WO2021120453A1 - 冷水机组及其控制方法 - Google Patents

冷水机组及其控制方法 Download PDF

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Publication number
WO2021120453A1
WO2021120453A1 PCT/CN2020/083749 CN2020083749W WO2021120453A1 WO 2021120453 A1 WO2021120453 A1 WO 2021120453A1 CN 2020083749 W CN2020083749 W CN 2020083749W WO 2021120453 A1 WO2021120453 A1 WO 2021120453A1
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WIPO (PCT)
Prior art keywords
compressor
gas
liquid separator
condenser
port
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PCT/CN2020/083749
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English (en)
French (fr)
Inventor
王书森
张捷
王铁伟
邓善营
Original Assignee
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 WO2021120453A1 publication Critical patent/WO2021120453A1/zh

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    • 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
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/30—Expansion means; Dispositions thereof
    • 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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors

Definitions

  • the invention relates to the technical field of air conditioners, in particular to a chiller and a control method thereof.
  • the chiller generally includes a compressor, a condenser, an electronic expansion valve, an evaporator, and a gas-liquid separator; the exhaust port of the compressor is connected to the refrigerant inlet of the condenser; the discharge port of the condenser is connected to the refrigerant of the evaporator through the electronic expansion valve The inlet is connected, and the refrigerant outlet of the evaporator is connected with the refrigerant inlet of the gas-liquid separator; the suction port of the compressor is connected with the exhaust port of the gas-liquid separator.
  • the evaporator is arranged in the room and cooperates with the fan to form a cooling fan, thus realizing the refrigeration cycle.
  • the gas-liquid separator is provided with a chamber, one end of the gas-liquid separator is provided with an exhaust port, and the gas-liquid separator is also provided with a refrigerant inlet; when the liquid-containing gaseous refrigerant enters the chamber of the gas-liquid separator through the refrigerant inlet; when the liquid-containing gaseous refrigerant enters the chamber of the gas-liquid separator through the refrigerant inlet After the middle, due to the different density of gas and liquid, when the liquid flows with the gas, the liquid will be subjected to the action of gravity to produce a downward velocity, while the gas still flows in the original direction, that is to say, the liquid and the gas are in the same direction. There is a tendency to separate in the gravitational field, and the downward liquid adheres to the wall and collects and sinks at the bottom of the gas-liquid separator.
  • this field needs a new chiller and its control method to solve the above problems.
  • the invention provides a chiller.
  • a chiller unit provided by the present invention includes a compressor, a condenser, a first throttling device, an evaporator, a gas-liquid separator and an ejector; the exhaust port of the compressor and the refrigerant inlet of the condenser Connection; the first discharge port of the condenser communicates with the refrigerant inlet of the evaporator through the first throttling device, and the refrigerant outlet of the evaporator communicates with the refrigerant inlet of the gas-liquid separator;
  • the exhaust port of the gas-liquid separator is in communication with the suction port of the compressor; the first end of the ejector is in communication with the first exhaust port of the condenser, and the second end of the ejector is in communication with the first exhaust port of the condenser.
  • the end is in communication with the discharge port of the gas-liquid separator, and the third end of the ejector is in communication with the suction port of the compressor.
  • the second exhaust port of the condenser is in communication with the supplementary air port of the gas-liquid separator, and the second exhaust port of the condenser is connected to A second throttling device is also arranged between the supplementary ports of the gas-liquid separator.
  • the exhaust port of the compressor is also in communication with the air supplement port of the gas-liquid separator, and the exhaust port of the compressor is connected to the gas-liquid separator.
  • a third throttling device is also arranged between the supplementary air ports of the liquid separator.
  • the second discharge port of the condenser is also in communication with the refrigerant inlet of the gas-liquid separator; and the second discharge port of the condenser A fourth throttling device is also connected with the gas-liquid separator.
  • the compressor is a magnetic levitation compressor, and the second discharge port of the condenser is also connected with the cooling inlet of the magnetic levitation compressor; and
  • the magnetic levitation compressor is equipped with a temperature sensor and a second electronic control valve.
  • a pressure regulating pipeline is connected between the cooling outlet of the compressor and the suction port of the compressor, and the pressure regulating pipeline is provided with A pressure regulating valve.
  • the economizer includes a condensing part and an evaporating part; the first drain of the condenser passes through the condensing part and the The first throttle device is in communication; the first discharge port of the condenser is also in communication with the refrigerant inlet of the evaporator through the fifth throttling device, and the refrigerant outlet of the evaporator is connected to the refrigerant through a third electronic control valve.
  • the air supply port of the compressor is connected.
  • the gas-liquid separator includes a body, a chamber is formed in the body, an exhaust port is opened at one end of the body, and the body is also A refrigerant inlet is provided; and the exhaust port and the refrigerant inlet are respectively communicated with the chamber; a baffle passage is formed in the chamber, and the baffle passage is along the refrigerant inlet to the exhaust port Bend and extend in the direction.
  • the gas-liquid separator further includes a plurality of baffle plates, and the plurality of baffle plates are respectively connected to the inner wall of the main body to form the baffle. Flow channel.
  • the baffle channel is spiral or S-shaped.
  • the present invention also provides a control method of the above-mentioned chiller, which includes: when the fan is running, obtaining the actual value of the suction pressure of the compressor and the setting value of the suction pressure; comparing the suction pressure The size of the actual pressure value and the set value of the suction pressure; the required capacity value of the compressor is calculated according to the comparison result; the actual capacity value of the compressor is adjusted to the required capacity value.
  • the water chiller provided by the present invention connects the first exhaust port of the condenser and the discharge port of the gas-liquid separator to the suction port of the compressor through an ejector, respectively.
  • the ejector can be connected to the first exhaust port of the condenser, and the compressor will eject the high-temperature and high-pressure gaseous refrigerant in the condenser through the ejector.
  • negative pressure is formed at the second end of the ejector connected to the gas-liquid separator, and the liquid refrigerant in the gas-liquid separator is sucked into the ejector at a small flow rate.
  • the high-temperature and high-pressure gaseous refrigerant flowing out of the condenser and the condenser are combined and vaporized, and then returned to the suction port of the compressor together, so that the liquid level of the refrigerant in the gas-liquid separator can be reduced and no refrigerant is wasted.
  • the second exhaust port of the condenser of the chiller is communicated with the supplementary air port of the gas-liquid separator through a second throttling device, so that when the chiller is turned on, the number of When the energy demand of the load is less than the minimum energy output limit of the compressor, the high-temperature and high-pressure gaseous refrigerant discharged by the compressor can directly enter the gas-liquid separator through the second exhaust port of the condenser and the gas-liquid separator's supplementary gas port to participate in the refrigerant. cycle. In this way, it is ensured that the compressor will not stop when the load of the air cooler is small.
  • Figure 1 is a schematic diagram of the structure of the chiller of this embodiment
  • Figure 2 is a schematic diagram of the structure of the gas-liquid separator of this embodiment
  • Fig. 3 is a schematic flow chart of the control method of the chiller in this embodiment.
  • the terms “installed”, “connected”, and “connected” should be understood in a broad sense. For example, they can be fixed or fixed. It is a detachable connection or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components.
  • installed e.g., they can be fixed or fixed. It is a detachable connection or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium, and it can be the internal communication between two components.
  • the specific meaning of the above-mentioned terms in the present invention can be understood according to specific circumstances.
  • a gas-liquid separator 280 provided in this embodiment includes a body; a chamber is formed in the body, and an exhaust port is opened at one end of the body (that is, the exhaust of the gas-liquid separator shown in Figure 2).
  • the air port 286), the body is also provided with a refrigerant inlet (ie, the refrigerant inlet 285 of the gas-liquid separator shown in Figure 2); and the exhaust port and the refrigerant inlet are respectively communicated with the chamber;
  • a baffle channel 284 is formed in the chamber , The baffle passage 284 bends and extends in the direction from the refrigerant inlet to the exhaust port.
  • the gas-liquid separator 280 shown in FIG. 2 is provided with an exhaust port on the upper part, and a refrigerant inlet is provided near the lower part.
  • a baffle channel 284 that is bent and extended in the direction from the refrigerant inlet to the exhaust port is arranged in the inner cavity of the gas-liquid separator 280, thereby increasing the flow of the gaseous refrigerant from the refrigerant.
  • the path from the inlet to the exhaust port forms a loss of kinetic energy of the refrigerant and effectively reduces the flow rate of the refrigerant, so that a small amount of liquid refrigerant in the gaseous refrigerant has enough time and distance to settle.
  • the resistance and collision between the refrigerant and the baffle channel 284 can further separate the gaseous refrigerant from the liquid refrigerant, thereby greatly improving the separation efficiency of the gas-liquid separator 280.
  • the gas-liquid separator 280 further includes a plurality of baffle plates 283, and the plurality of baffle plates 283 are respectively connected to the inner wall of the main body and enclosed in a plenum Road 284.
  • a plurality of baffle plates 283 are alternately arranged in the inner cavity of the gas-liquid separator 280 along the horizontal direction, and a channel for the refrigerant to pass is formed between the baffle plate 283 and the inner wall of the chamber to form a gas-liquid separator 280.
  • the baffle passage 284 in the liquid separator 280 realizes the purpose of changing the flow direction of the refrigerant multiple times and increasing the length of the refrigerant flow path.
  • the baffle channel 284 is spiral or S-shaped.
  • the shape of the baffle passage 284 may be a spiral shape around the axis of the body and extending from the refrigerant inlet end to the exhaust end; or, the shape of the baffle passage 284 may also be along the opposite level as shown in FIG. 2 The direction keeps turning back and forming an S shape extending from the refrigerant inlet end to the exhaust end.
  • the refrigerant inlet is located between the baffle channel 284 and the preset liquid level position of the chamber.
  • the refrigerant inlet is preferably arranged between the baffle channel 284 and the preset liquid level position of the chamber, that is, below the baffle plate 283 corresponding to the bottommost layer of the baffle channel 284 and the preset liquid level of the chamber Between locations.
  • the gaseous refrigerant is just above the preset liquid level when entering the gas-liquid separator 280 from the refrigerant inlet to prevent the gaseous refrigerant from entering below the liquid level and carrying liquid again; and the refrigerant inlet is located below the baffle channel 284, which can facilitate the gaseous refrigerant to enter the fold.
  • the flow channel 284 flows along the baffle channel 284.
  • the preset liquid level position of the gas-liquid separator refers to the highest liquid level allowed by the gas-liquid separator in normal use.
  • a liquid discharge port (ie, the liquid discharge port 287 of the gas-liquid separator shown in FIG. 2) is further provided on the end of the body far from the exhaust port. ).
  • the liquid discharge port may be arranged on the side of the body of the gas-liquid separator 280, so that the pipeline extends to the bottom end of the cavity, and the liquid discharge port is provided on the end of the gas-liquid separator 280 away from the exhaust port.
  • a small amount of liquid refrigerant in the gas-liquid separator 280 can be combined with the high temperature and high pressure gas refrigerant discharged from the compressor 110 or the high temperature and high pressure gas refrigerant discharged from the condenser 210 and vaporized. Enter the compressor 110 to achieve the purpose of reducing the liquid refrigerant in the gas-liquid separator 280 without wasting the refrigerant.
  • the gas-liquid separator 280 further includes a liquid level gauge, which is arranged on the outside of the body near the end of the liquid discharge port.
  • the liquid level in the gas-liquid separator 280 can be detected by installing a level gauge on the end of the body close to the drain port, and the liquid level position that needs to be drained of the liquid refrigerant can be preset. When the liquid level is reached, the valve of the liquid discharge port is opened to allow the liquid refrigerant to flow out.
  • the level gauge provided on the gas-liquid separator 280 is referred to as the second level gauge 281 here.
  • the gas-liquid separator 280 is equipped with a second level gauge 281, as long as the liquid level of the refrigerant is slightly larger than the preset liquid level position where the liquid refrigerant needs to be drained, the liquid refrigerant is discharged; When the surface drops to the normal range, the discharge is stopped. In this way, the amount of liquid refrigerant discharged from the gas-liquid separator 280 each time is small. If part of the high-temperature and high-pressure gas refrigerant in the exhaust port of the compressor 110 or the intake port of the condenser 210 is mixed with the liquid refrigerant, the The liquid refrigerant can be vaporized, and returns to the compressor 110 along the suction line of the compressor 110.
  • an electric control valve is connected to the liquid discharge port.
  • the actual liquid level position information measured by the liquid level gauge can be received through the control system of the chiller or air conditioner, and the on-off of the electronic control valve can be controlled according to the comparison result of the actual liquid level position and the preset liquid level position, so as to The discharge of the gas-liquid separator 280 is controlled.
  • the body is also provided with an air supplement port (that is, the air supplement port 288 of the gas-liquid separator shown in FIG. 2), and the air supplement port is located in the baffle channel Between 284 and the preset liquid level of the chamber.
  • an air supplement port that is, the air supplement port 288 of the gas-liquid separator shown in FIG. 2
  • the chiller as shown in FIG. 1 includes a plurality of cooling fans on the inside, and each cooling fan includes an evaporator 270 and a fan 273.
  • each cooling fan includes an evaporator 270 and a fan 273.
  • the compressor 110 can reduce the energy output within a certain range as the load decreases. However, when the energy of the compressor 110 decreases to a certain value, it may cause the compressor 110 to stop, so the part of the high temperature and high pressure entering the condenser 210 can be reduced.
  • the gaseous refrigerant flows into the gas-liquid separator 280, and then returns to the compressor 110 with the suction line of the compressor 110 to ensure that the load of the chiller is small and the chiller can still maintain normal energy output.
  • the gas-liquid separator 280 further includes a safety valve, and the safety valve is provided at one end of the body close to the exhaust port (as shown in FIG. 2 The second safety valve 282).
  • blockage of the refrigerant route or other unexpected conditions may cause the pressure in the gas-liquid separator 280 to be too high.
  • the second safety valve 282 By setting the second safety valve 282 on the gas-liquid separator 280, when the pressure in the gas-liquid separator 280 reaches a certain level When the value is reached, the second safety valve 282 is automatically opened to relieve the pressure, so as to ensure that the gas-liquid separator 280 is not damaged.
  • the second safety valve 282 can be arranged close to the exhaust port of the gas-liquid separator 280, so that when the pressure is relieved, the gaseous refrigerant is released, which is more environmentally friendly and economical than releasing the liquid refrigerant.
  • this embodiment also provides a chiller, including a compressor 110, a condenser 210, a first throttling device 260, an evaporator 270, a gas-liquid separator 280, and an ejector 802;
  • the discharge port of the compressor 110 is connected with the refrigerant inlet of the condenser 210; the first liquid discharge port of the condenser 210 is in communication with the refrigerant inlet of the evaporator 270 through the first throttling device 260, and the refrigerant outlet of the evaporator 270 is connected to the gas-liquid
  • the refrigerant inlet of the separator 280 is connected; the exhaust port of the gas-liquid separator 280 is connected with the suction port of the compressor 110; the first end of the ejector 802 is connected with the first exhaust port of the condenser 210, the ejector
  • the second end of the 802 is in communication with the discharge port of the gas-liquid separator
  • the first exhaust port of the condenser 210 and the discharge port 287 of the gas-liquid separator are respectively connected to the suction port of the compressor 110 through an ejector 802.
  • the ejector 802 can be connected to the first exhaust port of the condenser 210, and the compressor 110 can reduce the high temperature and high pressure in the condenser 210 The gaseous refrigerant is sucked into the suction port of the compressor 110 through the ejector 802 at a higher flow rate.
  • a negative pressure is formed at the second end of the ejector 802 connected to the gas-liquid separator 280, and the gas in the gas-liquid separator 280
  • the liquid refrigerant is sucked into the ejector 802 and the high temperature and high pressure gaseous refrigerant flowing out of the condenser 210 at a small flow rate, merges and vaporizes, and then returns to the suction port of the compressor 110 together, so that the liquid level of the refrigerant in the gas-liquid separator 280 can be reduced. And to ensure that no refrigerant is wasted.
  • a first electronic control valve 801 can be provided between the first end of the ejector 802 and the first exhaust port of the condenser 210, so that when the liquid level of the gas-liquid separator 280 is controlled, the An electronic control valve 801 realizes the conduction and cut-off between the ejector 802 and the first exhaust port of the condenser 210 and the control of the flow rate.
  • the discharge port 287 of the gas-liquid separator can also be provided with a corresponding electronic control valve to realize the opening, closing and flow control of the discharge port 287 of the gas-liquid separator;
  • the second level gauge 281 monitors the liquid level of the refrigerant in the gas-liquid separator 280 and feeds it back to the control system of the chiller.
  • the control system of the chiller controls the first electric control valve 801 and the gas-liquid separator 280 on the discharge port.
  • the electronic control valve is used to control the discharge process of the gas-liquid separator 280.
  • the condenser 210 in this embodiment can be selected as a shell and tube condenser 210.
  • a one-way valve 120 can also be provided between the exhaust port of the compressor 110 and the intake port of the condenser 210. The one-way valve 120 only allows the refrigerant to flow from the compressor 110 to the condenser 210, avoiding the reverse flow of the refrigerant. Ensure the reliability and safety of the chiller system operation.
  • the second exhaust port of the condenser 210 is in communication with the supplementary gas port 288 of the gas-liquid separator, and the second exhaust port of the condenser 210 is connected to the gas-liquid separator.
  • a second throttling device 501 is also provided between the supplementary air ports 288 of the separator.
  • the high-temperature and high-pressure gaseous refrigerant discharged from the compressor 110 may pass through the second exhaust port of the condenser 210,
  • the gas supplement port of the gas-liquid separator 280 directly enters the gas-liquid separator 280 to participate in the refrigerant circulation. In this way, it is ensured that the compressor 110 will not stop when the load of the air cooler is small.
  • the discharge pressure of the compressor 110 can be monitored by the first pressure sensor 112 provided on the discharge port of the compressor 110, and the third pressure sensor 303 provided on the suction port of the compressor 110 can be used to monitor the suction of the compressor 110.
  • the gas pressure is used to determine whether it is necessary to connect the second exhaust port of the condenser 210 with the supplementary gas port 288 of the gas-liquid separator.
  • the exhaust port of the compressor 110 is also connected with the air supplement port of the gas-liquid separator 280, and the exhaust port of the compressor 110 is connected to the gas-liquid separator 280.
  • a third throttle device 601 is also provided between the supplementary air ports.
  • the exhaust port of the compressor 110 can be connected to the supplemental port of the gas-liquid separator 280, and the high-temperature and high-pressure gaseous refrigerant passes through the third throttle device 601 After the pressure is reduced, it directly enters the gas-liquid separator 280 to participate in the refrigerant cycle, thereby reducing the system pressure of the chiller and assisting the shutdown of the compressor 110.
  • the discharge pressure of the compressor 110 can be monitored by the first pressure sensor 112 provided on the discharge port of the compressor 110, and the third pressure sensor 303 provided on the suction port of the compressor 110 can be used to monitor the suction of the compressor 110.
  • the gas pressure is used to determine whether it is necessary to connect the discharge port of the compressor 110 with the supplementary gas port of the gas-liquid separator 280.
  • the second discharge port of the condenser 210 is also connected with the refrigerant inlet of the gas-liquid separator 280; and the second discharge port of the condenser 210 is connected to the gas-liquid separator 280.
  • a fourth throttling device 702 is also connected between the liquid separators 280.
  • the second discharge port of the condenser 210 can be connected to the refrigerant inlet of the gas-liquid separator 280, so that the liquid refrigerant in the condenser 210 can pass through the first After the four-throttle device 702 enters the gas-liquid separator 280 to vaporize, the temperature inside the gas-liquid separator 280 is reduced.
  • the third temperature sensor 302 is provided on the suction port of the compressor 110 to detect the exhaust temperature of the gas-liquid separator to determine whether the gas-liquid separator needs to be cooled.
  • the compressor 110 is a magnetic levitation compressor 110, and the second discharge port of the condenser 210 is also connected with the cooling inlet of the magnetic levitation compressor 110; and the magnetic levitation compressor 110 is equipped with a temperature sensor and a second electronic control valve.
  • the second discharge port of the condenser 210 can be connected to the cooling inlet of the magnetic levitation compressor 110 through the second electronic control valve , The liquid refrigerant in the condenser 210 enters the compressor 110 to vaporize, and the temperature inside the compressor 110 is reduced.
  • the compressors of one-to-multiple direct expansion units are mostly rotor or scroll compressors.
  • the compressor capacity is small and the refrigeration system contains the lubricating oil required by the compressor.
  • the unit control requires complex calculations based on indoor temperature, etc., resulting in The system is complex.
  • a pressure regulating pipeline is connected between the motor or electronic component cooling outlet of the compressor 110 and the suction port of the compressor 110, and the pressure regulating pipeline is provided There is a pressure regulating valve 901 to prevent condensation of internal motors or electronic components.
  • the discharge temperature and pressure of the compressor 110 can be monitored by setting the first temperature sensor 111 and the first pressure sensor 112 on the discharge port of the compressor 110, and the third temperature sensor 302 and the first pressure sensor are provided on the suction port of the compressor 110.
  • Three pressure sensors 303 are used to monitor the suction temperature and pressure of the compressor 110.
  • the water chiller unit further includes an economizer 240, which includes a condensing part and an evaporating part; the first liquid discharge port of the condenser 210 is connected to the first liquid outlet through the condensing part.
  • the throttling device 260 is connected; the first discharge port of the condenser 210 is also connected to the refrigerant inlet of the evaporator through the fifth throttling device 401, and the refrigerant outlet of the evaporator is connected to the air supplement port of the compressor 110 through the third electronic control valve 404 Connected.
  • the liquid refrigerant discharged from the first discharge port of the condenser 210 passes through the pressure reduction effect of the fifth throttling device 401 and then enters the evaporation part of the economizer 240 to evaporate and absorb heat.
  • the refrigerant in the condensing part of the economizer 240 Condensation releases heat.
  • the supercooling degree of the refrigerant entering the evaporator 270 is increased, so as to increase the evaporation efficiency of the refrigerant in the evaporator 270 and improve water cooling The cooling capacity of the unit.
  • the refrigerant in the evaporating part of the economizer 240 evaporates and absorbs heat and becomes a gaseous refrigerant to enter the compressor 110 to supplement air and increase enthalpy, which has the effect of increasing the cooling capacity and energy efficiency of the unit.
  • a first temperature sensor 111 and a first pressure sensor 112 are provided on the discharge port of the compressor 110 to monitor the discharge temperature and pressure of the compressor 110, and a third temperature sensor 302 and a third pressure are provided on the suction port of the compressor 110
  • the sensor 303 monitors the suction temperature and pressure of the compressor 110.
  • the indoor air cooler generally includes multiple sets, and each set of air coolers is equipped with an independent evaporator 270, a fan 273, and a first throttling device 260.
  • compressors used in one-to-multiple direct expansion units are rotor compressors or scroll compressors.
  • the capacity of the rotor compressors or scroll compressors is small, and the lubricating oil used by the compressors will enter the refrigerant pipeline. In, affect the working performance of the chiller.
  • the existing chillers need to perform complex calculations based on the indoor temperature during the energy control process of the compressor, resulting in complex system control.
  • this embodiment also provides a control method for the above-mentioned water chiller, including:
  • the actual value of the suction pressure of the compressor may be obtained through the third pressure sensor 303 provided at the suction port of the compressor.
  • the evaporator's evaporation temperature needs to be determined according to the set value of the air outlet temperature of the air cooler.
  • the evaporation temperature of the evaporator needs to be lower than the set value of the air outlet temperature of the air cooler.
  • the evaporation pressure can be determined by the evaporation temperature; generally, in order to overcome the resistance loss when the compressor suctions, the evaporation pressure of the evaporator needs to be high Regarding the suction pressure of the compressor, the evaporating pressure is generally 0.1-0.2kgf/cm 2 higher than the suction pressure, so because the outlet air temperature of the air cooler is determined, the set value of the suction pressure of the compressor can be determined .
  • the actual capacity value of the compressor is adjusted to be equal to the required capacity value of the compressor.
  • the required capacity value of the compressor the actual capacity value of the compressor + K* (the set value of the suction pressure of the compressor-the actual value of the suction pressure of the compressor), where K is the compressor's Energy adjustment factor.
  • the actual capacity value of the compressor is adjusted to be equal to the required capacity value of the compressor.
  • the required capacity value of the compressor the actual capacity value of the compressor + K* (the set value of the suction pressure of the compressor-the actual value of the suction pressure of the compressor), where K is the compressor's Energy adjustment factor.
  • this embodiment realizes the energy adjustment of the compressor only by the suction pressure of the compressor, so that the actual suction pressure of the compressor matches the energy demand of the compressor.
  • the energy adjustment of the compressor of this embodiment The process has the advantage of simplicity.
  • the compressor can also be adjusted according to its suction temperature.
  • the preset suction temperature of the compressor can be 10-15°C higher than the evaporation temperature of the evaporator.
  • the suction temperature of the compressor is adjusted to reach the preset temperature. Setting the suction temperature can also achieve the purpose of energy regulation on the compressor.
  • the direct expansion chiller of this embodiment can be divided into an indoor air cooler and a magnetic levitation host (that is, the outdoor part of the chiller opposite to the indoor air cooler).
  • the magnetic levitation main is equipped with a starter cabinet and a control cabinet to control various types of the chiller. Valves and compressors are controlled.
  • the control method of the chiller of this embodiment further includes: judging whether the chiller is turned on, and controlling the compressor according to the startup condition of the chiller. Specifically, when the air cooler is turned on, the compressor is started and the compressor is adjusted for energy; when the air cooler is all turned off, the compressor is also shut down.
  • maglev main unit When controlling the maglev main unit, it is only necessary to obtain whether the indoor air cooler is turned on, and to control the energy adjustment of the compressor according to the suction pressure of the compressor, instead of obtaining the specific number of the air cooler, which can simplify the maglev main unit
  • the direct control process of part (outdoor part) and chiller (indoor part) As long as the air cooler is turned on, the compressor is turned on, and when all air coolers are shut down, the compressor stops again.
  • each air cooler in the indoor air cooler section is equipped with an independent controller.
  • the controller can adjust the first according to the superheat of the indoor air cooler (that is, the difference between the temperature at the outlet end of the evaporator and the saturation temperature corresponding to the pressure at the outlet end).
  • the throttling device 260 realizes the control of starting, stopping and adjusting the first throttling device 260.
  • the cooling fan in this embodiment When the cooling fan in this embodiment is controlled, when the actual indoor temperature is greater than or equal to the sum of the indoor set temperature and the start temperature difference of the cooling fan, it indicates that there is a cooling demand in the room, and the corresponding cooling fan (ie, evaporator 270 and Fan 273, the first throttle device 260), and adjust the first throttle device 260; when the air outlet temperature of the cooler is less than or equal to the difference between the indoor set temperature and the shutdown temperature, it means that the indoor temperature has been adjusted, then Turn off the corresponding air cooler.
  • the corresponding cooling fan ie, evaporator 270 and Fan 273, the first throttle device 260
  • a second temperature sensor 271 and a second pressure sensor 272 may also be provided on the refrigerant outlet of the evaporator 270, and the control system controls the first section according to the refrigerant outlet temperature of the evaporator 270.
  • the flow device 260 adjusts. For example, when the first throttling device 260 is an electronic expansion valve, when the superheat of the refrigerant outlet of the evaporator 270 is large, the opening of the electronic expansion valve is increased; when the superheat of the refrigerant outlet of the evaporator 270 is small, The opening degree of the electronic expansion valve is reduced to ensure the evaporation effect of the evaporator 270.
  • the degree of superheat is the difference between the actual temperature of the refrigerant outlet of the evaporator 270 and the saturation temperature corresponding to the actual pressure.
  • a fourth electronically controlled valve 250 may be provided between the condenser 210 and the first throttling device 260.
  • the first throttling device 260 may be an electronic expansion valve or a capillary tube.
  • the four electric control valve 250 may be an electric ball valve. Therefore, the fourth electronic control valve 250 controls the conduction of the refrigerant in the indoor air cooler when the compressor 110 is turned on, and it is turned off when the compressor 110 is turned off.
  • the fifth electronic control valve 301 can also be used to control the conduction and cut-off of the refrigerant between the suction port of the compressor 110 and the discharge port of the gas-liquid separator 280.
  • the fifth electronic control valve 301 may be a butterfly valve.
  • the opening and closing of the first refrigerant outlet of the condenser 210 can also be controlled by the ball valve 220 or other electronically controlled valves.
  • a first safety valve 211 may be provided on the condenser 210.
  • the first safety valve 211 is automatically opened to relieve the pressure. To ensure that the condenser 210 is not damaged.
  • a first filter drier 230 may be provided on the first refrigerant outlet of the condenser 210 to filter impurities in the refrigerant, and then the refrigerant is passed through the first dry filter. After the device 230 enters the first throttling device 260 or the economizer 240 and the fifth throttling device 401 to ensure the cooling efficiency of the chiller.
  • a second filter drier 701 can also be provided on the second refrigerant outlet of the condenser 210, so that the refrigerant enters the compressor 110 or the gas-liquid separator 280 after being filtered by the second filter drier 701.
  • the first liquid level gauge 213 provided on the condenser 210 is used to monitor the liquid level in the condenser 210, and the fifth temperature sensor 212 on the condenser 210 detects the condenser.
  • the control system of the water-cooled unit can control the external air-cooled or water-cooled devices connected to the condenser, such as the cooling tower and its pipeline, according to the liquid level and temperature in the condenser 210.
  • a fourth temperature sensor 402 and a fourth pressure sensor 403 may be connected to the pipeline between the economizer 240 and the air supply port of the compressor 110, and the economizer 240 The temperature and pressure of the refrigerant outlet of the evaporator section adjust the fifth throttling device 401.

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Abstract

空调技术领域，具体涉及一种冷水机组。解决现有冷水机组中气液分离器(280)中冷媒的液面过高会造成压缩机(110)吸气带液发生损坏或降低冷水机组的制冷性能的问题。为此目的，通过将冷凝器(210)的第一排气口、气液分离器(280)的排液口分别通过引射器(802)连接在压缩机(110)的吸气口上。当气液分离器(280)中的冷媒液面超过设定位置时，可以使压缩机(110)将冷凝器(210)中的高温高压气态冷媒通过引射器(802)以较高的流速吸至压缩机(110)的吸气口，同时在引射器(802)连接气液分离器(280)的第二端形成负压，将气液分离器(280)中的液态冷媒以微小的流量吸入引射器(802)中与冷凝器(210)流出的高温高压气态冷媒汇合并汽化，然后一同返回压缩机(110)的吸气口，如此可以降低气液分离器(280)中的冷媒液面并保证不浪费冷媒。

Description

冷水机组及其控制方法 技术领域
本发明涉及空调技术领域，具体涉及一种冷水机组及其控制方法。
背景技术
冷水机组一般包括压缩机、冷凝器、电子膨胀阀、蒸发器和气液分离器；压缩机的排气口与冷凝器的冷媒进口连接；冷凝器的排液口通过电子膨胀阀与蒸发器的冷媒进口连通，蒸发器的冷媒出口与气液分离器的冷媒进口连通；压缩机的吸气口与气液分离器的排气口连通。且蒸发器设置于室内并与风机配合形成冷风机，如此实现制冷循环。
气液分离器内设置有腔室，气液分离器的一端开设有排气口，气液分离器上还设置有冷媒进口；当含液的气态冷媒由冷媒进口进入气液分离器的腔室中后，由于气体与液体的密度不同，液体在与气体一起流动时，液体会受到重力的作用，产生一个向下的速度，而气体仍然朝着原来的方向流动，也就是说液体与气体在重力场中有分离的倾向，向下的液体附着在壁面上汇集并沉在气液分离器底部。
但是，气液分离器中冷媒的液面过高会造成压缩机吸气带液发生损坏或者降低冷水机组的制冷性能。
相应地，本领域需要一种新的冷水机组及其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，即为了解决现有的冷水机组中气液分离器中冷媒的液面过高会造成压缩机吸气带液发生损坏或者降低冷水机组的制冷性能的问题，本发明提供了一种冷水机组。
本发明提供的一种冷水机组，包括压缩机、冷凝器、第一节流装置、蒸发器、气液分离器和引射器；所述压缩机的排气口与所述冷凝器的冷媒进口连接；所述冷凝器的第一排液口通过所述第一节流装置 与所述蒸发器的冷媒进口连通，所述蒸发器的冷媒出口与所述气液分离器的冷媒进口连通；所述气液分离器的排气口与所述压缩机的吸气口连通；所述引射器的第一端与所述冷凝器的第一排气口连通，所述引射器的第二端与所述气液分离器的排液口连通，且所述引射器的第三端与所述压缩机的吸气口连通。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述冷凝器的第二排气口与所述气液分离器的补气口连通，且所述冷凝器的第二排气口与所述气液分离器的补气口之间还设置有第二节流装置。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述压缩机的排气口还与所述气液分离器的补气口连通，且所述压缩机的排气口与所述气液分离器的补气口之间还设置有第三节流装置。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述冷凝器的第二排液口还与所述气液分离器的冷媒进口连通；且所述冷凝器的第二排液口与所述气液分离器之间还连接有第四节流装置。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述压缩机为磁悬浮压缩机，所述冷凝器的第二排液口还与所述磁悬浮压缩机的冷却进口连通；且所述磁悬浮压缩机配置有温度传感器和第二电控阀。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述压缩机的冷却出口与所述压缩机的吸气口之间连接有压力调节管路，且所述压力调节管路上设置有压力调节阀。
作为本发明提供的上述冷水机组的一种优选的技术方案，还包括经济器，所述经济器包括冷凝部和蒸发部；所述冷凝器的第一排液口通过所述冷凝部与所述第一节流装置连通；所述冷凝器的第一排液口还通过第五节流装置与所述蒸发部的冷媒进口连通，所述蒸发部的冷媒出口通过第三电控阀与所述压缩机的补气口连通。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述气液分离器包括本体，所述本体内形成有腔室，所述本体的一端开设有排气口，所述本体上还设置有冷媒进口；且所述排气口和所述冷媒进口分别与所述腔室连通；所述腔室内形成有折流通道，所述折流通道沿所述冷媒进口至所述排气口的方向弯折延伸。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述气液分离器还包括多个导流板，多个所述导流板分别与所述本体内壁连接并围成所述折流通道。
作为本发明提供的上述冷水机组的一种优选的技术方案，所述折流通道为螺旋状或者S形。
此外，本发明还提供了一种上述冷水机组的控制方法，包括：当所述风机运行时，获取所述压缩机的吸气压力实际值和和吸气压力设定值；比较所述吸气压力实际值和吸气压力设定值的大小；根据比较的结果，计算所述压缩机的需求能力值；将所述压缩机的实际能力值调节至所述需求能力值。
本发明提供的一种冷水机组，通过将冷凝器的第一排气口、气液分离器的排液口分别通过引射器连接在压缩机的吸气口上。当气液分离器中的冷媒液面超过设定位置时，可以将引射器与冷凝器的第一排气口之间的导通，压缩机将冷凝器中的高温高压气态冷媒通过引射器以较高的流速吸至压缩机的吸气口，同时在引射器连接气液分离器的第二端形成负压，将气液分离器中的液态冷媒以微小的流量吸入引射器中与冷凝器流出的高温高压气态冷媒汇合并汽化，然后一同返回压缩机的吸气口，如此可以降低气液分离器中的冷媒液面并保证不浪费冷媒。
此外，本发明提供的一种冷水机组，冷水机组的冷凝器的第二排气口与气液分离器的补气口之间通过第二节流装置连通，使得当冷风机开启数量较少而导致负载的能量需求小于压缩机的最低能量输出限制时，压缩机排出的高温高压的气态冷媒可以通过冷凝器的第二排气口、气液分离器的补气口直接进入气液分离器中参与冷媒循环。如此，保证了冷风机负载较小时压缩机不会停机。
附图说明
下面参照附图并结合直膨式冷水机组来描述本发明的冷水机组。附图中：
图1为本实施例的冷水机组的结构示意图；
图2为本实施例的气液分离器的结构示意图；
图3为本实施例的冷水机组的控制方法的流程示意图。
附图标记列表
110-压缩机；120-单向阀；111-第一温度传感器；112-第一压力传感器；210-冷凝器；211-第一安全阀；212-第五温度传感器；213-第一液位计；220-球阀；230-第一干燥过滤器；240-经济器；250-第四电控阀；260-第一节流装置；270-蒸发器；271-第二温度传感器；272-第二压力传感器；273-风机；280-气液分离器；281-第二液位计；282-第二安全阀；283-导流板；284-折流通道；285-气液分离器的冷媒进口；286-气液分离器的排气口；287-气液分离器的排液口；288-气液分离器的补气口；301-第五电控阀；302-第三温度传感器；303-第三压力传感器；401-第五节流装置；402-第四温度传感器；403-第四压力传感器；404-第三电控阀；501-第二节流装置；601-第三节流装置；701-第二干燥过滤器；702-第四节流装置；801-第一电控阀；802-引射器；901-压力调节阀。
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，虽然本实施方式是结合冷水机组对气液分离器进行介绍的，但是这并非旨在于限制本发明的保护范围，在不偏离本发明原理的条件下，本领域技术人员可以将本发明应用于其他应用场景。例如，壁挂式空调、多联机空调、立柜式空调等空调设备中。
需要说明的是，在本发明的描述中，术语“中心”、“上”、“下”、“左”、“右”、“竖直”、“水平”、“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”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
此外，还需要说明的是，在本发明的描述中，除非另有明确的规定和限定，术语“安装”、“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体地连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连，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。
如图2所示，本实施例提供的一种气液分离器280，包括本体；本体内形成有腔室，本体的一端开设有排气口(即图2所示的气液分离器的排气口286)，本体上还设置有冷媒进口(即图2所示的气液分离器的冷媒进口285)；且排气口和冷媒进口分别与腔室连通；腔室内形成有折流通道284，折流通道284沿冷媒进口至排气口的方向弯折延伸。
示例性地，如图2所示的气液分离器280，其上部设置有排气口，靠近下部的位置设置有冷媒进口。
本实施例提供的一种气液分离器280，通过在气液分离器280的内腔中设置沿冷媒进口至排气口的方向弯折延伸的折流通道284，增大了气态冷媒由冷媒进口流至排气口的路程，以此形成对冷媒动能的损耗，有效降低冷媒的流速，使得气态冷媒中带有的少量的液态冷媒有足够的时间和路程进行沉降。此外，冷媒与折流通道284之间的阻力作用和碰撞作用可以进一步地将气态冷媒与液态冷媒进行分离，从而极大的提高了气液分离器280的分离效率。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，气液分离器280还包括多个导流板283，多个导流板283分别与本体内壁连接并围成折流通道284。
示例性地，多个导流板283在气液分离器280的内腔中沿水平方方向间隔交错布置，且导流板283与腔室内壁之间形成供冷媒通过的通道，即可形成气液分离器280中的折流通道284，并实现多次改变冷媒的流向和增加冷媒的流路的长度的目的。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，折流通道284为螺旋状或者S形。
示例性地，折流通道284的形状可以为绕本体的轴线且由冷媒进口端延伸至排气端的螺旋状；或者，折流通道284的形状还可以为图2所示的沿着相反的水平方向不断折返，且形成由冷媒进口端延伸至排气端的S形。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，冷媒进口位于折流通道284与腔室的预设液面位置之间。
示例性地，冷媒进口优选的设置在折流通道284与腔室的预设液面位置之间，即折流通道284的最底层对应的导流板283的下方与腔室的预设液面位置之间。
使得气态冷媒由冷媒进口进入气液分离器280中时刚好位于预设液面位置以上，避免气态冷媒进入液面以下再次带液；而冷媒进口位于折流通道284以下，可以便于气态冷媒进入折流通道284并沿折流通道284流动。其中，气液分离器的预设液面位置指的是气液分离器在正常使用时所允许的液面的最高位置。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，本体上远离排气口的一端还设置有排液口(即图2所示的气液分离器的排液口287)。
示例性地，排液口可以设置在气液分离器280本体的侧面，让管路伸入至腔体最底端，通过在气液分离器280上远离排气口的一端设置排液口，当液态冷媒的液位超过设定值时，可以将气液分离器280中的少量的液态冷媒与压缩机110排出的高温高压的气态冷媒或者冷凝器210排出的高温高压气态冷媒汇合并汽化后进入压缩机110，以实现既可以减少气液分离器280中的液态冷媒又能不浪费冷媒的目的。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，还包括液位计，液位计设置在本体外部靠近排液口的一端。
示例性地，可以通过在本体外部靠近排液口的一端设置液位计来检测气液分离器280中的液位，可以预先设定需要对液态冷媒进行排流的液面位置，当液态冷媒达到该液位时，即开启排液口的阀门，使液态冷媒流出。为了方便与下文中冷凝器210上设置的第一液位计213相区分，此处将气液分离器280上设置的液位计称为为第二液位计281。
由于气液分离器280设置了第二液位计281，所以只要冷媒的液面稍微大于预先设定需要对液态冷媒进行排流的液面位置，即进行液态冷媒的排放；当液态冷媒的液面下降到正常范围时，即停止排液。如此，气液分离器280每次排出的液态冷媒的量会很少，如果将压缩机110的排气口或者冷凝器210的进气口中的部分高温高压的气态冷媒与该液态冷媒混合，该液态冷媒即可汽化，随着压缩机110的吸气管路返回压缩机110。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，排液口上连接有电控阀。
示例性地，可以通过冷水机组或者空调的控制系统接收液位计测量的实际液面位置信息，并根据实际液面位置与预设液面位置的比较结果控制该电控阀的通断，以实现对气液分离器280的排液的控制。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，本体上还设置有补气口(即图2所示的气液分离器的补气口288)，补气口位于折流通道284与腔室的预设液面之间。
示例性地，如图1所示的冷水机组中的是内侧包括多个冷风机，每个冷风机均包括蒸发器270和风机273。冷水机组在使用时会遇到冷风机开启的数量较少导致水冷机组的负载较小的情况。压缩机110可以随着负载的减少在一定范围内降低能量输出，但是，压缩机110的能量降低到一定值后时有可能导致压缩机110停机，所以可以将进入冷凝器210中的部分高温高压的气态冷媒再通入气液分离器280中，然后随着压缩机110的吸气管路返回压缩机110中，以保证冷风机的负载小时，冷水机组仍然能保持正常的能量输出。
作为本实施例提供的上述气液分离器280的一种优选的实施方式，气液分离器280还包括安全阀，本体上靠近排气口的一端设置有该安全阀(如图2所示的第二安全阀282)。
示例性地，冷媒路线堵塞或者其他意外情况会导致气液分离器280中的压力过高，通过在气液分离器280上设置第二安全阀282，当气液分离器280中的压力达到一定值时，第二安全阀282自动开启达到泄压的作用，以保证气液分离器280不发生损坏。进一步地，可以将第二安全阀282靠近气液分离器280的排气口设置，这样在泄压时释放的是气态冷媒，其比释放液态冷媒更环保和经济。
此外，如图1所示，本实施例还提供了一种冷水机组，包括压缩机110、冷凝器210、第一节流装置260、蒸发器270、气液分离器280和引射器802；压缩机110的排气口与冷凝器210的冷媒进口连接；冷凝器210的第一排液口通过第一节流装置260与蒸发器270的冷媒进口连通，蒸发器270的冷媒出口与气液分离器280的冷媒进口连通；气液分离器280的排气口与压缩机110的吸气口连通；引射器802的第一端与冷凝器210的第 一排气口连通，引射器802的第二端与气液分离器280的排液口连通，且引射器802的第三端与压缩机110的吸气口连通。
示例性地，在本实施例中，冷凝器210的第一排气口、气液分离器的排液口287分别通过引射器802连接在压缩机110的吸气口上。当气液分离器280中的冷媒液面超过设定位置时，可以将引射器802与冷凝器210的第一排气口之间的导通，压缩机110将冷凝器210中的高温高压气态冷媒通过引射器802以较高的流速吸至压缩机110的吸气口，同时在引射器802连接气液分离器280的第二端形成负压，将气液分离器280中的液态冷媒以微小的流量吸入引射器802中与冷凝器210流出的高温高压气态冷媒汇合并汽化，然后一同返回压缩机110的吸气口，如此可以降低气液分离器280中的冷媒液面并保证不浪费冷媒。
可以理解的是，引射器802的第一端与冷凝器210的第一排气口之间可以设置第一电控阀801，以在对气液分离器280液位进行控制时，通过第一电控阀801实现引射器802与冷凝器210的第一排气口之间的导通和截止以及流量大小的控制。
气液分离器的排液口287上也可以设置相应的电控阀，以实现对气液分离器的排液口287的开启、关闭和流量的控制；可以通过气液分离器280上设置的第二液位计281来监测气液分离器280中冷媒的液面并反馈给冷水机组的控制系统，冷水机组的控制系统通过控制第一电控阀801和气液分离器280的排液口上设置的电控阀来对气液分离器280的排液过程进行控制。
本实施例中的冷凝器210可以选择为壳管式冷凝器210。压缩机110的排气口与冷凝器210的进气口之间还可以设置单向阀120，该单向阀120仅允许冷媒由压缩机110流向冷凝器210，避免了冷媒的逆向流动，以保证冷水机组系统运行的可靠性和安全性。
作为本实施例提供的上述冷水机组的一种优选的实施方式，冷凝器210的第二排气口与气液分离器的补气口288连通，且冷凝器210的第二排气口与气液分离器的补气口288之间还设置有第二节流装置501。
示例性地，当冷风机开启数量较少，导致负载的能量需求小于压缩机110的最低能量输出限制时，压缩机110排出的高温高压的气态冷媒可以通过冷凝器210的第二排气口、气液分离器280的补气口直接进 入气液分离器280中参与冷媒循环。如此，保证了冷风机负载较小时压缩机110不会停机。
可以通过在压缩机110的排气口上设置的第一压力传感器112来监测压缩机110的排气压力，以及在压缩机110的吸气口上设置的第三压力传感器303来监测压缩机110的吸气压力，以确定是否需要将冷凝器210的第二排气口与气液分离器的补气口288连通导通。
作为本实施例提供的上述冷水机组的一种优选的实施方式，压缩机110的排气口还与气液分离器280的补气口连通，且压缩机110的排气口与气液分离器280的补气口之间还设置有第三节流装置601。
示例性地，当压缩机110以高压状态工作而需要停机时，可以将压缩机110的排气口与气液分离器280的补气口导通，高温高压的气态冷媒通过第三节流装置601降低压力后直接进入气液分离器280中参与冷媒循环，以此来降低冷水机组的系统压力并协助压缩机110停机。
可以通过在压缩机110的排气口上设置的第一压力传感器112来监测压缩机110的排气压力，以及在压缩机110的吸气口上设置的第三压力传感器303来监测压缩机110的吸气压力，以确定是否需要将压缩机110的排气口与气液分离器280的补气口导通。
作为本实施例提供的上述冷水机组的一种优选的实施方式，冷凝器210的第二排液口还与气液分离器280的冷媒进口连通；且冷凝器210的第二排液口与气液分离器280之间还连接有第四节流装置702。
示例性地，当气液分离器280中的温度较高时，可以将冷凝器210的第二排液口与气液分离器280的冷媒进口导通，让冷凝器210中的液态冷媒经过第四节流装置702后进入气液分离器280中汽化，降低气液分离器280内部的温度。可以理解的是，通过在压缩机110的吸气口上设置第三温度传感器302来检测气液分离器的排气温度，以确定是否需要对气液分离器进行降温。
作为本实施例提供的上述冷水机组的一种优选的实施方式，压缩机110为磁悬浮压缩机110，冷凝器210的第二排液口还与磁悬浮压缩机110的冷却进口连通；且磁悬浮压缩机110配置有温度传感器和第二电控阀。
示例性地，当压缩机110中的温度传感器检测到压缩机110 的温度较高时，可以通过第二电控阀将冷凝器210的第二排液口与磁悬浮压缩机110的冷却进口导通，让冷凝器210中的液态冷媒进入压缩机110中汽化，降低压缩机110内部的温度。
目前一拖多直膨机组压缩机多为转子或是涡旋压缩机，压机能力较小且制冷系统含有压机所需的润滑油，机组控制需要根据室内温度等进行复杂的运算，从而造成系统复杂。
作为本实施例提供的上述冷水机组的一种优选的实施方式，压缩机110的电机或电子元件冷却出口与压缩机110的吸气口之间连接有压力调节管路，且压力调节管路上设置有压力调节阀901，防止内部电机或电子元件凝露。
可以通过在压缩机110的排气口上设置第一温度传感器111和第一压力传感器112来监测压缩机110的排气温度和压力，在压缩机110的吸气口上设置第三温度传感器302和第三压力传感器303来监测压缩机110的吸气温度和压力。
作为本实施例提供的上述冷水机组的一种优选的实施方式，冷水机组还包括经济器240，经济器240包括冷凝部和蒸发部；冷凝器210的第一排液口通过冷凝部与第一节流装置260连通；冷凝器210的第一排液口还通过第五节流装置401与蒸发部的冷媒进口连通，蒸发部的冷媒出口通过第三电控阀404与压缩机110的补气口连通。
示例性地，冷凝器210的第一排液口排出的液态冷媒通过第五节流装置401的降压作用后进入经济器240的蒸发部进行蒸发吸热，同时经济器240的冷凝部的冷媒冷凝放热，经济器240的蒸发部的冷媒与冷凝部的冷媒热交换后，提高了进入蒸发器270的冷媒的过冷度，以增加冷媒的在蒸发器270中的蒸发效率，并提高水冷机组的制冷能力。
此外，经济器240的蒸发部的冷媒蒸发吸热后变成气态冷媒进入压缩机110中补气增焓，有提高机组制冷量及能效的作用。
还可以在经济器240与压缩机110的补气口之间的管路上连接第四温度传感器402和第四压力传感器403，并根据经济器240的蒸发部的冷媒出口的温度和压力对第五节流装置401进行调节。
在压缩机110的排气口上设置第一温度传感器111和第一压力传感器112来监测压缩机110的排气温度和压力，在压缩机110的吸气口 上设置第三温度传感器302和第三压力传感器303来监测压缩机110的吸气温度和压力。本实施例提供的冷水机组在使用时，室内冷风机一般包括多组，每组冷风机均配备有独立的蒸发器270及风机273、第一节流装置260。
目前一拖多直膨机组中使用的压缩机多为转子压缩机或是涡旋压缩机，转子压缩机或是涡旋压缩机的能力较小，且压缩机使用的润滑油会进入冷媒管路中，影响冷水机组的工作性能。此外，现有的冷水机组在压缩机的能量控制过程中需要根据室内温度等进行复杂的运算，从而造成系统控制复杂。
此外，为了解决现有的冷水机组的控制过程复杂的问题，如图3所示，本实施例还提供了一种上述冷水机组的控制方法，包括：
S100、当风机运行时，获取压缩机的吸气压力实际值和和吸气压力设定值；
S200、比较吸气压力实际值和吸气压力设定值的大小；
S300、根据比较的结果，计算压缩机的需求能力值；
S400、将压缩机的实际能力值调节至需求能力值。
示例性地，可以通过压缩机的吸气口设置的第三压力传感器303获取压缩机的吸气压力的实际值。而吸气压力的设定值在确定时，需要先根据冷风机的出风温度的设定值确定蒸发器的蒸发温度，蒸发器的蒸发温度需要比冷风机的出风温度的设定值低8～10度，由于蒸发温度为冷媒在蒸发压力下沸腾时的饱和温度，通过蒸发温度即可确定蒸发压力；一般地，为了克服压缩机吸气时的阻力损失，蒸发器的蒸发压力需要高于压缩机的吸气压力，一般蒸发压力较吸气压力高0.1-0.2kgf/cm 2，如此由于冷风机的出风温度是确定的，从而可以确定出压缩机的吸气压力的设定值。
当压缩机的吸气压力的实际值小于压缩机的吸气压力设定值时，则将压缩机的实际能力值调节至等于压缩机的需求能力值。在调节过程中，压缩机的需求能力值＝压缩机的实际能力值+K*(压缩机的吸气压力设定值-压缩机的吸气压力的实际值)，其中，K为压缩机的能量调节系数。
当压缩机的吸气压力的实际值大于压缩机的吸气压力设定值时，则将压缩机的实际能力值调节至等于压缩机的需求能力值。在调节过程中，压缩机的需求能力值＝压缩机的实际能力值+K*(压缩机的吸气压力设定值-压缩机的吸气压力的实际值)，其中，K为压缩机的能量调节系数。
如此，本实施例仅通过压缩机的吸气压力即实现了对压缩机的能量调节，以使压缩机的实际吸气压力和压缩机的能量需求相匹配，本实施例的压缩机的能量调节过程具有简单的优点。
上述说明了根据压缩机的吸气压力对压缩机进行能量调节的方法，但是，本领域的技术人员可以理解的是，在不偏离本发明对压缩机进行能量调节的原理的前提下，本领域技术人员可以对该方法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。例如，还可以根据压缩机的吸气温度对压缩机进行能量调节。先根据蒸发器的蒸发温度确定压缩机的预设吸气温度，压缩机的预设吸气温度可以比蒸发器的蒸发温度高10～15℃，通过将压缩机的吸气温度调节至达到预设吸气温度，同样也可以实现对压缩机进行能量调节的目的。
本实施例的直膨式冷水机组可以分为室内冷风机与磁悬浮主机(即冷水机组中与室内冷风机相对的室外部分)，磁悬浮主装有启动柜及控制柜来对冷水机组中的各种阀门及压缩机进行控制。
本施例的冷水机组的控制方法还包括：判断冷风机是否开启，并根据冷风机的开机情况对压缩机进行控制。具体地，当冷风机开启时即启动压缩机，并对压缩机进行能量调节；当冷风机全部关闭时，则压缩机也停机。
对磁悬浮主机部分进行控制时，只需要获取室内冷风机是否开启，并根据压缩机的吸气压力对压缩机进行能量调节的控制，而不需要获取冷风机具体开启的数量，从而可以简化磁悬浮主机部分(室外部分)与冷水机组(室内部分)的直接控制过程。只要有冷风机开启时，压缩机就开启，当冷风机全部停机时，压缩机再停机。
此外，室内冷风机部分每台冷风机都装有独立的控制器，控制器可以根据室内冷风机的过热度(即蒸发器出口端温度与出口端压力 对应的饱和温度的差值)调节第一节流装置260，从实现对第一节流装置260进行启停和调节的控制。在本实施例中的冷风机进行控制时，当室内实际温度大于等于室内设定温度与冷风机的启动温差之和时，说明室内有降温需求，则开启相应的冷风机(即蒸发器270及风机273、第一节流装置260)，并对第一节流装置260进行调节；当冷风机的出风温度小于等于室内设定温度与停机温差之差时，说明室内温度已经调节完成，则关闭相应的冷风机。
本领域技术人员可以理解的是，本发明的保护范围并不限于上述实施例所公开的气液分离器和冷水机组的内容，在不偏离本发明对气液分离器和冷水机组的工作原理的前提下，本领域技术人员可以对上述设置方式进行多种调整和组合，以便本发明能够适用于更多具体的应用场景。
例如，在另一种可替换的实施方式中，还可以在蒸发器270的冷媒出口上设置第二温度传感器271和第二压力传感器272，控制系统根据蒸发器270的冷媒出口温度对第一节流装置260进行调节。如第一节流装置260为电子膨胀阀时，当蒸发器270的冷媒出口的过热度较大时，则增大电子膨胀阀的开度；当蒸发器270的冷媒出口的过热度较小时，则减小电子膨胀阀的开度，以保证蒸发器270的蒸发效果。其中过热度为蒸发器270的冷媒出口的实际温度与实际压力对应的饱和温度的差值。
再如，在一种可替换的实施方式中，可在冷凝器210与第一节流装置260之间设置第四电控阀250，第一节流装置260可以为电子膨胀阀或者毛细管，第四电控阀250可以为电动球阀。从而通过第四电控阀250控制室内冷风机中冷媒在压缩机110开机时的导通，以及在压缩机110关机时截止。
再如，在另一种可替换的实施方式中，还可以通过第五电控阀301控制压缩机110的吸气口与气液分离器280的排气口之间冷媒的导通与截止。其中，第五电控阀301可以为蝶阀。还可以通过球阀220或者其他的电控阀来控制冷凝器210的第一冷媒出口的打开和关闭。
再如，在另一种可替换的实施方式中，还可以在冷凝器210上设置第一安全阀211，当冷凝器210中的压力达到预警值时，第一安全阀211自动开启达到泄压的作用，以保证冷凝器210不发生损坏。
再如，在另一种可替换的实施方式中，还可以在冷凝器210的第一冷媒出口上设置第一干燥过滤器230，以过滤冷媒中的杂质，然后再将冷媒经过第一干燥过滤器230后进入第一节流装置260或者经济器240与第五节流装置401，以保证冷水机组的制冷效率。同理，还可以在冷凝器210的第二冷媒出口上设置第二干燥过滤器701，使得冷媒经过第二干燥过滤器701的过滤后再进入压缩机110或气液分离器280中。
再如，在另一种可替换的实施方式中，冷凝器210上设置的第一液位计213用来监测冷凝器210中的液位，冷凝器210上的第五温度传感器212检测冷凝器210中的温度，水冷机组的控制系统可以根据冷凝器210中的液位和温度来控制与冷凝器连接的外部的风冷或水冷装置，如冷却塔及其管路。
再如，在另一种可替换的实施方式中，还可以在经济器240与压缩机110的补气口之间的管路上连接第四温度传感器402和第四压力传感器403，并根据经济器240的蒸发部的冷媒出口的温度和压力对第五节流装置401进行调节。
当然，上述可以替换的实施方式之间、以及可以替换的实施方式和优选的实施方式之间还可以交叉配合使用，从而组合出新的实施方式以适用于更加具体的应用场景。
此外，本领域的技术人员能够理解，尽管在此所述的一些实施例包括其它实施例中所包括的某些特征而不是其它特征，但是不同实施例的特征的组合意味着处于本发明的保护范围之内并且形成不同的实施例。例如，在本发明的权利要求书中，所要求保护的实施例的任意之一都可以以任意的组合方式来使用。
至此，已经结合附图所示的优选实施方式描述了本发明的技术方案，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. 一种冷水机组，其特征在于：
    包括压缩机、冷凝器、第一节流装置、蒸发器、气液分离器和引射器；所述蒸发器配置有风机；
    所述压缩机的排气口与所述冷凝器的冷媒进口连接；所述冷凝器的第一排液口通过所述第一节流装置与所述蒸发器的冷媒进口连通，所述蒸发器的冷媒出口与所述气液分离器的冷媒进口连通；所述气液分离器的排气口与所述压缩机的吸气口连通；
    所述引射器的第一端与所述冷凝器的第一排气口连通，所述引射器的第二端与所述气液分离器的排液口连通，且所述引射器的第三端与所述压缩机的吸气口连通。
  2. 根据权利要求1所述的冷水机组，其特征在于：
    所述冷凝器的第二排气口与所述气液分离器的补气口连通，且所述冷凝器的第二排气口与所述气液分离器的补气口之间还设置有第二节流装置。
  3. 根据权利要求1所述的冷水机组，其特征在于：
    所述压缩机的排气口还与所述气液分离器的补气口连通，且所述压缩机的排气口与所述气液分离器的补气口之间还设置有第三节流装置。
  4. 根据权利要求1所述的冷水机组，其特征在于：
    所述冷凝器的第二排液口还与所述气液分离器的冷媒进口连通；
    且所述冷凝器的第二排液口与所述气液分离器之间还连接有第四节流装置。
  5. 根据权利要求1所述的冷水机组，其特征在于：
    所述压缩机为磁悬浮压缩机，所述冷凝器的第二排液口还与所述磁悬浮压缩机的冷却进口连通；且所述磁悬浮压缩机配置有温度传感器和第二电控阀。
  6. 根据权利要求1所述的冷水机组，其特征在于：
    所述压缩机的冷却出口与所述压缩机的吸气口之间连接有压力调节管路，且所述压力调节管路上设置有压力调节阀。
  7. 根据权利要求1所述的冷水机组，其特征在于：
    还包括经济器，所述经济器包括冷凝部和蒸发部；
    所述冷凝器的第一排液口通过所述冷凝部与所述第一节流装置连通；
    所述冷凝器的第一排液口还通过第五节流装置与所述蒸发部的冷媒进口连通，所述蒸发部的冷媒出口通过第三电控阀与所述压缩机的补气口连通。
  8. 根据权利要求1所述的冷水机组，其特征在于：
    所述气液分离器包括本体，所述本体内形成有腔室，所述本体的一端开设有排气口，所述本体上还设置有冷媒进口；且所述排气口和所述冷媒进口分别与所述腔室连通；
    所述腔室内形成有折流通道，所述折流通道沿所述冷媒进口至所述排气口的方向弯折延伸。
  9. 根据权利要求8所述的冷水机组，其特征在于：
    所述气液分离器还包括多个导流板，多个所述导流板分别与所述本体内壁连接并围成所述折流通道；
    并且/或者，所述折流通道为螺旋状或者S形。
  10. 一种权利要求1～9中任一项所述的冷水机组的控制方法，其特征在于，包括：
    当所述风机运行时，获取所述压缩机的吸气压力实际值和和吸气压力设定值；比较所述吸气压力实际值和吸气压力设定值的大小；
    根据比较的结果，计算所述压缩机的需求能力值；
    将所述压缩机的实际能力值调节至所述需求能力值。
PCT/CN2020/083749 2019-12-20 2020-04-08 冷水机组及其控制方法 WO2021120453A1 (zh)

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