WO2020259131A1 - Unité de refroidissement d'eau et procédé de commande - Google Patents

Unité de refroidissement d'eau et procédé de commande Download PDF

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Publication number
WO2020259131A1
WO2020259131A1 PCT/CN2020/091093 CN2020091093W WO2020259131A1 WO 2020259131 A1 WO2020259131 A1 WO 2020259131A1 CN 2020091093 W CN2020091093 W CN 2020091093W WO 2020259131 A1 WO2020259131 A1 WO 2020259131A1
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WO
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Prior art keywords
pressure
exhaust
gas
outlet
port
Prior art date
Application number
PCT/CN2020/091093
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English (en)
Chinese (zh)
Inventor
王书森
王铁伟
邓善营
殷志文
张捷
孟庆超
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 WO2020259131A1 publication Critical patent/WO2020259131A1/fr

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
    • 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
    • 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
    • F25B39/00—Evaporators; Condensers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems

Definitions

  • the invention belongs to a heat pump system, and specifically relates to a chiller.
  • Two-stage compression refrigeration cycles are widely used in some refrigeration compressors.
  • the existing heat pump system adopts the method of intermediate gas supplementation. Specifically, the liquid from the condenser is separated from the gas and liquid, and the separated gas is used as the intermediate gas supplement to directly enter the high pressure chamber of the compressor; the separated liquid enters the evaporation
  • the evaporator evaporates and absorbs cold energy, and the low pressure vapor from the evaporator enters the low pressure cavity of the compressor. Because the gaseous refrigerant from the outlet of the evaporator is usually in a slightly liquid state, the compressor will increase power consumption when compressed by liquid, especially for centrifugal refrigeration compressors. Liquid compression will easily penetrate the blades of the impeller and directly damage the compressor. The key components of the compressor reduce the operating reliability of the compressor and shorten its service life.
  • the current heat pump system has a low degree of subcooling of the refrigerant liquid at the outlet of the gas-liquid separation device, which causes part of the liquid in front of the throttling device to vaporize, and there is a technical problem that the unit cooling capacity drops and the expansion valve does not work properly.
  • the present invention proposes a chiller to solve the above problems.
  • the present invention adopts the following technical solutions to achieve it.
  • a chiller includes: a compressor, which includes a first-stage compression chamber and a second-stage compression chamber that are communicated, and the compressor has an air suction port and a low-pressure supplementary port that are connected to the first-stage compression chamber, respectively, and The intermediate pressure air supplement port and the exhaust port communicated with the secondary compression chamber.
  • the condenser has a condensation inlet and a condensation outlet, and the condensation inlet is connected with the exhaust port.
  • the heat exchanger has a heat absorption channel and a heat release channel.
  • the evaporator has an evaporation inlet and an evaporation outlet, and the evaporation outlet is connected with the suction port.
  • a gas-liquid separation device which has a liquid inlet, a first outlet, and a second outlet, the liquid inlet is connected to the condensation outlet, the first outlet is connected to the medium pressure supplementary gas port, and the second outlet Connected to the inlet of the heat release channel, one of the outlets of the heat release channel is connected to the evaporation inlet, and the other is connected to the inlet of the heat absorption channel through a throttling element, and the outlet of the heat absorption channel is connected to the heat absorption channel. Connect to the low-pressure air supply port.
  • a first-level throttling device is provided between the condenser and the gas-liquid separation device.
  • a secondary throttling device is arranged between the gas-liquid separation device and the evaporator.
  • a first liquid level detection device is provided in the condenser.
  • the gas-liquid separation device is provided with a second liquid level detection device.
  • the suction port is provided with a suction temperature sensor and a suction pressure sensor.
  • the exhaust port is provided with an exhaust temperature sensor and an exhaust pressure sensor.
  • the low pressure supplemental gas port is provided with a first supplemental gas temperature sensor and a first supplementary gas pressure sensor.
  • the high-pressure air supplement port is provided with a second air supplement temperature sensor and a second air supplement pressure sensor.
  • a flow regulating device is provided between the first outlet and the intermediate pressure supplementary air port.
  • the compressor is a two-stage centrifugal compressor
  • a guide vane is provided at the entrance of the one-stage compression chamber
  • a drive motor is connected to the guide vane.
  • the present invention also proposes a control method of a water chiller, including the aforementioned water chiller, and the control method of the control method of the water chiller is as follows.
  • the liquid level of the condenser is detected, and the opening degree of the primary throttling device is adjusted according to the liquid level of the condenser.
  • the liquid level of the gas-liquid separation device is detected, and the opening degree of the secondary throttling device is adjusted according to the liquid level of the gas-liquid separation device.
  • the compressor protection step includes any combination of the suction pressure protection step, the discharge pressure and discharge temperature protection step, and the discharge superheat protection step.
  • the method for adjusting the opening degree of the secondary throttling device according to the liquid level of the gas-liquid separation device is as follows. When the liquid level of the gas-liquid separation device is lower than the first set value, the opening degree of the secondary throttling device is reduced, and when the liquid level of the gas-liquid separation device is higher than the second set value, the The opening degree of the secondary throttling device, wherein the first setting value is greater than 0, and the second setting value is greater than the first setting value.
  • a flow adjustment device is provided between the first outlet and the intermediate pressure supplementary port, and the control method further includes the step of calculating the inhalation superheat of the intermediate pressure supplemental port, When the popularity is less than 0, perform the following operations.
  • the suction pressure protection step includes: detecting suction pressure, deloading the unit when the suction pressure is lower than the low-pressure warning set value, and shutting down the unit when the suction pressure is lower than the low-pressure protection setting value.
  • Exhaust pressure and exhaust temperature protection steps include: detecting exhaust pressure and exhaust temperature, when the exhaust pressure and exhaust temperature are higher than the high-pressure warning set value, the unit deloads, when the exhaust pressure is higher than the high-pressure protection value The unit shuts down.
  • Exhaust superheat protection steps include: calculating the exhaust superheat, when the exhaust superheat is lower than the exhaust pre-warning setting value, the unit deloads, when the exhaust gas superheat is lower than the exhaust protection setting value, the unit shuts down.
  • Exhaust superheat is the saturation temperature difference between exhaust temperature and exhaust pressure.
  • the chiller of the present invention adds a heat exchanger behind the gas-liquid separation device, so that the refrigerant from the gas-liquid separation device enters the heat release channel of the heat exchanger ,
  • One of the refrigerant flowing out of the heat release channel enters the heat absorption channel of the heat exchanger, absorbs the refrigerant in the heat release channel, vaporizes and evaporates, and becomes a low-pressure gaseous refrigerant through the low-pressure air supply port to supplement the first-stage compression chamber, and the other way enters the evaporation In the evaporator, it absorbs heat and evaporates into a gaseous state and enters the compressor.
  • the refrigerant passes through the heat release channel to release heat before entering the evaporator, it can increase the supercooling degree of the refrigerant before entering the evaporator and improve the unit mass refrigerant cooling Reduce the amount of flash gas before the refrigerant enters the evaporator, adjust the opening of the throttling element according to the pressure and temperature of the refrigerant, and then adjust the amount of refrigerant entering the evaporator to improve the compressor suction liquid.
  • FIG. 1 is a schematic diagram of an embodiment of the chiller proposed by the present invention.
  • Figure 2 is a p-h diagram of the chiller in Figure 1.
  • FIG. 3 is a flow chart of an embodiment of the chiller control method proposed by the present invention.
  • this embodiment proposes a chiller, as shown in Figure 1, including a compressor 11, a condenser 12, a heat exchanger 13, a gas-liquid separation device 14, and an evaporator 15.
  • the compressor 11 includes a stage The compression cavity and the secondary compression cavity, the primary compression cavity and the secondary compression cavity are connected, and the primary compression cavity is also connected with an air suction port 112 and a low pressure air supplement port 115, and the secondary compression cavity is also connected with an intermediate pressure air supplement port 114
  • the exhaust port 113, the condenser 12 has a condensation inlet 121 and a condensation outlet 122, the condensation inlet 121 is connected to the exhaust port 113 of the secondary compression chamber;
  • the evaporator 15 has an evaporation inlet 151 and an evaporation outlet 152, and the heat exchanger 13 has The heat absorption channel 131 and the heat release channel 132;
  • the gas-liquid separation device 14 has a liquid inlet 141, a first outlet 142 and a second outlet 143, the
  • the heat absorption channel 131 The outlet is connected to the low-pressure supplementary air port 115, and the evaporation outlet 152 is connected to the suction port 112.
  • the working principle of this chiller is: the low-pressure steam produced in the evaporator 15 is first sucked into the first-stage compression chamber by the compressor 11.
  • the first-stage compression chamber compresses the steam to an intermediate pressure, and then enters the second-stage compression chamber to be further compressed to the condensing pressure p k, It then enters the condenser 12 and is condensed into liquid.
  • the refrigerant from the condenser 12 enters the gas-liquid separation device 14 for gas-liquid separation.
  • the separated medium-pressure gas is used as intermediate supplementary gas, enters the intermediate-pressure supplementary port, and merges with the exhaust from the first-stage compression chamber to enter the second-stage compression chamber; the liquid refrigerant separated by the gas-liquid separation device 14 enters the heat exchanger to release heat Channel, one of the refrigerant flowing out of the heat release channel enters the heat absorption channel of the heat exchanger, absorbs the refrigerant in the heat release channel, vaporizes and evaporates, becomes a low-pressure gaseous refrigerant, and supplies air to the first-stage compression chamber through the low-pressure air inlet.
  • the pressure and temperature of part of the refrigerant can then adjust the superheat of the refrigerant entering the compressor and improve the compressor suction liquid.
  • the degree of subcooling increases the cooling capacity per unit mass of refrigerant, reduces the flash gas before the refrigerant enters the evaporator, adjusts the opening of the throttling element according to the pressure and temperature of the refrigerant, and then adjusts the amount of refrigerant entering the evaporator to improve the compressor Inhalation with liquid. Compared with the traditional anti-compressor liquid compression solution, this solution has a simple system pipeline layout structure, which is beneficial to reduce costs.
  • the liquid separated by the gas-liquid separation device 14 enters the heat release channel 132 of the heat exchanger 13 to release heat to further reduce its temperature, it is helpful to increase the subcooling degree of the evaporator after entering the evaporator and increase the cooling capacity per unit mass of refrigerant.
  • a small part of the refrigerant from the heat release channel 132 needs to enter the heat absorption channel 131 to absorb the heat of the refrigerant in the heat release channel 132. This part of the refrigerant needs to be further throttled and reduced for vaporization before entering the heat absorption channel 131.
  • a throttle element 18 at the front end of the heat absorption channel 131, it is used to throttle and reduce the pressure of the refrigerant entering the heat absorption channel 131, and the low-pressure gaseous refrigerant flowing out of the heat absorption channel 131 enters the low-pressure supplementary port 115 for Replenish refrigerant for the primary compression cavity to improve its compression energy efficiency.
  • a first-level throttling device 16 is provided between the condenser 12 and the gas-liquid separation device 14, which plays a role of throttling and reducing the pressure of the refrigerant.
  • the high-pressure liquid refrigerant from the condenser 12 is throttled by the first-stage throttling device 16, and the refrigerant pressure drops to the intermediate pressure pm.
  • the refrigerant can be initially reduced in pressure, which is beneficial to the subsequent stage Gas-liquid separation and the amount of refrigerant entering the subsequent stage.
  • the refrigerant includes liquid refrigerant and gas refrigerant that is not fully liquefied in the condenser 12, and part of the liquid refrigerant vaporizes when passing through the first-level throttling device 16, and the mixed refrigerant enters the gas-liquid In the separation device 14, gas-liquid separation is performed.
  • the separated gaseous refrigerant is still at an intermediate pressure state due to the pressure. Therefore, the separated gaseous refrigerant is directly entered into the secondary compression chamber through the air supplement port 114 for compression. After being compressed by the first-stage compression chamber, it directly enters the second-stage compression chamber as intermediate supplementary air, which can reduce the power consumption of the first-stage compression chamber and increase the unit refrigeration capacity, which increases the efficiency of the unit by about 7%.
  • the primary throttling device 16 can be implemented in the form of an electronic expansion valve, an orifice plate, and an electronic expansion valve combined with an orifice plate.
  • the temperature and pressure of the refrigerant entering the gas-liquid separation device 14 can be adjusted by adjusting the opening of the first-stage throttling device 16.
  • a secondary throttling device 17 is provided between the heat exchanger 13 and the evaporator 15.
  • the liquid refrigerant separated by the gas-liquid separation device 14 passes through the heat release channel 132 of the heat exchanger 13 and then is subcooled, and then one of them is throttled to the evaporation pressure p0 by the secondary throttling device 17, and then enters the evaporator 15 to evaporate. Take the cold.
  • the heat release passage 132 of the heat exchanger can increase the degree of subcooling of the refrigerant before entering the secondary throttling device 17, which can increase the cooling capacity per unit mass of refrigerant and reduce the presence of flash gas before the secondary throttling device 17.
  • the secondary throttling device 17 in this embodiment can also be implemented in the form of an electronic expansion valve, an orifice plate, and an electronic expansion valve combined with an orifice plate.
  • the temperature and pressure of the refrigerant entering the evaporator 15 can be adjusted by adjusting the opening degree of the secondary throttling device 17.
  • the heat exchanger 13 in this embodiment can be realized by adopting an economizer, for example, a plate-type heat exchanger economizer can be adopted, which is simple to implement and is convenient for docking with products on the market.
  • an economizer for example, a plate-type heat exchanger economizer can be adopted, which is simple to implement and is convenient for docking with products on the market.
  • the gas-liquid separation device in this embodiment can be realized by a flash evaporator.
  • the condenser 12 is provided with a first liquid level detection device 123, which is used for detecting the liquid level of the liquid refrigerant in the condenser 12; detecting the liquid level of the liquid refrigerant in the condenser 12 is used to adjust the opening of the first-stage throttling device 16 For example, when the liquid level of the condenser 12 is lower than the third set value, the opening degree of the first-stage throttling device 16 is reduced, and when the liquid level of the condenser 12 is higher than the fourth set value, it is increased by one The opening degree of the throttle device 16, wherein the third setting value is greater than 0, and the fourth setting value is greater than the third setting value.
  • the gas-liquid separation device 14 is provided with a second liquid level detection device 144, which is used for the liquid level of the liquid refrigerant in the gas-liquid separation device 14. Detecting the liquid level of the liquid refrigerant in the gas-liquid separation device 14 is used to adjust the opening of the secondary throttling device 17. For example, when the liquid level of the gas-liquid separation device 14 is lower than the first set value, the secondary throttle is reduced. The opening degree of the flow device 17, when the liquid level of the gas-liquid separation device 14 is higher than the second setting value, the opening degree of the secondary throttling device 17 is increased.
  • the first setting value is greater than 0, and the second setting value The value is greater than the first set value.
  • the suction port 112 is provided with a suction temperature sensor 21 and a suction pressure sensor 22; it is used to detect suction pressure and suction temperature, and is used for suction protection of the compressor.
  • a suction temperature sensor 21 and a suction pressure sensor 22; it is used to detect suction pressure and suction temperature, and is used for suction protection of the compressor.
  • the exhaust port 113 is provided with an exhaust temperature sensor 23 and an exhaust pressure sensor 24, which are used to detect exhaust pressure and exhaust temperature, and are used for exhaust protection of the compressor.
  • an exhaust temperature sensor 23 and an exhaust pressure sensor 24 which are used to detect exhaust pressure and exhaust temperature, and are used for exhaust protection of the compressor.
  • the value detected by the above sensors can also be used to protect the compressor from overheating and to calculate the exhaust gas superheat.
  • the unit When the exhaust gas superheat is lower than the exhaust pre-warning set value, the unit will reduce load, and when the gas superheat is low When the set value of exhaust protection is stopped, the exhaust superheat is the saturation temperature difference between exhaust temperature and exhaust pressure.
  • the low-pressure supplemental gas port 115 is also provided with a first supplemental gas temperature sensor 25 and a first supplementary gas pressure sensor 26; they are respectively used to detect the temperature and pressure of the low-pressure supplementary gas, and are used to adjust the opening of the throttle element 18 to adapt it System cooling and load balance.
  • the high-pressure supplemental gas port 114 is provided with a second supplemental gas temperature sensor 27 and a second supplementary gas pressure sensor 28. They are used to detect the temperature and pressure of the high-pressure supplementary gas respectively, and are used to adjust the opening degree of the first-stage throttle device 16.
  • a flow adjustment device 28 is provided between the first outlet 142 of the gas-liquid separation device 14 and the intermediate pressure supplementary gas port 114, which is used to control the amount of supplementary gas for the secondary compression chamber, by calculating the intake of the intermediate pressure supplementary gas port 114
  • the degree of superheat when the suction superheat of the intermediate pressure supplementary port is less than 0, the opening degree of the first-level throttle device is reduced, and the opening degree of the second-stage throttle device is increased, and the opening degree of the flow regulating device is reduced Or close.
  • the compressor in this embodiment is a two-stage centrifugal compressor.
  • the inlet of the one-stage compression chamber is provided with a guide vane 116.
  • the guide vane 116 is connected to a drive motor (not shown in the figure), and the drive motor drives and guides
  • the flow sheet 116 moves to adjust the opening of the suction port 112, which can be used to assist the adjustment of the secondary throttling device and control the amount of refrigerant entering the compressor.
  • the compressor of this embodiment uses variable speed as the main capacity control method, and is assisted by the inlet guide vane 116 when necessary.
  • the refrigerant enters the primary compression chamber of the compressor through the suction port in the form of low-pressure and low-temperature superheated steam. Then, by adjusting the opening degree of the guide vane 116, it can assist the compressor control under partial load conditions.
  • the two impellers 29 and 30 are mounted on a common shaft 31.
  • the gaseous refrigerant passes through the primary impeller 29 to increase the velocity energy of the refrigerant, and in the secondary impeller 30 again increases velocity energy to the refrigerant, converts the velocity energy into the final exhaust pressure, and is discharged through the exhaust port 113.
  • the refrigerant enters the condenser 12 in the form of high-pressure superheated steam.
  • the first-stage impeller 19 is provided with a low-pressure gas supplement port 115 facing the inlet side, and a medium-pressure gas supplement port 114 is provided between the first-stage compression chamber and the second-stage compression chamber.
  • the compressor 11 of this embodiment can also be implemented by other compressors with two-stage compression functions, such as a screw compressor unit or a scroll compressor unit.
  • the ph diagram (pressure enthalpy diagram) of the chiller of this embodiment in the figure, 1'-2' represents the compression process of the first-stage compression chamber, and 2'-10-3 represents the first-stage compression chamber
  • 3-4 represents the compression process in the secondary compression chamber
  • 4-6 represents the cooling, condensation and subcooling process in the condenser 12
  • 6 7 represents the throttling process of the primary throttling device 16
  • the refrigerant at 7 o'clock is separated into saturated gas at 10 o'clock
  • the separated liquid is supercooled to 8'o'clock
  • 8'by the heat exchanger 13 -9' denotes the throttling process through the secondary throttling device 17
  • 9'-1' denotes the superheating process after being evaporated and cooled in the evaporator 15 and mixed with the superheated gas in the heat releasing passage 132
  • this embodiment proposes a method for controlling a chiller, which includes the chiller described in the first embodiment.
  • a chiller which includes the chiller described in the first embodiment.
  • the control method of the unit is.
  • the liquid level of the condenser 16 is detected, and the opening degree of the primary throttling device 16 is adjusted according to the liquid level of the condenser 16.
  • the liquid level of the gas-liquid separation device 14 is detected, and the opening degree of the secondary throttling device 17 is adjusted according to the liquid level of the gas-liquid separation device 14.
  • the compressor protection step includes any combination of the suction pressure protection step, the discharge pressure and discharge temperature protection step, and the discharge superheat protection step.
  • the method of adjusting the opening degree of the secondary throttling device 17 according to the liquid level of the gas-liquid separation device 14 is: when the liquid level of the gas-liquid separation device 14 is lower than the first set value, reduce the secondary throttling device 17 Opening degree.
  • reduce the opening degree of the secondary throttling device 17 When the liquid level of the gas-liquid separation device 14 is higher than the second set value, increase the opening degree of the secondary throttling device 17, wherein the first set value is greater than 0, and the second set value is greater than the first set value.
  • Set value the opening degree of the secondary throttling device 1 becomes larger.
  • the throttling device resumes the PID adjustment of the liquid level.
  • the opening degree of the primary throttling device 16 is forced to decrease, and the opening degree of the secondary throttling device 17 becomes larger.
  • the throttling device restores the PID adjustment of the liquid level.
  • Detecting the liquid level of the liquid refrigerant in the condenser 12 is used to adjust the opening of the first-stage throttling device 16.
  • the adjustment method is: when the liquid level of the condenser 12 is lower than the third set value, reduce the first-stage throttling The opening of the device 16, when the liquid level of the condenser 12 is higher than the fourth set value, increase the opening of the first-stage throttling device 16, where the third set value is greater than 0, and the fourth set value is greater than the fourth set value.
  • the opening of the first-level throttling device 16 is adjusted by PID with the detection value of the condenser liquid level, and finally stabilizes.
  • a flow adjusting device 28 is provided between the first outlet 142 and the intermediate pressure supplementary port 117.
  • the control method further includes the step of calculating the inhalation superheat of the intermediate pressure supplementary port.
  • the inspiratory superheat of the intermediate pressure supplementary port is less than 0
  • the throttling device resumes PID adjustment and the flow adjustment device opens.
  • the suction pressure protection step includes: detecting suction pressure, when the suction pressure is lower than the low-pressure warning set value, the unit deloads, and when the suction pressure is lower than the low-pressure protection set value, the unit shuts down;
  • Exhaust pressure and exhaust temperature protection steps include: detecting exhaust pressure and exhaust temperature, when the exhaust pressure and exhaust temperature are higher than the high-pressure warning set value, the unit deloads, when the exhaust pressure is higher than the high-pressure protection value Unit shutdown;
  • exhaust gas superheat protection steps include: calculating the exhaust gas superheat degree, when the exhaust gas superheat degree is lower than the exhaust gas warning setting value, the unit deloads, when the gas superheat degree is lower than the exhaust gas protection setting value, the unit shuts down ,
  • the exhaust superheat is the saturation temperature difference corresponding to the exhaust temperature and the exhaust pressure.
  • the control method of the throttling element 18 is: after the compressor is started, the opening degree of the throttling element 18 is controlled according to the target setting value of the superheat degree of the heat release passage 132 (default 8° C.).

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  • Engineering & Computer Science (AREA)
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  • General Engineering & Computer Science (AREA)
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Abstract

L'invention concerne une unité de refroidissement d'eau, comprenant : un compresseur, le compresseur comprenant une cavité de compression primaire et une cavité de compression secondaire communiquant l'une avec l'autre, et ayant un orifice d'aspiration de gaz, un orifice d'alimentation en gaz à basse pression, un orifice d'alimentation en gaz à pression intermédiaire et un orifice d'évacuation de gaz ; un condenseur ayant une entrée de condensation et une sortie de condensation ; un échangeur de chaleur ayant un canal d'absorption de chaleur et un canal d'évacuation de chaleur ; un évaporateur ayant une entrée d'évaporation et une sortie d'évaporation, la sortie d'évaporation étant reliée à l'orifice d'aspiration de gaz ; et un séparateur gaz-liquide ayant une entrée de liquide, une première sortie et une seconde sortie, la première sortie étant reliée à l'orifice d'alimentation en gaz à pression intermédiaire, et la seconde sortie étant reliée à une entrée du canal d'évacuation de chaleur. Un trajet à partir d'une sortie du canal d'évacuation de chaleur est relié à l'entrée d'évaporation, et l'autre trajet est relié à une entrée du canal d'absorption de chaleur. Dans l'unité de refroidissement d'eau de l'invention, avant d'entrer dans l'évaporateur, un fluide frigorigène passe à travers le canal d'évacuation de chaleur de façon à évacuer la chaleur, ce qui permet d'augmenter le degré de surfusion du fluide frigorigène avant que le fluide frigorigène n'entre dans l'évaporateur, d'augmenter une capacité de refroidissement par masse d'unité du fluide frigorigène, de réduire le gaz de détente dans le fluide frigorigène avant que celui-ci n'entre dans l'évaporateur, et de diminuer une pression et la température du fluide frigorigène.
PCT/CN2020/091093 2019-06-22 2020-05-19 Unité de refroidissement d'eau et procédé de commande WO2020259131A1 (fr)

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CN201910545523.7A CN112113364A (zh) 2019-06-22 2019-06-22 一种冷水机组及控制方法
CN201910545523.7 2019-06-22

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Cited By (1)

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CN112728729A (zh) * 2021-02-23 2021-04-30 珠海格力节能环保制冷技术研究中心有限公司 空调系统及具有其的空调器

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CN113739275B (zh) * 2021-08-03 2022-12-13 青岛海信日立空调系统有限公司 一种空调系统

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