WO2017096992A1 - 带有中间补气的压缩系统、空调系统及其判断控制方法 - Google Patents

带有中间补气的压缩系统、空调系统及其判断控制方法 Download PDF

Info

Publication number
WO2017096992A1
WO2017096992A1 PCT/CN2016/098676 CN2016098676W WO2017096992A1 WO 2017096992 A1 WO2017096992 A1 WO 2017096992A1 CN 2016098676 W CN2016098676 W CN 2016098676W WO 2017096992 A1 WO2017096992 A1 WO 2017096992A1
Authority
WO
WIPO (PCT)
Prior art keywords
air supply
compressor
valve
liquid
compression system
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/CN2016/098676
Other languages
English (en)
French (fr)
Inventor
赵桓
谭锋
李鹏飞
梁尤轩
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.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to US16/060,695 priority Critical patent/US10330350B2/en
Priority to CA3007722A priority patent/CA3007722C/en
Publication of WO2017096992A1 publication Critical patent/WO2017096992A1/zh
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Images

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
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
    • 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
    • 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
    • F24F11/89—Arrangement or mounting of control or safety devices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
    • 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
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • F25B49/022—Compressor control arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/077—Compressor control units, e.g. terminal boxes, mounted on the compressor casing wall containing for example starter, protection switches or connector contacts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—Component parts or details not otherwise provided for in this subclass
    • F25B2400/23—Separators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/02—Increasing the heating capacity of a reversible cycle during cold outdoor conditions
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/03—Cavitations
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • 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
    • F25B2500/00—Problems to be solved
    • F25B2500/31—Low ambient temperatures
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/02—Compressor control
    • 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
    • F25B2600/2509—Economiser 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
    • F25B2700/19—Pressures
    • F25B2700/193—Pressures of the compressor
    • F25B2700/1931—Discharge pressures
    • 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
    • F25B2700/21152—Temperatures of a compressor or the drive means therefor at the discharge side of the compressor

Definitions

  • the invention belongs to the technical field of air conditioners, and particularly relates to a compression system with an intermediate air supply, an air conditioning system and a judgment and control method thereof.
  • the single-stage compression heat pump can only start at normal operation at minus 20 degrees, and the heat generation is seriously attenuated. The heating effect cannot be guaranteed, and the reliability of the unit is also severe. The test.
  • the two-stage compression system with jet boosting has higher heat generation at higher temperatures and higher energy efficiency.
  • the two-stage compression system can reduce the pressure ratio of the single-stage compressor, reduce the exhaust gas temperature, and improve the suction efficiency and compression efficiency, thereby improving the heating and heating efficiency.
  • the two-stage compression with jet boosting is divided into a high pressure stage and a low pressure stage, which has two or more cylinders, wherein the first stage compressor is called a low pressure cylinder, and the second stage compression is called a high pressure cylinder.
  • the principle of jet boosting is to inject gaseous refrigerant into the suction port of the compressor high pressure cylinder from the jet increase port in the middle of the compressor. The injected gaseous refrigerant will be mixed with the refrigerant discharged after being compressed by the low pressure cylinder, and then enter the high pressure cylinder. compression.
  • the intermediate jet has a very important influence on the performance and reliability of the system.
  • the jet liquid will cause the lubricating oil in the compressor to dilute, and when more liquid refrigerant enters the compressor cylinder at a higher speed.
  • the suction valve piece may be excessively bent or broken, and the cylinder may be severely worn. Closing the intermediate jet control valve can effectively prevent the jet of liquid from flowing for the long-term operation of the compressor, but greatly reduces the performance of the two-stage compression system.
  • the intermediate jet needs both normal opening and timely closing when the jet is liquid, and how to detect and judge the jet flow and the accuracy of the judgment will affect the performance and reliability of the two-stage compression system.
  • the method of detecting the superheat of qi is used to determine whether the middle qi is liquid, but this method is judged to be single, and the following deficiencies exist: First, when the qi sensible temperature pack is placed behind the air supply valve, due to the intermediate compensation The valve has a certain throttling, which causes the temperature of the qi detection to decrease, so that the detection of the superheat of the qi is low and the plenum valve is often closed, causing the valve to be normally closed; the second is when the qi is inflated.
  • the detected air temperature is higher, and the superheat of the air supply is too large, which may result in the detection of a small amount of liquid in the air, and the reliability of the compressor cannot be guaranteed.
  • the compression system in the prior art cannot accurately determine whether the intermediate qi is liquid, and it is impossible to judge the state of a small amount of liquid and a large amount of liquid, which may cause a liquid hammer in the compressor, and is reliable.
  • the technical problem is not guaranteed, so the present invention studies a compression system with an intermediate air supply, an air conditioning system, and a judgment control method thereof.
  • the technical problem to be solved by the present invention is to overcome the defect that the compression system in the prior art cannot accurately determine whether the intermediate air supply is liquid, thereby providing a compression system with an intermediate air supply, an air conditioning system and Determine the control method.
  • the present invention provides a compression system with an intermediate air supply, comprising a compressor, an intermediate air supply line, and an air supply valve disposed on the intermediate air supply line, wherein the refrigerant is located on the intermediate gas supply line according to the flow direction of the refrigerant.
  • the inlet end of the air supply valve is provided with a first pressure detecting device and a first temperature detecting device, and at the outlet end of the air filling valve, a second temperature detecting device is provided, the system further comprising a compressor exhaust disposed at the compressor a second pressure detecting device and a third temperature detecting device on the pipeline.
  • the first temperature detecting device is a first tempering temperature sensing package
  • the second temperature detecting device is a second tempering temperature sensing package
  • the third temperature detecting device is a venting temperature sensing package.
  • the first pressure detecting device is a medium pressure sensor
  • the second pressure detecting device is a high pressure sensor
  • the makeup valve is a two-way valve.
  • the makeup valve is an electromagnetic expansion valve.
  • one end of the intermediate makeup line is connected to the intermediate pressure suction end of the compressor.
  • the compression system further includes a flasher, and the other end of the intermediate makeup line is connected to the flasher.
  • the compressor is a two-stage compressor.
  • the present invention also provides an air conditioning system comprising the aforementioned compression system with an intermediate plenum.
  • the invention also provides a judgment control method for a compression system with intermediate air supply, which is directed to The aforementioned compression system with intermediate air supply performs control adjustment of the intermediate air supply.
  • the corrected superheat degree detected and calculated by the first pressure detecting means and the first temperature detecting means, and the temperature difference before and after the intake valve detected and calculated by the first temperature detecting means and the second temperature detecting means are passed and passed.
  • the exhaust gas superheat degree detected and calculated by the second pressure detecting device and the third temperature detecting device are simultaneously determined to determine whether or not the intermediate supplemental superheat degree is liquid.
  • the values of SH1, SH2 and TH are detected and calculated every T1 minute interval during the operation of the compressor, and when SH2 ⁇ a, the conditions of SH1 and TH are further determined:
  • a is the specified exhaust superheat
  • b is the specified supplemental superheat
  • c is the specified pre-valve difference
  • T1 is the specified time interval, which is the set constant.
  • the values of SH1, SH2 and TH are detected and calculated every T1 minute interval when the compressor is running, and when SH2 ⁇ a, the conditions of SH1 and TH are further determined:
  • a is the specified exhaust superheat
  • b is the specified supplemental superheat
  • c is the specified pre-valve difference
  • T1 is the specified time interval, which is the set constant.
  • the specified supplemental superheat b is 0, and the specified infill valve front-to-back difference c is 1.
  • the air supply valve is further accurately controlled based on the judgment result of the air supply belt.
  • the air supply valve is a two-way valve
  • the two-way valve is immediately closed based on reliability considerations.
  • the air supply valve is an electronic expansion valve
  • the opening of the electronic expansion valve is adjusted; and when it is judged that the qi is severely charged, the electronic expansion valve is immediately closed.
  • the invention provides a compression system with an intermediate air supply, an air conditioning system and a judgment and control method thereof, which have one or more of the following beneficial effects:
  • a compression system with intermediate qi provided by the design of the invention can accurately determine whether the qi in the middle of the compressor is liquid
  • the invention combines the air supply control of the electronic expansion valve, can accurately control the air supply amount and the air supply state, and improves the system operation efficiency while ensuring the long-term reliability of the two-stage compressor;
  • Figure 1 is a schematic view showing the structure of a compression system with an intermediate qi according to the present invention
  • Fig. 2 is a flow chart showing the judgment control flow of the judgment control method of the compression system with intermediate air supply according to the present invention.
  • 1 compressor
  • 2 intermediary air supply line
  • 3 invalid air valve
  • 4 first pressure detecting device
  • 5 first temperature detecting device
  • 6 second temperature detecting device
  • 7 second pressure detecting device
  • 8 third temperature detecting device
  • 9 flasher
  • 11 exhaust line
  • 12 medium pressure suction end.
  • the present invention provides a compression system with an intermediate air supply, comprising a compressor 1, an intermediate air supply line 2, and an air supply valve 3 disposed on the intermediate air supply line 2, wherein According to the flow direction of the refrigerant, a first pressure detecting device 4 and a first temperature detecting device 5 are disposed at the inlet end of the makeup valve 3 on the intermediate air supply line 2, and a second portion is disposed at the outlet end of the air supply valve 3.
  • the temperature detecting device 6 further includes a second pressure detecting device 7 and a third temperature detecting device 8 disposed on the exhaust line 11 of the compressor 1.
  • the compression system with intermediate qi provided by the design of the invention can detect and calculate the superheat of the supplement by the first, second and third temperature detecting devices and the first and second pressure detecting devices.
  • the temperature difference before and after the gas valve and the superheat of the exhaust gas can be effectively judged whether or not there is liquid in the middle qi by synchronizing the three; and the system can also distinguish a small amount of liquid and a large amount of qi.
  • the intermediate air supply of the two-stage compressor can be effectively controlled to avoid the liquid blow of the compressor, and the reliable and efficient operation of the two-stage compressor can be guaranteed for a long time.
  • the method is simple and reliable, and the cost is low.
  • the first temperature detecting device 5 is a first tempering temperature sensing package
  • the second temperature detecting device 6 is a second tempering temperature sensing package
  • the third temperature detecting device 8 is a venting temperature sensing device. package.
  • the first temperature detecting device as the first tempering temperature sensing package is a preferred type and selection, it is possible to accurately detect the temperature at the front end of the intermediate air supply line (in the flow direction of the refrigerant), Calculating the superheat of the supplemental gas at this point provides an effective precondition; by selecting the second temperature detecting device as the second tempering temperature sensing package is also a preferred type and selection, and the intermediate air supply line can be accurately detected.
  • the temperature at the rear end of the gas valve (according to the flow direction of the refrigerant) provides an effective precondition for calculating the temperature difference before and after the air supply valve; selecting the exhaust temperature sensing package by the third temperature detecting device 8 is also a preferred type. And the selection can accurately detect the exhaust temperature of the compressor exhaust line 11, and thus provide an effective precondition for calculating the superheat of the exhaust gas at the place.
  • the first pressure detecting device 4 is a medium pressure sensor
  • the second pressure detecting device 7 is a high pressure sensor.
  • the first pressure detecting device is a preferred type and selection, it is possible to accurately detect the pressure (medium pressure) at the front end of the air supply valve of the intermediate air supply line (in the flow direction of the refrigerant), and then calculate The value of the saturated steam temperature under the pressure state is obtained, which provides an effective precondition for calculating the superheat of the supplemental gas;
  • the selection of the second pressure detecting device as the high pressure sensor is also a preferred type and selection, and can be accurate.
  • the pressure condition (high pressure) of the compressor exhaust line 11 is detected, and the saturated steam temperature value under the pressure state is calculated, which provides an effective method for calculating the superheat degree of the exhaust gas at the place. Prerequisites.
  • the makeup valve 3 is a two-way valve.
  • This is a preferred type and implementation of the air supply valve.
  • the two-way valve can effectively open or close according to whether the intermediate air supply is liquid or not, thereby performing the control operation to prevent the liquid hammer phenomenon of the compressor. Improve the reliability of operation.
  • the makeup valve 3 is an electromagnetic expansion valve.
  • This is also a preferred type and embodiment of the air supply valve.
  • the electromagnetic expansion valve can effectively open or close according to whether the intermediate air supply is liquid or not, and can also be lightly or according to the intermediate air supply. It is a serious operation to reduce or decrease the opening degree, and the operation of the control is performed to prevent the occurrence of liquid shock of the compressor and improve the reliability of the operation.
  • one end of the intermediate supplemental gas line 2 is connected to the intermediate pressure suction end 12 of the compressor 1.
  • the refrigerant in the intermediate air supply line can be effectively added to the intermediate pressure suction end of the compressor, thereby effectively functioning as a gas supplement.
  • the compression system further comprises a flasher 9, and the other end of the intermediate supplemental gas line 2 is connected to the flasher 9.
  • the flasher By setting the flasher, it is effective to flash-evaporate the refrigerant with liquid and gaseous state, so that the gaseous and liquid refrigerants are effectively separated, and the gaseous refrigerant enters the medium pressure of the compressor through the intermediate gas supply line.
  • the inhalation end can effectively function as a qi and augmentation.
  • the compressor 1 is a two-stage compressor.
  • This is a preferred type and embodiment of the compressor of the present invention, the purpose of which is to perform two-stage supercharging, reduce the compression ratio of a single compressor, and increase the enthalpy between the stages to improve the enthalpy of the refrigerant operation.
  • it is not limited to a two-stage compressor, and may be a multi-stage type or a structure in which two or more compressors are connected in series.
  • the present invention also provides an air conditioning system comprising the aforementioned compression system with an intermediate plenum.
  • the air conditioning system including the compression system with the intermediate air supply, the first, second, third temperature detecting device and the first and second pressure detecting devices can detect and calculate the air supply superheat degree and the air supply valve before and after the air supply valve
  • the temperature difference and the superheat of the exhaust gas can be effectively judged whether or not there is a liquid in the middle qi by synchronizing the three; and the system can also distinguish a small amount of liquid with a small amount of liquid and a large amount of liquid.
  • the state can effectively control the intermediate air supply of the two-stage compressor to avoid the liquid hammer generated by the compressor, and can ensure the reliable and efficient operation of the two-stage compressor for a long time.
  • the method is simple and reliable, and the cost is low.
  • the present invention also provides a judgment control method for a compression system with an intermediate air supply, which performs control adjustment of the intermediate air supply for the aforementioned compression system with intermediate air supply.
  • the first, second, and third temperature detecting devices and the first and second pressure detecting devices can detect and calculate the supplemental superheat degree,
  • the temperature difference before and after the air supply valve and the superheat of the exhaust gas can be effectively judged whether or not there is liquid in the middle qi by synchronously judging the three; and the system can also distinguish a small amount of liquid from the qi and A large amount of liquid state, so that the intermediate air supply of the two-stage compressor can be effectively controlled to avoid liquid hammer generated by the compressor, and the reliable and efficient operation of the two-stage compressor can be guaranteed for a long time.
  • the method is simple and reliable, and the cost is low.
  • the corrected superheat degree detected and calculated by the first pressure detecting means and the first temperature detecting means, and the temperature difference before and after the intake valve detected and calculated by the first temperature detecting means and the second temperature detecting means are passed and passed
  • the exhaust gas superheat degree detected and calculated by the second pressure detecting device and the third temperature detecting device are simultaneously determined to determine whether or not the intermediate supplemental superheat degree is liquid. This is a specific method of judgment. The method can accurately determine the condition of the qi-filled liquid, and can distinguish the state of a small amount of liquid with a small amount of liquid and a large amount of liquid, which can ensure the reliable operation and efficient operation of the compressor for a long time.
  • This is a specific detection and calculation step for judging the process of the superheating degree SH1 and the exhaust superheat SH2 and the temperature difference TH before and after the air supply valve.
  • the compressor operates at intervals of T1 minutes (T1 can be set as needed), detects the temperature before and after the air inlet valve Tm1 and Tm2, the exhaust gas temperature Td, the supplemental pressure and the exhaust pressure, and calculates the supplemental superheat degree SH1.
  • T1 can be set as needed
  • the specific judgment method is as follows:
  • a is the specified exhaust superheat
  • b is the specified supplemental superheat
  • c is the specified pre-valve difference
  • T1 is the specified time interval, which is the set constant.
  • the situation of SH1 and TH is further determined:
  • a is the specified exhaust superheat
  • b is the specified supplemental superheat
  • c is the specified pre- and post-valve difference, which are all set constants, and the size is determined according to the system scheme.
  • the specified supplemental superheat b is 0, and the specified infill valve difference is c is 1.
  • Further c values may preferably be selected to be 1, 1.5 or 2 depending on the difference in the system.
  • the air supply valve is further accurately controlled based on the judgment result of the air supply belt.
  • the air valve is controlled by the judgment result to achieve effective control of the liquid in the middle of the compressor, and the liquid is prevented from entering the compressor to form a liquid hammer, thereby ensuring reliable operation.
  • the air supply valve is a two-way valve
  • the two-way valve when it is judged that the air supply is slightly liquid, the two-way valve is immediately closed based on reliability considerations (ie, from the viewpoint of reliability).
  • This is a specific control means for the air supply valve as a preferred embodiment of the two-way valve, which can effectively prevent liquid from entering the compressor.
  • the air supply valve is an electronic expansion valve
  • the opening of the electronic expansion valve is adjusted to reduce the liquid pressure of the compressor while maintaining the efficient operation of the system;
  • the electronic expansion valve is immediately closed, thereby protecting the long-term reliable operation of the compressor. This keeps the system efficient and long-term reliable while protecting the compressor from liquid impact.
  • the present invention adopts a method of synchronously judging the degree of superheat of the air, the temperature difference before and after the air supply valve, and the superheat of the exhaust gas to determine whether the intermediate superheating degree is liquid.
  • the method can accurately determine the condition of the qi-filled liquid, and can distinguish the state of a small amount of liquid with a small amount of liquid and a large amount of liquid, which can ensure the reliable operation and efficient operation of the compressor for a long time.
  • the supplemental air temperature 1, the supplemental air temperature 2, and the exhaust gas temperature detected by the compressor first temperature detecting device 5, the second temperature detecting device 6, and the third temperature detecting device 8 are defined as Tm1, Tm2, and Td, respectively.
  • the position of each temperature sensor and pressure sensor is shown in Figure 1.
  • the intermediate pressure detected by the medium pressure sensor at the tempering temperature sensor is Pm, and the corresponding saturated steam temperature is Tmc.
  • the exhaust pressure detected by the high pressure sensor at the exhaust sensible temperature package is Pd, and the corresponding saturated steam temperature is Tdc.
  • the supplemental superheat and exhaust superheat to SH1 and SH2, respectively, and the temperature difference before and after the supplemental valve is TH, then:
  • the scheme is based on the superheat of the supplemental air, and the supplemental temperature sensor and the medium pressure sensor are installed between the supplemental gas control valve and the flasher, as shown in Fig. 1, and the second temperature detecting device 6 is added at the same time.
  • the exhaust superheat is used as a basis for judging, and it is possible to accurately determine whether or not the intermediate qi is liquid.
  • the compressor is running for T1 minutes, check the temperature before and after the air supply valve Tm1 and Tm2, the exhaust gas temperature Td, the supplemental pressure and the exhaust pressure, calculate the supplementary air superheat degree SH1, the exhaust superheat degree SH2 and the temperature before and after the air supply valve.
  • the difference TH as shown in Figure 2, is determined as follows:
  • SH2 ⁇ a, SH1 and TH have the following conditions:
  • SH2 ⁇ a, SH1 and TH have the following conditions:
  • the air supply valve can be precisely controlled. For example, if the air supply control valve uses a two-way valve, when it is judged that the air supply is slightly liquid, the air supply valve can be immediately closed based on the reliability angle; if the air supply control valve uses an electronic expansion valve, when it is judged that the air supply is slightly liquid, Adjust the opening of the small qi electronic expansion valve to keep the system running efficiently while protecting the compressor from liquid shock. When the state of the system changes suddenly, from the state of nourishing air to the state of severe liquid, the air supply valve should be closed immediately to protect the long-term reliable operation of the compressor.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air Conditioning Control Device (AREA)
  • Control Of Positive-Displacement Pumps (AREA)

Abstract

一种带有中间补气的压缩系统、空调系统及其及判断控制方法，包括压缩机(1)、中间补气管路(2)和设置于所述中间补气管路(2)上的补气阀(3)，其中按照制冷剂流向，在中间补气管路(2)上位于补气阀(3)的进口端设置有第一压力检测装置(4)和第一温度检测装置(5)、位于其出口端设置有第二温度检测装置(6)，所述系统还包括设置在所述压缩机(1)排气管路上(11)的第二压力检测装置(7)和第三温度检测装置(8)。通过本发明能够准确地判断压缩机中间补气是否带液及补气少量和大量带液的情况，从而避免由于中间补气带液而造成压缩机中的润滑油稀释、压缩机磨损甚至产生液击的情况的发生。

Description

带有中间补气的压缩系统、空调系统及其判断控制方法 技术领域
本发明属于空调技术领域，具体涉及一种带有中间补气的压缩系统、空调系统及其判断控制方法。
背景技术
环境温度越低，对空调制热量的需求越大，但目前单级压缩的热泵只能做到零下20度正常启动运行，且制热量严重衰减，制热效果不能保证，机组可靠性也受到严峻的考验。
相比单级压缩热泵，带有喷气增焓双级压缩系统在低温下制热量较大，能效较高。且双级压缩系统能减少单级压缩机的压比，降低排气温度，同时可提高吸气效率和压缩效率，从而提升制热量和制热效率。
带有喷气增焓双级压缩分为高压级和低压级，它具有两个或以上的气缸，其中用于第一级压缩机的称为低压缸，用于第二级压缩的称为高压缸。喷气增焓的原理是从压缩机中部的喷气增焓口将气态冷媒喷入压缩机高压缸的吸气口，喷入的气态冷媒将与经过低压缸压缩后排出的冷媒混合，然后进入高压缸压缩。
在双级压缩喷气增焓系统中，中间喷气对系统性能和可靠性有非常重要的影响，喷气带液将导致压缩机中润滑油稀释，当有较多液态冷媒以较高速度进入压缩机气缸时，由于液体的冲击和不可压缩，会引起吸气阀片过度弯曲或断裂，以及气缸严重磨损的情况。而关闭中间喷气控制阀可以有效避免喷气带液有利于压缩机长期运行，但大大降低了双级压缩系统的性能。
因此，中间喷气既需要常开又需要在喷气带液时及时关闭，而如何检测及判断喷气带液以及判断的准确性将影响双级压缩系统的性能和可靠性。目前多采用检测补气过热度的方法来判别中间补气是否带液，但此种方法判断单一，且存在以下不足：一是当补气感温包放在补气阀后时，由于中间补气阀带有一定的节流导致补气检测温度降低，以致检测补气过热度偏低而经常关闭补气阀，造成补气阀常关的现象；二是当补气感 温包放在补气阀前时，所检测的补气温度较高，补气过热度偏大，导致在喷气少量带液时检测不出来的情况，压缩机可靠性得不到保证。
由于现有技术中的压缩系统存在无法准确判断中间补气是否带液的情况，且无法判断出补气少量带液和大量带液的状态，从而导致压缩机有可能发生液击的情况，可靠性得不到保证等的技术问题，因此本发明研究设计出一种带有中间补气的压缩系统、空调系统及其判断控制方法。
发明内容
因此，本发明要解决的技术问题在于克服现有技术中的压缩系统存在无法准确判断中间补气是否带液的情况的缺陷，从而提供一种带有中间补气的压缩系统、空调系统及其判断控制方法。
本发明提供一种带有中间补气的压缩系统，包括压缩机、中间补气管路和设置于所述中间补气管路上的补气阀，其中按照制冷剂流向，在中间补气管路上位于所述补气阀的进口端设置有第一压力检测装置和第一温度检测装置、位于所述补气阀的出口端设置有第二温度检测装置，所述系统还包括设置在所述压缩机排气管路上的第二压力检测装置和第三温度检测装置。
优选地，所述第一温度检测装置为第一补气感温包，所述第二温度检测装置为第二补气感温包，所述第三温度检测装置为排气感温包。
优选地，所述第一压力检测装置为中压传感器，所述第二压力检测装置为高压传感器。
优选地，所述补气阀为二通阀。
优选地，所述补气阀为电磁膨胀阀。
优选地，所述中间补气管路的一端连接到所述压缩机的中压吸气端。
优选地，所述压缩系统还包括闪发器，且所述中间补气管路的另一端连接到所述闪发器。
优选地，所述压缩机为双级式压缩机。
本发明还提供一种空调系统，其包括前述的带有中间补气的压缩系统。
本发明还提供一种带有中间补气的压缩系统的判断控制方法，其针对 前述的带有中间补气的压缩系统进行中间补气的控制调节。
优选地，通过第一压力检测装置和第一温度检测装置检测并计算出的补气过热度、通过第一温度检测装置和第二温度检测装置检测并计算出的补气阀前后温度差和通过第二压力检测装置和第三温度检测装置检测并计算出的排气过热度三者同步进行判断，来判别中间补气过热度是否带液。
优选地，其中补气过热度SH1和排气过热度SH2和补气阀前后温度差TH的计算公式分别为：SH1＝Tm1-Tmc；SH2＝Td-Tdc；TH＝Tm1-Tm2；其中Tm1、Tm2和Td分别为第一、第二和第三温度检测装置检测出的温度，Tmc为第一压力检测装置检测出的压力值Pm下对应的饱和蒸汽温度，Tdc为第二压力检测装置检测出的排气压力值Pd下对应的饱和蒸汽温度。
优选地，压缩机运行时每间隔T1分钟，检测并计算SH1、SH2及TH的值，当SH2≥a时，进一步判断SH1和TH的情况：
若SH1＞b且TH＜c时，判定压缩机补气未带液；
若SH1≤b或TH≥c时，判定压缩机补气轻微带液，但并未影响压缩机可靠性；
其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，T1为指定的时间间隔，均为设定的常数。
优选地，压缩机运行时每间隔T1分钟，检测并计算SH1、SH2及TH的值，当SH2＜a时，进一步判断SH1和TH的情况：
若SH1＞b，且TH＜c时，判定压缩机补气未带液，吸气存在带液；
若SH1≤b，且TH＜c时，判定补气轻微带液，但并未影响压缩机可靠性；
若SH1≤b，且TH≥c时，判定补气严重带液；
其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，T1为指定的时间间隔，均为设定的常数。
优选地，所述指定的补气过热度b为0，所述指定的补气阀前后差值c为1。
优选地，基于对补气带液的判断结果，进一步对补气阀进行精确控制。
优选地，若所述补气阀为二通阀，当判断补气轻微带液时，基于可靠性考虑则立即关闭所述二通阀。
优选地，若所述补气阀为电子膨胀阀，当判断补气轻微带液时，调小电子膨胀阀开度；而当判断补气严重带液时，则立即关闭所述电子膨胀阀。
本发明提供的一种带有中间补气的压缩系统、空调系统及其判断控制方法具有如下一项或多项有益效果：
1.通过本发明设计提供的一种带有中间补气的压缩系统，能够准确地判断压缩机中间补气是否带液的情况；
2.且还能够区别出补气少量带液和大量带液的状态，从而有效地避免由于中间补气带液而造成压缩机中的润滑油稀释，压缩机磨损甚至产生液击的情况的发生，延长了双级压缩机的使用寿命；
3.本发明结合电子膨胀阀的补气控制，可以精确控制补气量及补气状态，提高系统运行效率的同时保障了双级压缩机的长期可靠性；
4.该系统及方法简单可靠，且成本低。
附图说明
图1是本发明的带有中间补气的压缩系统的结构示意图；
图2是本发明的带有中间补气的压缩系统的判断控制方法的判断控制流程示意图。
图中附图标记表示为：
1—压缩机，2—中间补气管路，3—补气阀，4—第一压力检测装置，5—第一温度检测装置，6—第二温度检测装置，7—第二压力检测装置，8—第三温度检测装置，9—闪发器，11—排气管路，12—中压吸气端。
具体实施方式
如图1所示，本发明提供一种带有中间补气的压缩系统，包括压缩机1、中间补气管路2和设置于所述中间补气管路2上的补气阀3，其中按 照制冷剂流向，在中间补气管路2上位于所述补气阀3的进口端设置有第一压力检测装置4和第一温度检测装置5、位于补气阀3的出口端设置有第二温度检测装置6，所述系统还包括设置在所述压缩机1排气管路上11的第二压力检测装置7和第三温度检测装置8。
通过本发明设计提供的一种带有中间补气的压缩系统，能够通过第一、第二、第三温度检测装置及第一、第二压力检测装置检测并计算得出补气过热度、补气阀前后温度差和排气过热度，通过对该三者进行同步判断，能够有效地判断出中间补气是否存在带液的情况；并且通过该系统还能够区别出补气少量带液和大量带液的状态，从而可以有效控制双级压缩机的中间补气量，以避免压缩机产生液击，可以长期保障双级压缩机的可靠和高效运行。方法简单可靠，成本低。
优选地，所述第一温度检测装置5为第一补气感温包，所述第二温度检测装置6为第二补气感温包，所述第三温度检测装置8为排气感温包。通过将第一温度检测装置选择为第一补气感温包是一种优选的种类和选择，能够准确地检测出中间补气管路补气阀前端处(按制冷剂流向)的温度情况，为计算该处的补气过热度提供了有效的前提条件；通过将第二温度检测装置选择为第二补气感温包也是一种优选的种类和选择，能够准确地检测出中间补气管路补气阀后端处(按制冷剂流向)的温度情况，为计算补气阀前后温度差提供了有效的前提条件；通过将第三温度检测装置8选择排气感温包也是一种优选的种类和选择，能够准确地检测出压缩机排气管路11的排气温度，进而为计算该处的排气过热度提供了有效的前提条件。
优选地，所述第一压力检测装置4为中压传感器，所述第二压力检测装置7为高压传感器。通过将第一压力检测装置选择为中压传感器是一种优选的种类和选择，能够准确地检测出中间补气管路补气阀前端(按制冷剂流向)的压力情况(中压)，进而计算得出该压力状态下的饱和蒸汽温度值，为计算该处的补气过热度提供了有效的前提条件；通过将第二压力检测装置选择为高压传感器也是一种优选的种类和选择，能够准确地检测出压缩机排气管路11的压力情况(高压)，进而计算得出该压力状态下的饱和蒸汽温度值，为计算该处的排气过热度提供了有效的 前提条件。
优选地，所述补气阀3为二通阀。这是一种补气阀的优选种类和实施方式，通过二通阀能够根据中间补气是否带液而进行有效地开启或关闭的动作，从而执行控制的操作，防止压缩机液击现象的发生，提高了运行的可靠性。
优选地，所述补气阀3为电磁膨胀阀。这也是一种补气阀的优选种类和实施方式，通过电磁膨胀阀能够根据中间补气是否带液而进行有效地开启或关闭的动作，除此之外还能够根据中间补气带液轻微或是严重而执行将开度减小或是关闭的动作，执行控制的操作，防止压缩机液击现象的发生，提高了运行的可靠性。
优选地，所述中间补气管路2的一端连接到所述压缩机1的中压吸气端12。通过设置上述的连接结构能够有效地将中间补气管路中的制冷剂补入至压缩机的中压吸气端，起到补气增焓的有效作用。
优选地，所述压缩系统还包括闪发器9，且所述中间补气管路2的另一端连接到所述闪发器9。通过设置闪发器能够有效地起到将带有液态和气态的制冷剂进行闪蒸发作用，使得气态和液态制冷剂有效地分离，并且使气态制冷剂通过中间补气管路进入压缩机的中压吸气端，能够有效地起到补气增焓的作用。
优选地，所述压缩机1为双级式压缩机。这是本发明的压缩机的一种优选种类和实施方式，目的是执行双级增压，降低单个压缩机的压缩比，并且在各级之间补气增焓，提高制冷剂运行的焓值。当然也并不局限于双级式压缩机，也可以是多级式，或者两个或多个压缩机串联的结构。
本发明还提供一种空调系统，其包括前述的带有中间补气的压缩系统。通过包括带有中间补气的压缩系统的空调系统，能够通过第一、第二、第三温度检测装置及第一、第二压力检测装置检测并计算得出补气过热度、补气阀前后温度差和排气过热度，通过对该三者进行同步判断，能够有效地判断出中间补气是否存在带液的情况；并且通过该系统还能够区别出补气少量带液和大量带液的状态，从而可以有效控制双级压缩机的中间补气量，以避免压缩机产生液击，可以长期保障双级压缩机的可靠和高效运行。方法简单可靠，成本低。
如图2所示，本发明还提供一种带有中间补气的压缩系统的判断控制方法，其针对前述的带有中间补气的压缩系统进行中间补气的控制调节。通过针对带有中间补气的压缩系统的中间补气进行判断控制，能够通过第一、第二、第三温度检测装置及第一、第二压力检测装置检测并计算得出补气过热度、补气阀前后温度差和排气过热度，通过对该三者进行同步判断，能够有效地判断出中间补气是否存在带液的情况；并且通过该系统还能够区别出补气少量带液和大量带液的状态，从而可以有效控制双级压缩机的中间补气量，以避免压缩机产生液击，可以长期保障双级压缩机的可靠和高效运行。方法简单可靠，成本低。
优选地，通过第一压力检测装置和第一温度检测装置检测并计算出的补气过热度、通过第一温度检测装置和第二温度检测装置检测并计算出的补气阀前后温度差和通过第二压力检测装置和第三温度检测装置检测并计算出的排气过热度三者同步进行判断，来判别中间补气过热度是否带液。这是具体的判断方法。该方法可以准确判断补气带液情况，能够区别出补气少量带液和大量带液的状态，可以长期保障压缩机的可靠运行和高效运行。
优选地，其中补气过热度SH1和排气过热度SH2和补气阀前后温度差TH的计算公式分别为：SH1＝Tm1-Tmc；SH2＝Td-Tdc；TH＝Tm1-Tm2；其中Tm1、Tm2和Td分别为第一、第二和第三温度检测装置检测出的温度，Tmc为第一压力检测装置检测出的压力值Pm下对应的饱和蒸汽温度，Tdc为第二压力检测装置检测出的排气压力值Pd下对应的饱和蒸汽温度。这是判断方法过程中补气过热度SH1和排气过热度SH2和补气阀前后温度差TH的具体检测和计算步骤。
优选地，压缩机运行时每间隔T1分钟(T1可根据需要设定)，检测补气阀前后温度Tm1及Tm2、排气温度Td、补气压力和排气压力，计算补气过热度SH1、排气过热度SH2及补气阀前后温度差值TH，如图2所示，具体判断方法如下：
当SH2≥a时(此时说明排气过热度高)，进一步判断SH1和TH的情况：
若SH1＞b且TH＜c时，判定压缩机补气未带液；此时说明补气阀 前端的制冷剂过热度较高，且经过补气阀两端的温降较小，说明补气进入压缩机的气体未带液；
若SH1≤b或TH≥c时，判定压缩机补气轻微带液，但并未影响压缩机可靠性；此时说明补气阀前端的制冷剂过热度较低，且经过补气阀两端的温降较大，说明补气进入压缩机的气体轻微带液(若出现严重带液的情况则排气过热度即SH2一定会很低；而此处的前提条件是排气过热度高，因此该条件下通常不可能存在严重带液)。
其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，T1为指定的时间间隔，均为设定的常数。
通过以上的判断手段能够有效地判断出当排气过热度较高时压缩机中间吸气是否带液或带液量大小的情况。
优选地，当SH2＜a时，(此时说明排气过热度低)进一步判断SH1和TH的情况：
若SH1＞b，且TH＜c时，判定压缩机补气未带液，吸气存在带液；此时说明补气阀前端的制冷剂过热度较高，且经过补气阀两端的温降较小，说明补气进入压缩机的气体未带液，而又由于SH2<a，则说明压缩机吸气存在带液的情况。
若SH1≤b，且TH＜c时，判定补气轻微带液，但并未影响压缩机可靠性；此时说明补气阀前端的制冷剂过热度较低，且经过补气阀两端的温降较小，说明补气进入压缩机的气体轻微带液，但未影响压缩机运行的可靠性；
若SH1≤b，且TH≥c时，判定补气严重带液(即温降较大会存在严重带液的情况)，需立即关闭补气阀；此时说明补气阀前端的制冷剂过热度较低，且经过补气阀两端的温降较大，说明补气进入压缩机的气体严重带液。
其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，均为设定的常数，大小根据系统方案确定。
通过上述判断手段能够能够有效地判断出当排气过热度较低时压缩机中间吸气是否带液或带液量大小的情况。
优选地，所述指定的补气过热度b为0，所述指定的补气阀前后差值 c为1。这是上述指定的补气过热度b和指定的补气阀前后差值c的优选取值，这是根据大量的实验和研究过程而得出的数值。进一步c值可根据系统的差异情况而优选选择为1、1.5或2。
优选地，基于对补气带液的判断结果，进一步对补气阀进行精确控制。通过判断结果控制补气阀进而达到对压缩机中间带液进行有效控制的作用，防止液体进入压缩机中而形成液击，保证了可靠性的运行。
优选地，若所述补气阀为二通阀，当判断补气轻微带液时，基于可靠性考虑(即从可靠性的角度考虑)则立即关闭所述二通阀。这是补气阀作为二通阀的优选实施方式的具体控制手段，能够有效地防止液体进入压缩机。
优选地，若所述补气阀为电子膨胀阀，当判断补气轻微带液时，调小电子膨胀阀开度，在保护压缩机不受液击的同时可保持系统高效运行；而当判断系统状态发生突变，由补气不带液状态变为严重带液状态时，则立即关闭所述电子膨胀阀，从而保护压缩机的长期可靠运行。从而在保护压缩机不受液击的同时可保持系统高效且长期可靠的运行。
下面介绍一下本发明的优选实施例
如图1所示，本发明采用一种补气过热度、补气阀前后温度差和排气过热度三者同步判断的方法，来判别中间补气过热度是否带液。该方法可以准确判断补气带液情况，能够区别出补气少量带液和大量带液的状态，可以长期保障压缩机的可靠运行和高效运行。
如图2所示，具体方案如下：
定义压缩机第一温度检测装置5、第二温度检测装置6、和第三温度检测装置8检测到的补气温度1、补气温度2和排气温度分别为Tm1、Tm2和Td。各感温包及压力传感器的位置如图1所示。定义补气感温包处中压传感器检测的中间压力为Pm，对应的饱和蒸汽温度为Tmc，定义排气感温包处高压传感器检测的排气压力为Pd，对应的饱和蒸汽温度为Tdc。定义补气过热度和排气过热度分别为SH1和SH2，补气阀前后温度差为TH，则有：
SH1＝Tm1-Tmc；
SH2＝Td-Tdc；
TH＝Tm1-Tm2；
本方案在补气过热度的基础上，并将补气感温包和中压传感器安装在补气控制阀与闪发器之间，如图1所示，同时增加了第二温度检测装置6和排气过热度作为判断依据，可以准确判断中间补气是否带液的情况。压缩机运行时每间隔T1分钟，检测补气阀前后温度Tm1及Tm2、排气温度Td、补气压力和排气压力，计算补气过热度SH1、排气过热度SH2及补气阀前后温度差值TH，如图2所示，具体判断方法如下：
SH2≥a，SH1和TH有以下几种情况：
若SH1＞0且TH＜1时，判定补气未带液；
若SH1≤0或TH≥1时，判定补气轻微带液，但并未影响压缩机可靠性；
SH2＜a，SH1和TH有以下几种情况：
若SH1＞0，且TH＜1时，判定补气未带液，吸气存在带液；
若SH1≤0，TH＜1时，判定补气轻微带液，但并未影响压缩机可靠性；
若SH1≤0，TH≥1时，判定补气严重带液，需立即关闭补气阀；
其中a、b、c均为常数，根据系统方案确定。
基于对补气带液的判断结果，可以对补气阀进行精确控制。如补气控制阀使用二通阀，当判断补气轻微带液时，基于可靠性角度可以立即关闭补气阀；如补气控制阀使用电子膨胀阀，当判断补气轻微带液时，可调小补气电子膨胀阀开度，在保护压缩机不受液击的同时可保持系统高效运行。而当系统状态发生突变，由补气不带液状态变为严重带液状态时，需立即关闭补气阀以保护压缩机的长期可靠运行。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上所述仅为本发明的较佳实施例而已，并不用以限制本发明，凡在本发明的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本发明的保护范围之内。以上所述仅是本发明的优选实施方式，应 当指出，对于本技术领域的普通技术人员来说，在不脱离本发明技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本发明的保护范围。

Claims (18)

  1. 带有中间补气的压缩系统，包括压缩机(1)、中间补气管路(2)和设置于所述中间补气管路(2)上的补气阀(3)，其特征在于：按照制冷剂流向，在所述中间补气管路(2)上位于所述补气阀(3)的进口端设置有第一压力检测装置(4)和第一温度检测装置(5)、位于所述补气阀(3)的出口端设置有第二温度检测装置(6)；
    所述系统还包括设置在所述压缩机(1)排气管路(11)上的第二压力检测装置(7)和第三温度检测装置(8)。
  2. 根据权利要求1所述的带有中间补气的压缩系统，其特征在于：所述第一温度检测装置(5)为第一补气感温包，所述第二温度检测装置(6)为第二补气感温包，所述第三温度检测装置(8)为排气感温包。
  3. 根据权利要求1-2之一所述的带有中间补气的压缩系统，其特征在于：所述第一压力检测装置(4)为中压传感器，所述第二压力检测装置(7)为高压传感器。
  4. 根据权利要求1-3之一所述的带有中间补气的压缩系统，其特征在于：所述补气阀(3)为二通阀。
  5. 根据权利要求1-3之一所述的带有中间补气的压缩系统，其特征在于：所述补气阀(3)为电磁膨胀阀。
  6. 根据权利要求1-5之一所述的带有中间补气的压缩系统，其特征在于：所述中间补气管路(2)的一端连接到所述压缩机(1)的中压吸气端(12)。
  7. 根据权利要求6所述的带有中间补气的压缩系统，其特征在于：所述压缩系统还包括闪发器(9)，且所述中间补气管路(2)的另一端连接到所述闪发器(9)。
  8. 根据权利要求1-7之一所述的带有中间补气的压缩系统，其特征在于：所述压缩机(1)为双级式压缩机。
  9. 一种空调系统，其特征在于：包括权利要求1-8之一所述的带有中间补气的压缩系统。
  10. 一种带有中间补气的压缩系统的判断控制方法，其特征在于：针 对权利要求1-8之一所述的带有中间补气的压缩系统进行中间补气的控制调节。
  11. 根据权利要求10所述的判断控制方法，其特征在于：通过第一压力检测装置和第一温度检测装置检测并计算出的补气过热度、通过第一温度检测装置和第二温度检测装置检测并计算出的补气阀前后温度差、和通过第二压力检测装置和第三温度检测装置检测并计算出的排气过热度三者进行判断，来判别中间补气过热度是否带液。
  12. 根据权利要求11所述的判断控制方法，其特征在于：其中补气过热度SH1、排气过热度SH2、和补气阀前后温度差TH的计算公式分别为：
    SH1＝Tm1-Tmc；
    SH2＝Td-Tdc；
    TH＝Tm1-Tm2；
    其中Tm1、Tm2和Td分别为第一、第二和第三温度检测装置检测出的温度，Tmc为第一压力检测装置检测出的压力值Pm下对应的饱和蒸汽温度，Tdc为第二压力检测装置检测出的排气压力值Pd下对应的饱和蒸汽温度。
  13. 根据权利要求12所述的判断控制方法，其特征在于：
    压缩机运行时每间隔T1分钟，检测并计算SH1、SH2及TH的值，
    当SH2≥a时，进一步判断SH1和TH的情况：
    若SH1＞b且TH＜c时，判定压缩机补气未带液；
    若SH1≤b或TH≥c时，判定压缩机补气轻微带液，但并未影响压缩机可靠性；
    其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，T1为指定的时间间隔，均为设定的常数。
  14. 根据权利要求12或13所述的判断控制方法，其特征在于：压缩机运行时每间隔T1分钟，检测并计算SH1、SH2及TH的值，当SH2＜a时，进一步判断SH1和TH的情况：
    若SH1＞b，且TH＜c时，判定压缩机补气未带液，吸气存在带液；
    若SH1≤b，且TH＜c时，判定补气轻微带液，但并未影响压缩机可 靠性；
    若SH1≤b，且TH≥c时，判定补气严重带液；
    其中a为指定的排气过热度、b为指定的补气过热度、c为指定的补气阀前后差值，T1为指定的时间间隔，均为设定的常数。
  15. 根据权利要求13-14之一所述的判断控制方法，其特征在于：
    所述指定的补气过热度b为0，所述指定的补气阀前后差值c为1。
  16. 根据权利要求13-15之一所述的判断控制方法，其特征在于：基于对补气带液的判断结果，进一步对补气阀进行精确控制。
  17. 根据权利要求16所述的判断控制方法，其特征在于：若所述补气阀为二通阀，当判断补气轻微带液时，则立即关闭所述二通阀。
  18. 根据权利要求16所述的判断控制方法，其特征在于：若所述补气阀为电子膨胀阀，当判断补气轻微带液时，调小电子膨胀阀开度；而当判断补气严重带液时，则立即关闭所述电子膨胀阀。
PCT/CN2016/098676 2015-12-10 2016-09-12 带有中间补气的压缩系统、空调系统及其判断控制方法 Ceased WO2017096992A1 (zh)

Priority Applications (2)

Application Number Priority Date Filing Date Title
US16/060,695 US10330350B2 (en) 2015-12-10 2016-09-12 Air conditioning system, compression system with gas secondary injection and judgment and control method thereof
CA3007722A CA3007722C (en) 2015-12-10 2016-09-12 Air conditioning system, compression system with gas secondary injection and judgment and control method thereof

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CN201510916651.XA CN105371514B (zh) 2015-12-10 2015-12-10 带有中间补气的压缩系统、空调系统及其判断控制方法
CN201510916651.X 2015-12-10

Publications (1)

Publication Number Publication Date
WO2017096992A1 true WO2017096992A1 (zh) 2017-06-15

Family

ID=55373940

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CN2016/098676 Ceased WO2017096992A1 (zh) 2015-12-10 2016-09-12 带有中间补气的压缩系统、空调系统及其判断控制方法

Country Status (4)

Country Link
US (1) US10330350B2 (zh)
CN (1) CN105371514B (zh)
CA (1) CA3007722C (zh)
WO (1) WO2017096992A1 (zh)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105371514B (zh) * 2015-12-10 2018-05-18 珠海格力电器股份有限公司 带有中间补气的压缩系统、空调系统及其判断控制方法
CN105371548B (zh) * 2015-12-11 2017-11-21 珠海格力电器股份有限公司 双级压缩机的补气增焓控制方法、设备和装置
CN105485989B (zh) * 2015-12-14 2018-03-13 珠海格力电器股份有限公司 一种双级压缩空调系统的补气控制方法
CN109899278B (zh) * 2017-12-08 2021-09-03 丹佛斯（天津）有限公司 用于压缩机的控制器及控制方法、压缩机组件和制冷系统
CN108759211B (zh) * 2018-06-12 2020-11-17 重庆美的通用制冷设备有限公司 双级离心机组及双级离心机组的中间补气控制方法
CN108759029B (zh) * 2018-06-19 2020-11-03 安徽美芝精密制造有限公司 空调系统、空调系统的控制方法及空调器
EP3901538B1 (en) * 2020-04-24 2024-04-10 Copeland Europe GmbH Flash tank-based control of refrigerant injection into a compressor
CN111648935A (zh) * 2020-06-09 2020-09-11 上海慧得节能科技有限公司 一种同时回收不同压力乏汽的装置及其使用方法
CN113091236B (zh) * 2020-08-21 2021-12-28 广州松下空调器有限公司 一种空调器液击保护方法、装置及空调器
CN112013560B (zh) * 2020-08-26 2022-06-03 佛山市冰力鲜制冷设备制造有限公司 一种mrc二级压缩混合制冷用保温装置
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
CN112484340B (zh) * 2020-11-20 2022-03-25 珠海格力电器股份有限公司 热泵设备运行控制方法、装置及热泵设备
CN115420006B (zh) * 2022-09-05 2024-07-26 宁波奥克斯电气股份有限公司 一种空调器及其控制方法、装置和可读存储介质
CN115875792B (zh) * 2022-10-28 2024-07-19 珠海格力电器股份有限公司 用于喷气增焓压缩机空调器的控制方法、装置及空调器
CN117267975A (zh) * 2023-10-07 2023-12-22 珠海格力电器股份有限公司 补气压缩机和空调系统及其控制方法
CN119617678A (zh) * 2024-12-27 2025-03-14 深圳市英维克科技股份有限公司 制冷装置

Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN200996753Y (zh) * 2006-12-26 2007-12-26 海信集团有限公司 带经济器的中间补气压缩机制冷系统
WO2008042358A1 (en) * 2006-10-02 2008-04-10 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor
US20120167601A1 (en) * 2011-01-04 2012-07-05 Carrier Corporation Ejector Cycle
US20120192579A1 (en) * 2009-10-23 2012-08-02 Carrier Corporation Refrigerant vapor compression system operation
CN202813860U (zh) * 2012-09-26 2013-03-20 美意(浙江)空调设备有限公司 新型水冷机组
CN203274353U (zh) * 2012-06-19 2013-11-06 合肥天鹅制冷科技有限公司 水源回热型高温热泵
CN103411291A (zh) * 2013-08-30 2013-11-27 海信（山东）空调有限公司 一种膨胀阀喷射控制方法及系统
KR20140123822A (ko) * 2013-04-15 2014-10-23 엘지전자 주식회사 공기조화기 및 그 제어방법
EP2924369A1 (en) * 2014-03-20 2015-09-30 LG Electronics Inc. Air conditioner and method for controlling an air conditioner
CN105065248A (zh) * 2015-08-19 2015-11-18 珠海格力电器股份有限公司 变容压缩机及控制方法
CN105371514A (zh) * 2015-12-10 2016-03-02 珠海格力电器股份有限公司 带有中间补气的压缩系统、空调系统及其判断控制方法
CN205191969U (zh) * 2015-12-10 2016-04-27 珠海格力电器股份有限公司 带有中间补气的压缩系统及空调系统

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006125793A (ja) * 2004-11-01 2006-05-18 Hitachi Home & Life Solutions Inc 空気調和装置
JP4408413B2 (ja) * 2004-12-22 2010-02-03 日立アプライアンス株式会社 冷凍装置及びこれを用いた空気調和機
CN100366992C (zh) * 2005-11-25 2008-02-06 珠海格力电器股份有限公司 低温空调热泵系统及使用该系统降低温度调节波动的方法
US20100275624A1 (en) 2006-02-15 2010-11-04 Lg Electronics Inc. Air-Conditioning System And Controlling Method For The Same
JP2007232263A (ja) * 2006-02-28 2007-09-13 Daikin Ind Ltd 冷凍装置
KR101336720B1 (ko) * 2008-01-02 2013-12-05 엘지전자 주식회사 공기조화 시스템
JP5240332B2 (ja) * 2011-09-01 2013-07-17 ダイキン工業株式会社 冷凍装置
JP6029879B2 (ja) * 2012-07-10 2016-11-24 シャープ株式会社 ヒートポンプ式加熱装置
CN103629873B (zh) * 2012-08-23 2016-01-27 珠海格力节能环保制冷技术研究中心有限公司 双级压缩空调系统的控制方法
CN204830555U (zh) * 2015-08-03 2015-12-02 烟台顿汉布什工业有限公司 一种包含自动补气装置的双级离心机组及其控制系统

Patent Citations (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008042358A1 (en) * 2006-10-02 2008-04-10 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor
CN200996753Y (zh) * 2006-12-26 2007-12-26 海信集团有限公司 带经济器的中间补气压缩机制冷系统
US20120192579A1 (en) * 2009-10-23 2012-08-02 Carrier Corporation Refrigerant vapor compression system operation
US20120167601A1 (en) * 2011-01-04 2012-07-05 Carrier Corporation Ejector Cycle
CN203274353U (zh) * 2012-06-19 2013-11-06 合肥天鹅制冷科技有限公司 水源回热型高温热泵
CN202813860U (zh) * 2012-09-26 2013-03-20 美意(浙江)空调设备有限公司 新型水冷机组
KR20140123822A (ko) * 2013-04-15 2014-10-23 엘지전자 주식회사 공기조화기 및 그 제어방법
CN103411291A (zh) * 2013-08-30 2013-11-27 海信（山东）空调有限公司 一种膨胀阀喷射控制方法及系统
EP2924369A1 (en) * 2014-03-20 2015-09-30 LG Electronics Inc. Air conditioner and method for controlling an air conditioner
CN105065248A (zh) * 2015-08-19 2015-11-18 珠海格力电器股份有限公司 变容压缩机及控制方法
CN105371514A (zh) * 2015-12-10 2016-03-02 珠海格力电器股份有限公司 带有中间补气的压缩系统、空调系统及其判断控制方法
CN205191969U (zh) * 2015-12-10 2016-04-27 珠海格力电器股份有限公司 带有中间补气的压缩系统及空调系统

Also Published As

Publication number Publication date
CA3007722C (en) 2023-10-31
CN105371514B (zh) 2018-05-18
CA3007722A1 (en) 2017-06-15
US10330350B2 (en) 2019-06-25
US20180363954A1 (en) 2018-12-20
CN105371514A (zh) 2016-03-02

Similar Documents

Publication Publication Date Title
CN105371514B (zh) 带有中间补气的压缩系统、空调系统及其判断控制方法
CN104634033B (zh) 一种电子膨胀阀控制系统及方法
CN103398520B (zh) 空调系统及其气液分离器的液位检测方法
CN106196787B (zh) 热泵系统的控制方法及热泵系统
CN103411291B (zh) 一种膨胀阀喷射控制方法及系统
CN105485989B (zh) 一种双级压缩空调系统的补气控制方法
CN205191969U (zh) 带有中间补气的压缩系统及空调系统
US20050126190A1 (en) Loss of refrigerant charge and expansion valve malfunction detection
CN202392954U (zh) 空调器
CN104266426B (zh) 判断气液分离器中液位的方法及系统
US20130086932A1 (en) Vehicle Air-Conditioning Device, and Refrigerant Leakage Diagnosis Method for Vehicle Air-Conditioning Device
KR20110074109A (ko) 공기조화기 및 공기조화기의 제어방법
CN105065249B (zh) 压缩机性能检测装置、具有该装置的空调系统和控制方法
CN101469929B (zh) 空调机
CN110925940A (zh) 一种双级压缩补气装置、空调系统及补气控制方法
WO2021073098A1 (zh) 一种定频空调器缺冷媒保护方法
CN107289599A (zh) 一种检测空调冷媒泄露量的装置和方法
CN106765903B (zh) 一种用于空调系统的外风机的控制方法
CN105466094A (zh) 液位检测系统、具有该系统的空调系统及液位控制方法
CN110486917A (zh) 运行控制装置及方法、空调器和计算机可读存储介质
JP2014214913A (ja) 油戻し制御装置及び冷凍装置
CN105333660A (zh) 一种多联机系统的压缩机保护方法
JP2010060179A (ja) 制御装置、空気調和機及び冷凍装置
CN110440489B (zh) 一种可调节压差的化霜控制方法、装置及采暖机组
CN207831667U (zh) 一种热泵热水器机组

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 16872187

Country of ref document: EP

Kind code of ref document: A1

ENP Entry into the national phase

Ref document number: 3007722

Country of ref document: CA

NENP Non-entry into the national phase

Ref country code: DE

122 Ep: pct application non-entry in european phase

Ref document number: 16872187

Country of ref document: EP

Kind code of ref document: A1