of course, this setting is not restrictive, that is, the air conditioning unit is also
  • the touch-sensitive display screen may not be provided, or a button-type display screen, etc. may be provided, and this specific structural change does not deviate from the basic principle of the present invention.
  • the air conditioning unit further includes a temperature sensor and a controller
  • the temperature sensor can measure the temperature of the compressor 1
  • the controller can obtain the measurement data of the temperature sensor
  • the controller can also control the
  • the operation of the air conditioning unit includes, for example, controlling the opening degree of the electronic expansion valve 3, controlling the opening and closing state of the solenoid valve, and the like.
  • the controller may be the air conditioning unit.
  • the original controller may also be a controller separately provided for implementing the compressor cooling control method of the present invention, and technicians can set the structure and model of the controller by themselves according to actual use requirements.
  • the technical personnel can set the application object of the compressor cooling control method according to the actual use requirements; since the inverter compressor is prone to excessive temperature, it is preferable to compress the compressor of the present invention.
  • the machine cooling control method is applied to the magnetic levitation frequency conversion centrifugal air conditioning unit.
  • the change of the specific application object does not deviate from the basic principle of the present invention, and should belong to the protection scope of the present invention.
  • FIG 2 is a flowchart of the main steps of the compressor cooling control method of the present invention.
  • the compressor cooling control method of the present invention mainly includes the following steps:
  • step S1 the controller obtains the temperature of the compressor 1 through the temperature sensor; it should be noted that the present invention does not impose any limitation on the specific manner in which the controller obtains the temperature of the compressor 1, as long as It is only necessary that the controller can obtain the temperature of the compressor 1.
  • step S2 the controller can obtain the absolute pressure of the discharge port and the absolute pressure of the suction port of the compressor 1, and then calculate the ratio of the absolute pressure of the discharge port to the absolute pressure of the suction port, which is recorded as the compressor It should be noted that the present invention does not impose any restrictions on the manner in which the controller obtains the absolute pressure of the discharge port and the absolute pressure of the suction port of the compressor 1. The technician can set it according to actual needs.
  • step S1 and step S2 can be set by themselves, that is, the controller may first obtain the temperature of compressor 1, or first obtain the temperature of compressor 1. The pressure ratio, or the controller can also obtain the temperature and pressure ratio of the compressor 1 at the same time. This change in the order of obtaining the basic parameters does not deviate from the basic principle of the present invention.
  • step S3 if the controller determines that the temperature of the compressor 1 is greater than the preset temperature and the pressure ratio of the compressor 1 is less than the preset pressure ratio, it means that the compressor 1 is overheated and The pressure difference between the condenser 2 and the liquid injection pipe 5 is insufficient; at this time, the controller can control the opening of the electronic expansion valve 3 according to the temperature and pressure ratio of the compressor 1, thereby changing the condenser 2 and the liquid injection Pressure difference between pipeline 5.
  • the present invention does not impose any restrictions on its specific control mode, that is, the technician can set the opening adjustment mode of the electronic expansion valve 3 according to actual use requirements, as long as the controller is based on the temperature and the compressor 1
  • the pressure ratio to control the opening degree of the electronic expansion valve 3 falls within the protection scope of the present invention.
  • the technicians can set the preset temperature and the preset pressure ratio according to actual use requirements, as long as the temperature of the compressor 1 is greater than the preset temperature, the compression
  • the compressor 1 has overheating phenomenon, and when the pressure ratio of the compressor 1 is less than the preset pressure ratio, it means that the pressure difference between the condenser 2 and the liquid injection pipe 5 is insufficient.
  • FIG. 3 is a flowchart of the steps of the preferred embodiment of the compressor cooling control method of the present invention. As shown in Fig. 3, based on the air conditioning unit described in the above embodiment, a preferred embodiment of the compressor cooling control method of the present invention specifically includes the following steps:
  • step S113 Determine whether the opening degree of the electronic expansion valve is greater than the preset minimum opening degree; if yes, go to step S103; if not, go to step S114;
  • step S101 the controller obtains the temperature of the compressor 1 through the temperature sensor; as a preferred embodiment, when the compressor 1 is an inverter compressor, the temperature sensor is set in the compressor 1. Near the inverter in order to obtain the temperature of the inverter as the temperature of the compressor 1.
  • the present invention does not impose any limitation on the specific manner in which the controller obtains the temperature of the compressor 1, as long as the controller can obtain the temperature of the compressor 1.
  • the controller can also obtain the absolute pressure of the discharge port and the absolute pressure of the suction port of the compressor 1, and then calculate the ratio of the absolute pressure of the discharge port to the absolute pressure of the suction port, which is recorded as the pressure ratio of the compressor 1.
  • the present invention does not impose any restrictions on the manner in which the controller obtains the absolute pressure of the discharge port and the absolute pressure of the suction port of the compressor 1.
  • the technician can set it according to actual needs, as long as the control The pressure ratio of the compressor 1 can be finally obtained by the compressor.
  • the controller can determine whether the temperature of the compressor 1 is greater than the preset temperature and the pressure ratio of the compressor 1 is less than the preset pressure ratio; it should be noted that the technician can Set the value of the preset temperature and the preset pressure ratio according to actual use requirements. As long as the temperature of the compressor 1 is greater than the preset temperature, it means that the compressor 1 is overheated, and when the compressor 1 When the pressure ratio is less than the preset pressure ratio, it means that the pressure difference between the condenser 2 and the liquid spray pipe 5 is insufficient; preferably, the preset temperature is 50° C., and the preset pressure ratio is 1.5.
  • the temperature of compressor 1 is continuously greater than Whether the time of the preset temperature reaches the first preset time and whether the pressure ratio of the compressor 1 is less than the preset pressure ratio within the first preset time, or whether the temperature of the compressor 1 is judged Whether the time that is continuously greater than the preset temperature reaches the second preset time and whether the pressure ratio of the compressor 1 is also continuously less than the preset pressure ratio during the second preset time?
  • This specific determination method is changed It does not deviate from the basic principle of the present invention, and falls within the protection scope of the present invention.
  • step S102 if the controller determines that the temperature of the compressor 1 is greater than the preset temperature and the pressure ratio of the compressor 1 is less than the preset pressure ratio, it means that the compressor 1 is overheated. Phenomenon and the pressure difference between the condenser 2 and the liquid injection pipe 5 is insufficient; in this case, step S103 is executed, that is, the controller can control the opening of the electronic expansion valve 3 to reduce the preset opening, so as to quickly Increase the pressure in the condenser 2. It should be noted that the technician can set the size of the preset opening degree by himself according to actual use requirements.
  • the preset opening degree may be a constant value or a variable value; preferably, the control The device can determine the size of the preset opening according to the difference between the temperature of the compressor 1 and the preset temperature and the difference between the pressure ratio of the compressor 1 and the preset pressure ratio.
  • this setting The way is not restrictive.
  • the controller determines that the temperature of the compressor 1 is not greater than the preset temperature, it means that there is no overheating phenomenon in the compressor 1, and if the pressure ratio of the compressor 1 is not less than the preset pressure ratio, it means The pressure difference between the condenser 2 and the liquid spray pipe 5 is sufficient; in this case, step S101 can be executed again.
  • step S104 is executed, that is, the controller can obtain the temperature of the compressor 1 again, so as to determine the cooling condition of the compressor 1.
  • step S105 the controller can determine whether the temperature of the compressor 1 is less than or equal to the preset temperature, so as to determine whether the compressor 1 has been sufficiently cooled. Based on the judgment result of step S105, if the controller judges that the temperature of the compressor 1 is less than or equal to the preset temperature, it means that the temperature of the compressor 1 is already low enough.
  • step S106 is executed, that is, The controller no longer controls the opening degree of the electronic expansion valve 3 according to the temperature and pressure ratio of the compressor 1, so as to effectively ensure the heat exchange effect of the air conditioning unit.
  • step S107 is executed to make the next judgment.
  • step S107 the controller obtains the pressure ratio of the compressor 1 again, so as to indirectly determine the flow of refrigerant in the liquid injection pipe 5.
  • step S108 the controller can again determine whether the pressure ratio of the compressor 1 is greater than or equal to the preset pressure ratio, so as to determine whether the refrigerant supply amount of the liquid injection pipe 5 meets the standard. Based on the judgment result of step S108, if the controller judges that the pressure ratio of the compressor 1 is greater than or equal to the preset pressure ratio, it means that the pressure difference between the condenser 2 and the liquid injection pipe 5 is sufficiently large.
  • step S106 is executed, that is, the controller no longer controls the opening degree of the electronic expansion valve 3 according to the temperature and pressure ratio of the compressor 1, so as to effectively ensure the heat exchange effect of the air conditioning unit. If the controller determines that the pressure ratio of the compressor 1 is less than the preset pressure ratio, it means that the pressure difference between the condenser 2 and the liquid injection pipe 5 is not large enough. In this case, step S109 is executed. In order to make the next judgment.
  • step S109 the controller can obtain the high-pressure pressure of the compressor 1. It should be noted that the present invention does not impose any restrictions on the specific manner in which the controller obtains the high-pressure pressure of the compressor 1, as long as the The controller can finally obtain the high pressure pressure of the compressor 1.
  • step S110 the controller can determine whether the high pressure pressure of the compressor 1 continues to be greater than the preset high pressure pressure for the fourth preset time, so as to determine whether the compressor 1 has a high pressure warning . Based on the judgment result of step S110, if the controller judges that the high pressure pressure of the compressor 1 is continuously greater than the preset high pressure pressure for the fourth preset time, it means that the compressor 1 has a high pressure warning.
  • step S106 is executed, that is, the controller no longer controls the opening degree of the electronic expansion valve 3 according to the temperature and pressure ratio of the compressor 1, so as to effectively ensure the normal operation of the compressor 1.
  • the controller determines that the high pressure of the compressor 1 continues to be greater than the preset high pressure for a time period that has not reached the fourth preset time, it means that the compressor 1 can still work normally.
  • Step S111 is executed for the next judgment.
  • the skilled person can set the size of the preset high pressure pressure and the length of the fourth preset time according to actual use requirements, as long as the high pressure pressure of the compressor 1 is continuously greater than the When the time for the preset high pressure pressure reaches the fourth preset time, it means that the compressor 1 has a high pressure warning; preferably, the preset high pressure pressure is 1000Kpa, and the fourth preset time is 5S. .
  • step S111 the controller can obtain the low-pressure pressure of the compressor 1. It should be noted that the present invention does not impose any restrictions on the specific manner in which the controller obtains the low-pressure pressure of the compressor 1, as long as the The controller can finally obtain the low pressure pressure of the compressor 1. Then, in step S112, the controller can determine whether the low-pressure pressure of the compressor 1 has been continuously less than the preset low-pressure pressure for the fifth preset time, so as to determine whether the compressor 1 has a low-pressure warning . Based on the judgment result of step S112, if the controller judges that the low pressure pressure of the compressor 1 is continuously less than the preset low pressure pressure for the fifth preset time, it means that the compressor 1 has a low pressure warning.
  • step S106 is executed, that is, the controller no longer controls the opening degree of the electronic expansion valve 3 according to the temperature and pressure ratio of the compressor 1, so as to effectively ensure the normal operation of the compressor 1.
  • the controller determines that the low-pressure pressure of the compressor 1 continues to be less than the preset low-pressure pressure for a time that has not reached the fifth preset time, it means that the compressor 1 can still work normally.
  • Step S113 is executed for the next judgment.
  • the skilled person can set the size of the preset low pressure pressure and the length of the fifth preset time according to actual needs, as long as the low pressure pressure of the compressor 1 is continuously lower than the When the preset low pressure time reaches the fifth preset time, it means that the compressor 1 has a low pressure warning; preferably, the preset low pressure pressure is 300Kpa, and the fifth preset time is 5S. .
  • the controller can determine whether the opening degree of the electronic expansion valve 3 is greater than the preset minimum opening degree, so as to determine whether the heat exchange function of the air conditioning unit can still be performed normally. It should be noted that the technician can set the size of the preset minimum opening according to actual use requirements; preferably, the preset minimum opening is 30% of the maximum opening of the electronic expansion valve 3 .
  • step S113 if the opening degree of the electronic expansion valve 3 is greater than the preset minimum opening degree, it means that the heat exchange function of the air conditioning unit can be performed normally, and because the temperature of the compressor 1 still has not decreased at this time To the preset temperature, therefore, continue to perform step S103 to further increase the pressure difference between the condenser 2 and the liquid injection pipe 5; preferably, the time interval for reducing the opening of the electronic expansion valve 3 twice Is the third preset time, and the third preset time is 10S.
  • this is not restrictive, and technicians can also set the length of the third preset time according to actual usage requirements.
  • step S114 is executed, that is, the opening degree of the electronic expansion valve 3 is no longer reduced, so as to effectively ensure the replacement of the air conditioning unit.
  • Thermal capacity In this case, the compressor 1 can only be cooled by the cooling capacity at this time. Although the cooling time is longer in this case, the temperature of the compressor 1 can still be reduced to the preset temperature in the end. .
  • the controller can always keep the real-time operating load of the compressor 1 above the preset load, so as to effectively ensure that the compressor 1 will not The temperature rises too quickly.
  • the controller adjusts the operating load of the compressor 1 according to other control logic, if the controller determines that the target load of the compressor 1 is less than the preset load, the controller controls the compression The compressor 1 runs at the preset load, so as to effectively ensure that the real-time operating load of the compressor 1 will not be lower than the preset load; at the same time, if the controller determines that the target load of the compressor 1 is greater than or equal to the If the load is preset, the controller can directly control the compressor 1 to operate at the target load.
  • the technician can set the size of the preset load by himself according to the actual situation; preferably, the preset load is 30% of the maximum load of the compressor 1.

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Abstract

一种用于空调机组的压缩机冷却控制方法，旨在解决现有空调机组对压缩机进行冷却的方式不佳的问题。该空调机组包括液喷管路（5）、主循环回路以及设置在主循环回路上的压缩机（1）、冷凝器（2）、电子膨胀阀（3）和蒸发器（4），其中，液喷管路（5）能够对压缩机（1）进行喷淋冷却，电子膨胀阀（3）设置在冷凝器（2）与蒸发器（4）之间，压缩机（1）冷却控制方法包括：获取压缩机（1）的温度；获取压缩机（1）的压比；如果压缩机（1）的温度大于预设温度且压缩机的压比小于预设压比，则根据压缩机（1）的温度和压比控制电子膨胀阀（3）的开度，从而改变冷凝器（2）与液喷管路（5）之间的压力差，进而有效保证液喷管路（5）能够向压缩机（1）中供应足够多的冷媒来进行冷却。

Description

用于空调机组的压缩机冷却控制方法 技术领域
本发明属于空调技术领域，具体涉及一种用于空调机组的压缩机冷却控制方法。
背景技术
随着人们生活水平的不断提高，人们对生活环境也提出了越来越高的要求。为了维持舒适的环境温度，空调机组已经成为人们生活中必不可少的一种设备。虽然近年来空调机组的各项设计都已经越来越成熟，但是，现有空调机组依然存在一些问题；例如，压缩机作为每个空调机组必不可少的元件，压缩机能够通过自身的压缩作用来改变冷媒的状态，因而压缩机在工作过程中很容易出现发热现象。特别是对于变频压缩机而言，变频压缩机在提速过程中很容易产生过热现象，从而导致压缩机温度过高的问题；同时，如果压缩机的温度不能及时降低，则很容易导致压缩机被烧坏，进而导致整个空调机组都无法继续正常工作的问题。由此可见，对压缩机进行喷淋冷却的操作是不容忽视的，现有空调机组通常都是通过设置液喷管路来实现冷却压缩机的效果，即通过将经过冷凝器冷却后的冷媒直接引入压缩机中来实现冷却作用。
进一步地，现有压缩机上通常都设置有冷却口，液喷管路与冷却口相连，以使液喷管路中的冷媒能够通过冷却口进入压缩机中，进入压缩机中的液体冷媒能够通过蒸发作用实现吸热效果以降低压缩机的温度，并且冷却口处还设置有电磁阀来控制液喷管路的通断。由于冷凝器内属于高压环境，因此，现有很多空调机组仅依靠这种高压作用将冷媒压入压缩机中；但是，对于空调机组刚开机或者空调机组的负荷突然增大的情况而言，压缩机通常都需要大幅提高转速，此时，压缩机会产生大量热量，冷凝器与液喷管路之间虽然存在压差，但这个压差根本就不足以提供足够多的冷媒给压缩机进行冷却，因而很容易造成压缩机冷却不足的问题，严重时甚至会影响机组的正常使用。当然，现有部分空调机组也通过在液喷管路上增设冷媒泵以保证冷媒供应，但是，由于冷 媒泵和冷却口处设置的电磁阀无法实现同步控制，因而技术人员还需要在冷媒泵的两端额外设置一路单向阀来实现旁通。在其运行过程中，当电磁阀打开时，冷媒泵能够直接将冷媒供应给压缩机来进行冷却；当电磁阀关闭时，冷媒泵中的冷媒能够通过旁通管路来进行自循环；由此可知，这种冷却结构的控制方式十分复杂，因而很容易出现错误控制。除此之外，冷媒还很容易对冷媒泵的内部结构造成气蚀，从而导致冷媒泵的可靠度和使用寿命大幅降低。
相应地，本领域需要一种新的用于空调机组的压缩机冷却控制方法来解决上述问题。
发明内容
为了解决现有技术中的上述问题，即为了解决现有空调机组对压缩机进行冷却的方式不佳的问题，本发明提供了一种用于空调机组的压缩机冷却控制方法，所述空调机组包括液喷管路、主循环回路以及设置在所述主循环回路上的压缩机、冷凝器、电子膨胀阀和蒸发器，其中，所述液喷管路能够对所述压缩机进行喷淋冷却，所述电子膨胀阀设置在所述冷凝器与所述蒸发器之间，所述压缩机冷却控制方法包括：获取所述压缩机的温度；获取所述压缩机的压比；如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，“如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤具体包括：如果所述压缩机的温度持续大于所述预设温度的时间达到第一预设时间且在所述第一预设时间内出现了所述压缩机的压比小于所述预设压比的情况，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，“如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤具体包括：如果所述压缩机的温度持续大于所述预设温度的时间 达到第二预设时间且在所述第二预设时间内所述压缩机的压比持续小于所述预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤具体包括：使所述电子膨胀阀的开度减小预设开度，其中，所述预设开度是根据所述压缩机的温度与所述预设温度的差值和/或所述压缩机的压比与所述预设压比的差值确定的。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，“使所述电子膨胀阀的开度减小预设开度”的步骤进一步包括：每隔第三预设时间，使所述电子膨胀阀的开度减小预设开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：再次获取所述压缩机的温度；如果所述压缩机的温度小于或等于所述预设温度，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：再次获取所述压缩机的压比；如果所述压缩机的压比大于或等于所述预设压比，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：获取所述压缩机的高压压力；如果所述压缩机的高压压力持续大于预设高压压力的时间达到第四预设时间，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：获取所述压缩机的低压压力；如果所述压缩机的低压压力持续小于预设低压压力的时间达 到第五预设时间，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
在上述用于空调机组的压缩机冷却控制方法的优选技术方案中，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：如果所述压缩机的目标负荷小于预设负荷，则使所述压缩机以所述预设负荷运行；如果所述压缩机的目标负荷大于或等于所述预设负荷，则使所述压缩机以所述目标负荷运行。
本领域技术人员能够理解的是，在本发明的技术方案中，本发明的空调机组包括液喷管路、主循环回路以及设置在所述主循环回路上的压缩机、冷凝器、电子膨胀阀和蒸发器，其中，所述液喷管路能够对所述压缩机进行喷淋冷却，所述电子膨胀阀设置在所述冷凝器与所述蒸发器之间，本发明的压缩机冷却控制方法包括：获取所述压缩机的温度；获取所述压缩机的压比；如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。可以理解的是，空调机组通过改变电子膨胀阀的开度就能够改变冷凝器中的压力，从而改变冷凝器与液喷管路之间的压力差，以使冷凝器中的冷媒能够通过液喷管路顺利进入压缩机中。在本发明中，在所述压缩机的温度大于所述预设温度且所述压缩机的压比小于所述预设压比的情况下，则说明压缩机存在过热现象且冷凝器与液喷管路之间的压力差不足；在此情形下，所述空调机组能够根据所述压缩机的温度和压比来控制所述电子膨胀阀的开度，以便所述空调机组能够通过改变所述电子膨胀阀的开度来改变所述冷凝器与所述液喷管路之间的压力差，从而有效保证所述液喷管路能够向所述压缩机中供应足够多的冷却冷媒，进而有效保证所述压缩机的冷却效果。
进一步地，在本发明的优选技术方案中，如果所述压缩机的温度持续大于所述预设温度的时间达到所述第一预设时间且在所述第一预设时间内出现了所述压缩机的压比小于所述预设压比的情况，则判定所述压缩机存在过热现象且所述冷凝器与所述液喷管路之间的压力差不足，以便有效提高判断结果的准确性。
进一步地，在本发明的优选技术方案中，如果所述压缩机的温度持续大于所述预设温度的时间达到所述第二预设时间且在所述第二预设时间内所述压缩机的压比持续小于所述预设压比，则判定所述压缩机存在过热现象且所述冷凝器与所述液喷管路之间的压力差不足，以便有效提高判断结果的准确性。
进一步地，在本发明的优选技术方案中，在所述压缩机存在过热现象且所述冷凝器与所述液喷管路之间的压力差不足的情况下，所述空调机组能够每隔所述第三预设时间就使所述电子膨胀阀的开度减小所述预设开度，以便所述电子膨胀阀的开度能够逐渐减小；可以理解的是，在所述电子膨胀阀的开度不断减小的过程中，大量冷媒也会逐渐蓄积在所述冷凝器中，以使所述冷凝器中的压力不断提高，从而有效提高所述冷凝器与所述液喷管路之间的压力差，进而有效提高所述液喷管路的冷媒供应速度。优选地，本发明还能够根据所述压缩机的温度与所述预设温度的差值和/或所述压缩机的压比与所述预设压比的差值确定所述预设开度；具体而言，所述压缩机的温度与所述预设温度的差值越大和/或所述压缩机的压比与所述预设压比的差值越小，则所述预设开度越大；即所述压缩机的冷却需求越强烈或者所述冷凝器与所述液喷管路之间的压力差越小，则使所述电子膨胀阀以更快的速度关小，以便更快地增大所述冷凝器与所述液喷管路之间的压力差，进而使得所述液喷管路能够尽快按需求供应冷媒。
进一步地，在本发明的优选技术方案中，如果所述压缩机的温度小于或等于所述预设温度，则说明所述压缩机的温度已经降低至足够低，不需要继续冷却，因而不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度，以便有效保证所述空调机组的换热效果。
进一步地，在本发明的优选技术方案中，如果所述压缩机的压比大于或等于所述预设压比，则说明所述冷凝器与所述液喷管路之间的压力差已经足够大，即所述液喷管路的冷媒供应速度已经足够快，因而不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度，以便有效保证所述空调机组的换热效果。
进一步地，在本发明的优选技术方案中，如果所述压缩机的高压压力持续大于所述预设高压压力的时间达到所述第四预设时间，则 说明所述压缩机已经出现高压预警，为了有效保证所述压缩机的正常工作，在此情形下，不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度，以便有效保证所述压缩机的正常工作。
进一步地，在本发明的优选技术方案中，如果所述压缩机的低压压力持续小于所述预设低压压力的时间达到所述第五预设时间，则说明所述压缩机已经出现低压预警，为了有效保证所述压缩机的正常工作，在此情形下，不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度，以便有效保证所述压缩机的正常工作。
进一步地，在本发明的优选技术方案中，如果所述压缩机的目标负荷小于所述预设负荷，则使所述压缩机以所述预设负荷运行；可以理解的是，当所述压缩机的运行负荷过小时很容易导致压缩机在运行过程中产生各种故障问题，其中就包括压缩机升温过快而容易导致温度过高的问题，因此，当所述压缩机的目标负荷小于所述预设负荷时，所述空调机组控制所述压缩机以所述预设负荷运行，以便有效保证所述压缩机能够高效工作。同时，如果所述压缩机的目标负荷大于或等于所述预设负荷，则直接使所述压缩机以所述目标负荷运行，以便有效保证所述压缩机的工作需求。
附图说明
图1是本发明的空调机组的整体结构示意图；
图2是本发明的压缩机冷却控制方法的主要步骤流程图；
图3是本发明的压缩机冷却控制方法的优选实施例的步骤流程图。
具体实施方式
下面参照附图来描述本发明的优选实施方式。本领域技术人员应当理解的是，这些实施方式仅仅用于解释本发明的技术原理，并非旨在限制本发明的保护范围。例如，尽管本申请中按照特定顺序描述了本发明的方法的各个步骤，但是这些顺序并不是限制性的，在不偏离本发明的基本原理的前提下，本领域技术人员可以按照不同的顺序来执行所述步骤。
需要说明的是，在本发明的优选实施例的描述中，术语“左”、“右”、“内”、“外”等指示的方向或位置关系的术语是基于附图所示的方向或位置关系，这仅仅是为了便于描述，而不是指示或暗示所述装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本发明的限制。此外，术语“第一”、“第二”等仅用于描述目的，而不能理解为指示或暗示相对重要性。还需要说明的是，在本发明的优选实施例的描述中，除非另有明确的规定和限定，术语“相连”、“连接”等应做广义理解，例如，可以是直接相连，也可以通过中间媒介间接相连，还可以是两个元件内部的连通。对于本领域技术人员而言，可根据具体情况理解上述术语在本发明中的具体含义。
首先参阅图1，该图是本发明的空调机组的整体结构示意图。如图1所示，本发明的空调机组包括主循环回路以及依次设置在所述主循环回路上的压缩机1、冷凝器2、电子膨胀阀3和蒸发器4，所述空调机组中的冷媒通过所述主循环回路实现循环而实现换热；当然，为了方便说明，图1中仅示出了所述空调机组的主要元件，技术人员可以根据实际使用需求自行设定所述空调机组的具体结构，本发明不对所述空调机组的具体结构作任何限制，这种具体结构的改变并不偏离本发明的基本原理，属于本发明的保护范围。所述空调机组还包括液喷管路5，压缩机1上设置冷却口，所述冷却口处设置有电磁阀，液喷管路5的一端与冷凝器2的下端相连，其另一端与所述冷却口相连，以使冷凝器2中的冷媒能够通过所述冷却口直接进入压缩机1中，设置在所述冷却口处的电磁阀能够控制液喷管路5的通断。需要说明的是，本发明不对液喷管路5的具体设置方式作任何限制，技术人员可以根据实际使用需求自行设定；例如，液喷管路5的一端还可以连接至冷凝器2和电子膨胀阀3之间，并且冷却口的具体设置位置也可以改变，只要液喷管路5能够将冷却后的冷媒直接引入压缩机1中即可。此外，所述空调机组还包括触控显示屏，使用者可以通过所述触控显示屏来控制所述空调机组的运行情况；当然，这种设置并不是限制性的，即所述空调机组也可以没有设置所述触控显示屏，或者设置有按键式显示屏等，这种具体结构的改变并不偏离本发明的基本原理。
进一步地，所述空调机组还包括温度传感器和控制器，所述温度传感器能够测量压缩机1的温度，所述控制器能够获取所述温度传感器的测量数据，并且所述控制器还能够控制所述空调机组的运行，例如，控制电子膨胀阀3的开度、控制所述电磁阀的开闭状态等。本领域技术人员能够理解的是，本发明也不对所述控制器的具体结构和型号作任何限制，只要所述控制器能够实现上述功能即可，并且所述控制器既可以是所述空调机组原有的控制器，也可以是为执行本发明的压缩机冷却控制方法而单独设置的控制器，技术人员可以根据实际使用需求自行设定所述控制器的结构和型号。此外，还需要说明的是，技术人员可以根据实际使用需求自行设定所述压缩机冷却控制方法的应用对象；由于变频压缩机极易出现温度过高的情况，优选地，将本发明的压缩机冷却控制方法应用于磁悬浮变频离心式空调机组，当然，具体应用对象的改变并不偏离本发明的基本原理，应当属于本发明的保护范围。
下面参阅图2，该图是本发明的压缩机冷却控制方法的主要步骤流程图。如图2所示，基于上述实施例中所述的空调机组，本发明的压缩机冷却控制方法主要包括下列步骤：
S1：获取压缩机的温度；
S2：获取压缩机的压比；
S3：如果压缩机的温度大于预设温度且压缩机的压比小于预设压比，则根据压缩机的温度和压比控制电子膨胀阀的开度。
进一步地，在步骤S1中，所述控制器通过所述温度传感器获取压缩机1的温度；需要说明的是，本发明不对所述控制器获取压缩机1的温度的具体方式作任何限制，只要所述控制器能够获取到压缩机1的温度即可。接着，在步骤S2中，所述控制器能够获取压缩机1的排气口绝对压力和吸气口绝对压力，然后计算出排气口绝对压力与吸气口绝对压力的比值，记作压缩机1的压比；需要说明的是，本发明不对所述控制器获取压缩机1的排气口绝对压力和吸气口绝对压力的方式作任何限制，技术人员可以根据实际使用需求自行设定，只要所述控制器最终能够获取到压缩机1的压比即可。此外，本领域技术人员还能够理解的是，步骤S1和步骤S2的执行顺序是可以自行设定的，即所述控制器既可以先获取压缩机1的温度，也可以先获取压缩机1的压比，或者所述 控制器也可以同时获取压缩机1的温度和压比，这种基础参数获取顺序的改变并不偏离本发明的基本原理。
进一步地，在步骤S3中，如果所述控制器判断出压缩机1的温度大于所述预设温度且压缩机1的压比小于所述预设压比，则说明压缩机1存在过热现象且冷凝器2与液喷管路5之间的压力差不足；此时，所述控制器能够根据压缩机1的温度和压比控制电子膨胀阀3的开度，从而改变冷凝器2与液喷管路5之间的压力差。需要说明的是，本发明不对其具体控制方式作任何限制，即技术人员可以根据实际使用需求自行设定电子膨胀阀3的开度调节方式，只要所述控制器是根据压缩机1的温度和压比来控制电子膨胀阀3的开度就属于本发明的保护范围。此外，还需要说明的是，技术人员可以根据实际使用需求自行设定所述预设温度和所述预设压比的数值，只要当压缩机1的温度大于所述预设温度时则说明压缩机1存在过热现象，并且当压缩机1的压比小于所述预设压比时则说明冷凝器2与液喷管路5之间的压力差不足即可。
最后，参阅图3，该图是本发明的压缩机冷却控制方法的优选实施例的步骤流程图。如图3所示，基于上述实施例中所述的空调机组，本发明的压缩机冷却控制方法的优选实施例具体包括下列步骤：
S101：获取压缩机的温度和压比；
S102：判断压缩机的温度是否大于预设温度且压缩机的压比是否小于预设压比；如果是，则执行步骤S103；如果否，则执行步骤S101；
S103：使电子膨胀阀的开度减小预设开度；
S104：再次获取压缩机的温度；
S105：判断压缩机的温度是否小于或等于预设温度；如果是，则执行步骤S106；如果否，则执行步骤S107；
S106：不再根据压缩机的温度和压比控制电子膨胀阀的开度；
S107：再次获取压缩机的压比；
S108：判断压缩机的压比是否大于或等于预设压比；如果是，则执行步骤S106；如果否，则执行步骤S109；
S109：获取压缩机的高压压力；
S110：判断压缩机的高压压力持续大于预设高压压力的时间是否达到第四预设时间；如果是，则执行步骤S106；如果否，则执行步骤S111；
S111：获取压缩机的低压压力；
S112：判断压缩机的低压压力持续小于预设低压压力的时间是否达到第五预设时间；如果是，则执行步骤S106；如果否，则执行步骤S113；
S113：判断电子膨胀阀的开度是否大于预设最小开度；如果是，则执行步骤S103；如果否，则执行步骤S114；
S114：不再减小电子膨胀阀的开度。
进一步地，在步骤S101中，所述控制器通过所述温度传感器获取压缩机1的温度；作为一种优选实施例，当压缩机1为变频压缩机时，所述温度传感器设置在压缩机1的变频器附近，以便获取所述变频器的温度作为压缩机1的温度。此外，还需要说明的是，本发明不对所述控制器获取压缩机1的温度的具体方式作任何限制，只要所述控制器能够获取到压缩机1的温度即可。同时，所述控制器还能够获取压缩机1的排气口绝对压力和吸气口绝对压力，然后计算出排气口绝对压力与吸气口绝对压力的比值，记作压缩机1的压比；需要说明的是，本发明不对所述控制器获取压缩机1的排气口绝对压力和吸气口绝对压力的方式作任何限制，技术人员可以根据实际使用需求自行设定，只要所述控制器最终能够获取到压缩机1的压比即可。
进一步地，在步骤S102中，所述控制器能够判断压缩机1的温度是否大于所述预设温度且压缩机1的压比是否小于所述预设压比；需要说明的是，技术人员可以根据实际使用需求自行设定所述预设温度和所述预设压比的数值，只要当压缩机1的温度大于所述预设温度时则说明压缩机1存在过热现象，并且当压缩机1的压比小于所述预设压比时则说明冷凝器2与液喷管路5之间的压力差不足即可；优选地，所述预设温度为50℃，所述预设压比为1.5。此外，本领域技术人员能够理解的是，虽然本优选实施例中是通过判断压缩机1的温度是否大于所述预设温度和压缩机1的压比是否小于所述预设压比的方式来判断压缩机1的冷却需求和冷却情况，但是，这种判断方式并不是限制性的，技术人 员可以根据实际使用情况自行设定具体判断方式，例如，还可以通过判断压缩机1的温度持续大于所述预设温度的时间是否达到第一预设时间且在所述第一预设时间内是否出现压缩机1的压比小于所述预设压比的情况，或者通过判断压缩机1的温度持续大于所述预设温度的时间是否达到第二预设时间且在所述第二预设时间内压缩机1的压比是否也持续小于所述预设压比，这种具体判断方式的改变并不偏离本发明的基本原理，属于本发明的保护范围内。
进一步地，基于步骤S102的判断结果，如果所述控制器判断出压缩机1的温度大于所述预设温度且压缩机1的压比小于所述预设压比，则说明压缩机1存在过热现象且冷凝器2与液喷管路5之间的压力差不足；在此情形下，执行步骤S103，即所述控制器能够控制电子膨胀阀3的开度减小预设开度，以便快速增大冷凝器2中的压力。需要说明的是，技术人员可以根据实际使用需求自行设定所述预设开度的大小，所述预设开度既可以是一个常数值，也可以是一个变化值；优选地，所述控制器能够根据压缩机1的温度与所述预设温度的差值和压缩机1的压比与所述预设压比的差值确定所述预设开度的大小，当然，这种设定方式并不是限制性的。同时，如果所述控制器判断出压缩机1的温度不大于所述预设温度，则说明压缩机1不存在过热现象，如果压缩机1的压比不小于所述预设压比，则说明冷凝器2与液喷管路5之间的压力差足够；在此情形下，再次执行步骤S101即可。
进一步地，在电子膨胀阀3的开度减小所述预设开度之后，执行步骤S104，即所述控制器能够再次获取压缩机1的温度，以便判断压缩机1的冷却情况。接着，在步骤S105中，所述控制器能够判断压缩机1的温度是否小于或等于所述预设温度，以便判断压缩机1是否已经得到足够的冷却。基于步骤S105的判断结果，如果所述控制器判断出压缩机1的温度小于或等于所述预设温度，则说明压缩机1的温度已经足够低，在此情形下，执行步骤S106，即所述控制器不再根据压缩机1的温度和压比控制电子膨胀阀3的开度，以便有效保证所述空调机组的换热效果。同时，如果所述控制器判断出压缩机1的温度大于所述预设温度，则说明压缩机1的温度还不够低，在此情形下，执行步骤S107，以便进行下一步判断。
进一步地，在步骤S107中，所述控制器再次获取压缩机1的压比，以便间接判断液喷管路5中的冷媒流量情况。接着，在步骤S108中，所述控制器能够再次判断压缩机1的压比是否大于或等于所述预设压比，以便判断液喷管路5的冷媒供应量是否达标。基于步骤S108的判断结果，如果所述控制器判断出压缩机1的压比大于或等于所述预设压比，则说明冷凝器2与液喷管路5之间的压力差已经足够大，在此情形下，执行步骤S106，即所述控制器不再根据压缩机1的温度和压比控制电子膨胀阀3的开度，以便有效保证所述空调机组的换热效果。如果所述控制器判断出压缩机1的压比小于所述预设压比，则说明冷凝器2与液喷管路5之间的压力差还不够大，在此情形下，执行步骤S109，以便进行下一步判断。
进一步地，在步骤S109中，所述控制器能够获取压缩机1的高压压力；需要说明的是，本发明不对所述控制器获取压缩机1的高压压力的具体方式作任何限制，只要所述控制器最终能够获取到压缩机1的高压压力即可。接着，在步骤S110中，所述控制器能够判断压缩机1的高压压力持续大于所述预设高压压力的时间是否达到所述第四预设时间，以便判断压缩机1是否出现高压预警的情况。基于步骤S110的判断结果，如果所述控制器判断出压缩机1的高压压力持续大于所述预设高压压力的时间达到所述第四预设时间，则说明压缩机1已经出现高压预警的情况，在此情形下，执行步骤S106，即所述控制器不再根据压缩机1的温度和压比控制电子膨胀阀3的开度，以便有效保证压缩机1的正常工作。同时，如果所述控制器判断出压缩机1的高压压力持续大于所述预设高压压力的时间未达到所述第四预设时间，则说明压缩机1还能够正常工作，在此情形下，执行步骤S111，以便进行下一步判断。本领域技术人员能够理解的是，技术人员可以根据实际使用需求自行设定所述预设高压压力的大小和所述第四预设时间的长短，只要当压缩机1的高压压力持续大于所述预设高压压力的时间达到所述第四预设时间时就说明压缩机1已经出现高压预警的情况即可；优选地，所述预设高压压力为1000Kpa，所述第四预设时间为5S。
进一步地，在步骤S111中，所述控制器能够获取压缩机1的低压压力；需要说明的是，本发明不对所述控制器获取压缩机1的低 压压力的具体方式作任何限制，只要所述控制器最终能够获取到压缩机1的低压压力即可。接着，在步骤S112中，所述控制器能够判断压缩机1的低压压力持续小于所述预设低压压力的时间是否达到所述第五预设时间，以便判断压缩机1是否出现低压预警的情况。基于步骤S112的判断结果，如果所述控制器判断出压缩机1的低压压力持续小于所述预设低压压力的时间达到所述第五预设时间，则说明压缩机1已经出现低压预警的情况，在此情形下，执行步骤S106，即所述控制器不再根据压缩机1的温度和压比控制电子膨胀阀3的开度，以便有效保证压缩机1的正常工作。同时，如果所述控制器判断出压缩机1的低压压力持续小于所述预设低压压力的时间未达到所述第五预设时间，则说明压缩机1还能够正常工作，在此情形下，执行步骤S113，以便进行下一步判断。本领域技术人员能够理解的是，技术人员可以根据实际使用需求自行设定所述预设低压压力的大小和所述第五预设时间的长短，只要当压缩机1的低压压力持续小于所述预设低压压力的时间达到所述第五预设时间时就说明压缩机1已经出现低压预警的情况即可；优选地，所述预设低压压力为300Kpa，所述第五预设时间为5S。
需要说明的是，判断步骤S105、S108、S110和S112的执行顺序是可以随意调换的，这种具体步骤执行顺序之间的调换并不偏离本发明的基本原理，属于本发明的保护范围。
进一步地，在步骤S113中，所述控制器能够判断电子膨胀阀3的开度是否大于所述预设最小开度，以便判断所述空调机组的换热功能是否还能够正常执行。需要说明的是，技术人员可以根据实际使用需求自行设定所述预设最小开度的大小；优选地，所述预设最小开度为电子膨胀阀3的最大开度的百分之三十。基于步骤S113的判断结果，如果电子膨胀阀3的开度大于所述预设最小开度，则说明所述空调机组的换热功能能够正常执行，并且由于此时压缩机1的温度还是没有降低至所述预设温度，因此，继续执行步骤S103，以便进一步增大冷凝器2与液喷管路5之间的压力差；优选地，两次减小电子膨胀阀3的开度的时间间隔为第三预设时间，并且所述第三预设时间为10S。当然，这并不是限制性的，技术人员也可以根据实际使用需求自行设定所述第三预设时间的长短。同时，如果电子膨胀阀3的开度已经小于或等于所述预设最 小开度，则执行步骤S114，即不再继续减小电子膨胀阀3的开度，以便有效保证所述空调机组的换热能力。在此情形下，只能继续依靠此时的冷却能力对压缩机1进行冷却，虽然此情形下需要的冷却时间较长，但是最终依然还是能够将压缩机1的温度降低至所述预设温度。
此外，还需要说明的是，在步骤S103至步骤S114的执行期间，所述控制器能够始终将压缩机1的实时运行负荷保持在所述预设负荷之上，以便有效保证压缩机1不会出现过快升温的情况。具体地，在所述控制器根据其他控制逻辑对压缩机1的运行负荷进行调节时，如果所述控制器判断出压缩机1的目标负荷小于所述预设负荷，则所述控制器控制压缩机1以所述预设负荷运行，以便有效保证压缩机1的实时运行负荷不会低于所述预设负荷；同时，如果所述控制器判断出压缩机1的目标负荷大于或等于所述预设负荷，则所述控制器直接控制压缩机1以所述目标负荷运行即可。本领域技术人员能够理解的是，技术人员可以根据实际情况自行设定所述预设负荷的大小；优选地，所述预设负荷为压缩机1的最大负荷的百分之三十。
最后需要说明的是，上述实施例均是本发明的优选实施方案，并不作为对本发明保护范围的限制。本领域技术人员在实际使用本发明时，可以根据需要适当添加或删减一部分步骤，或者调换不同步骤之间的顺序。这种改变并没有超出本发明的基本原理，属于本发明的保护范围。
至此，已经结合附图描述了本发明的优选实施方案，但是，本领域技术人员容易理解的是，本发明的保护范围显然不局限于这些具体实施方式。在不偏离本发明的原理的前提下，本领域技术人员可以对相关技术特征作出等同的更改或替换，这些更改或替换之后的技术方案都将落入本发明的保护范围之内。

Claims (10)

  1. 一种用于空调机组的压缩机冷却控制方法，其特征在于，所述空调机组包括液喷管路、主循环回路以及设置在所述主循环回路上的压缩机、冷凝器、电子膨胀阀和蒸发器，其中，所述液喷管路能够对所述压缩机进行喷淋冷却，所述电子膨胀阀设置在所述冷凝器与所述蒸发器之间，
    所述压缩机冷却控制方法包括：
    获取所述压缩机的温度；
    获取所述压缩机的压比；
    如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  2. 根据权利要求1所述的压缩机冷却控制方法，其特征在于，“如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤具体包括：
    如果所述压缩机的温度持续大于所述预设温度的时间达到第一预设时间且在所述第一预设时间内出现了所述压缩机的压比小于所述预设压比的情况，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  3. 根据权利要求1所述的压缩机冷却控制方法，其特征在于，“如果所述压缩机的温度大于预设温度且所述压缩机的压比小于预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤具体包括：
    如果所述压缩机的温度持续大于所述预设温度的时间达到第二预设时间且在所述第二预设时间内所述压缩机的压比持续小于所述预设压比，则根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  4. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的 步骤具体包括：
    使所述电子膨胀阀的开度减小预设开度，其中，所述预设开度是根据所述压缩机的温度与所述预设温度的差值和/或所述压缩机的压比与所述预设压比的差值确定的。
  5. 根据权利要求4所述的压缩机冷却控制方法，其特征在于，“使所述电子膨胀阀的开度减小预设开度”的步骤进一步包括：
    每隔第三预设时间，使所述电子膨胀阀的开度减小预设开度。
  6. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：
    再次获取所述压缩机的温度；
    如果所述压缩机的温度小于或等于所述预设温度，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  7. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：
    再次获取所述压缩机的压比；
    如果所述压缩机的压比大于或等于所述预设压比，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  8. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：
    获取所述压缩机的高压压力；
    如果所述压缩机的高压压力持续大于预设高压压力的时间达到第四预设时间，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  9. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：
    获取所述压缩机的低压压力；
    如果所述压缩机的低压压力持续小于预设低压压力的时间达到第五预设时间，则不再根据所述压缩机的温度和压比控制所述电子膨胀阀的开度。
  10. 根据权利要求1至3中任一项所述的压缩机冷却控制方法，其特征在于，在执行“根据所述压缩机的温度和压比控制所述电子膨胀阀的开度”的步骤之后，所述压缩机冷却控制方法还包括：
    如果所述压缩机的目标负荷小于预设负荷，则使所述压缩机以所述预设负荷运行；
    如果所述压缩机的目标负荷大于或等于所述预设负荷，则使所述压缩机以所述目标负荷运行。
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