Refrigerating system control method and device

Abstract

The invention relates to a refrigerating system control method and device. The method comprises the steps that the current exhaust temperature of a first compressor of a refrigerating system is obtained; when the current exhaust temperature is larger than or equal to the first preset exhaust temperature, the first temperature gear where the current exhaust temperature is located is determined to be a first target temperature gear from a plurality of preset first temperature gears, and the temperature interval where the first target temperature gear is located is determined to be a target temperature interval from a plurality of preset temperature intervals; the temperature range of each temperature interval comprises at least one first temperature grade; the air return liquid injection valve is controlled to operate at a non-zero first preset opening degree associated with the first target temperature gear, and the exhaust liquid injection valve is controlled to operate at a second preset opening degree associated with the target temperature interval; the second preset opening degree associated with the temperature interval with the higher temperature is larger.

Description

Technical Field

[0001] This invention relates to the field of temperature control technology, and in particular to a method and apparatus for controlling a refrigeration system. Background Technology

[0002] With economic development and social progress, electronic components (such as chips) are increasingly widely used in people's lives. Before leaving the factory, electronic components need to be tested on testing and sorting equipment to test their stability and reliability under high and low temperature environments. Typically, testing and sorting equipment includes a refrigeration system, where the load end of the refrigeration system exchanges heat with the electronic components to control their temperature.

[0003] When a refrigeration system operates under normal temperature or high-temperature production conditions, the load generates a large amount of heat, resulting in a high return gas temperature and consequently a high discharge temperature, which negatively impacts the refrigeration system. Traditionally, a bypass pipe is connected to the rear end of the condenser. In this bypass pipe, the refrigerant mixes with the refrigerant returning from heat exchange with the external load and enters the compressor's return gas end together, thereby lowering the compressor's return gas temperature and ultimately reducing the compressor's discharge temperature.

[0004] The aforementioned cooling method controls the opening and closing of the solenoid valve on the bypass line based on the given upper and lower limits of the compressor discharge temperature. It cannot adjust the refrigerant flow rate in real time according to changes in discharge temperature. When the discharge temperature rises rapidly, the bypass line opens fully, carrying away most of the refrigerant flow from the main line. This can easily prevent the load from reaching the set production temperature and poses a risk of liquid carryover in the compressor. Furthermore, because the discharge temperature drops to the lower limit after the solenoid valve opens, it will rise again after the valve closes, easily leading to periodic temperature fluctuations and significant volatility, which is detrimental to the rapid and stable operation of the system. Summary of the Invention

[0005] Therefore, it is necessary to provide a refrigeration system control method and apparatus that can improve the above-mentioned problems.

[0006] A method for controlling a refrigeration system, comprising:

[0007] Obtain the current discharge temperature of the first compressor in the refrigeration system;

[0008] When the current exhaust temperature is greater than or equal to the first preset exhaust temperature, the first temperature range in which the current exhaust temperature is located is determined from a plurality of preset first temperature ranges as the first target temperature range, and the temperature range in which the first target temperature range is located is determined from a plurality of preset temperature ranges as the target temperature range; each temperature range contains at least one first temperature range.

[0009] The return gas injection valve is controlled to operate at a non-zero first preset opening degree associated with the first target temperature range, and the exhaust gas injection valve is controlled to operate at a second preset opening degree associated with the target temperature range; the higher the temperature range, the larger the second preset opening degree associated with it.

[0010] The return gas injection valve is located on the second bypass line of the refrigeration system used for the return gas cooling of the first compressor, and the exhaust gas injection valve is located on the first bypass line of the refrigeration system used for the exhaust gas cooling of the first compressor.

[0011] In one embodiment,

[0012] The temperature range that is less than the second preset exhaust temperature is the first temperature range. The first temperature range includes multiple first temperature levels. The first temperature level with a lower temperature in the first temperature range is associated with a smaller first preset opening. The second preset opening associated with the first temperature range is zero.

[0013] The second preset exhaust temperature is greater than the first preset exhaust temperature.

[0014] In one embodiment,

[0015] The temperature range with a temperature range greater than or equal to the second preset exhaust temperature is the second temperature range. Each second temperature range includes a first temperature level. The smaller the temperature of the second temperature range, the smaller the non-zero second preset opening degree associated with it. The first preset opening degree associated with the first temperature level included in all the second temperature ranges is a first fixed opening degree.

[0016] The second preset exhaust temperature is greater than the first preset exhaust temperature, and the first preset opening degree associated with the first temperature range that is less than the second preset exhaust temperature is less than the first fixed opening degree.

[0017] In one embodiment, it further includes:

[0018] When the current exhaust temperature is less than the third preset exhaust temperature, both the return gas injection valve and the exhaust injection valve are controlled to operate at zero opening.

[0019] The third preset exhaust temperature is lower than the first preset exhaust temperature.

[0020] In one embodiment,

[0021] Controlling the return gas injection valve to operate at a non-zero first preset opening degree associated with the first target temperature range, and controlling the exhaust gas injection valve to operate at a second preset opening degree associated with the target temperature range, includes:

[0022] The return gas injection valve is controlled to operate at a non-zero first initial opening, and the exhaust gas injection valve is controlled to operate at a second initial opening.

[0023] After the return gas injection valve operates at the first initial opening and the exhaust gas injection valve operates at the second initial opening for a first preset time, the return gas injection valve is controlled to switch from the first initial opening to the first preset opening associated with the first target temperature range, and the exhaust gas injection valve is controlled to switch from the second initial opening to the second preset opening associated with the target temperature range.

[0024] In one embodiment, it further includes:

[0025] Obtain the current production temperature at the load end of the refrigeration system;

[0026] When the current production temperature is greater than the first preset production temperature but less than the second preset production temperature, the second temperature range where the current production temperature is located is determined from a plurality of preset second temperature ranges as the second target temperature range.

[0027] Control the first thermostatic valve to operate at a third preset opening degree associated with the second target temperature range;

[0028] The higher the temperature of the second temperature range, the greater the associated third preset opening degree;

[0029] The first thermostatic valve is located on the third bypass pipe of the refrigeration system. The third bypass pipe connects the inlet end of the load end and the discharge end of the first compressor.

[0030] In one embodiment, it further includes:

[0031] When the current production temperature is greater than or equal to the second preset production temperature, the opening degree of the first thermostatic valve is controlled to be zero.

[0032] In one embodiment, it further includes:

[0033] When the current exhaust temperature is less than or equal to the fourth preset exhaust temperature, the third temperature range where the current exhaust temperature is located is determined from a plurality of preset third temperature ranges as the third target temperature range.

[0034] Control the first thermostatic valve to operate at a non-zero fourth preset opening degree associated with the third target temperature range;

[0035] The fourth preset exhaust temperature is lower than the first preset exhaust temperature, and the fourth preset opening degree associated with the third temperature range is smaller as the temperature increases.

[0036] The first thermostatic valve is located on the third bypass pipe of the refrigeration system. The third bypass pipe connects the inlet end of the load end and the discharge end of the first compressor.

[0037] In one embodiment, it further includes:

[0038] Obtain the current production temperature at the load end of the refrigeration system and the current discharge superheat of the second compressor;

[0039] When the current exhaust superheat is less than the preset exhaust superheat, the fourth temperature range associated with the current exhaust superheat is determined from a plurality of preset fourth temperature ranges as the fourth target temperature range.

[0040] Control the second thermostatic valve to operate at the fifth preset opening degree associated with the fourth target temperature range;

[0041] The higher the temperature of the fourth temperature setting, the smaller the associated fifth preset opening.

[0042] The second thermostatic valve is located on the fourth bypass pipe of the refrigeration system. The fourth bypass pipe is connected to the exhaust end and the return end of the second compressor.

[0043] A refrigeration system control device, comprising:

[0044] The acquisition module is used to acquire the current discharge temperature of the first compressor in the refrigeration system;

[0045] The determining module is configured to, when the current exhaust temperature is greater than or equal to a first preset exhaust temperature, determine the first temperature range associated with the current exhaust temperature as a first target temperature range from a plurality of preset first temperature ranges, and determine the temperature range in which the first target temperature range is located as a target temperature range from a plurality of preset temperature ranges; each temperature range contains at least one first temperature range.

[0046] The control module is used to control the return gas injection valve to operate at a non-zero first preset opening degree associated with the first target temperature range, and to control the exhaust gas injection valve to operate at a second preset opening degree associated with the target temperature range; the higher the temperature range, the larger the second preset opening degree associated with it.

[0047] The return gas injection valve is located on the second bypass line of the refrigeration system used for returning gas cooling of the first compressor, and the exhaust gas injection valve is located on the first bypass line of the refrigeration system used for exhaust gas cooling of the first compressor.

[0048] The aforementioned refrigeration system control method and apparatus, when the current production temperature is greater than or equal to a first preset discharge temperature, determines the first temperature range containing the current production temperature as the first target temperature range and the temperature range containing the first target temperature range as the target temperature range. It then controls the return gas injection valve to operate at a first preset opening degree associated with the first target temperature range and the discharge injection valve to operate at a second preset opening degree associated with the target temperature range. Thus, for different current discharge temperatures, controlling the return gas injection valve and the discharge injection valve to operate at appropriate opening degrees adjusts the refrigerant flow, thereby reducing the discharge temperature of the first compressor. Compared to the prior art method of reducing the first compressor discharge temperature by adjusting the refrigerant flow using a solenoid valve with only on / off functionality and no opening degree adjustment function, this method avoids removing a significant amount of cooling capacity from the first circulation loop, ensuring that the load side can reach the target production temperature. Furthermore, controlling the return gas injection valve and the discharge injection valve to operate at appropriate opening degrees to adjust the refrigerant flow for different current discharge temperatures prevents the current discharge temperature from rising again, reduces fluctuations in the current discharge temperature, and facilitates the rapid and stable operation of the refrigeration system. Attached Figure Description

[0049] Figure 1 This is a structural diagram of a refrigeration system provided in one embodiment of this application;

[0050] Figure 2 A flowchart of a refrigeration system control method provided in an embodiment of this application;

[0051] Figure 3 A flowchart of a refrigeration system control method provided in another embodiment of this application;

[0052] Figure 4 A diagram showing the relationship between the first temperature range, the second temperature range, and the first temperature setting in a refrigeration system control method provided in another embodiment of this application.

[0053] Explanation of reference numerals in the attached figures:

[0054] 100. Refrigeration system; 10. First refrigeration module; 11. First compressor; 12. First condenser; 13. First throttle valve; 14. Load end; 15. Second bypass line; 16. Return gas injection valve; 17. First bypass line; 18. Exhaust injection valve; 19. Main line; 110. First branch line; 120. Second branch line; 130. Oil separator; 140. Dryer filter; 150. Connecting line; 160. Unloading valve; 170. Expansion tank; 180. Third bypass line; 190. First thermostatic valve; 20. Second refrigeration module; 21. Second compressor; 22. Second condenser; 23. Second throttle valve; 24. Second dryer filter; 25. Fourth bypass line; 26. Second thermostatic valve; A. First circulation loop; B. Second circulation loop. Detailed Implementation

[0055] To make the above-mentioned objects, features, and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings. Many specific details are set forth in the following description to provide a thorough understanding of the present invention. However, the present invention can be practiced in many other ways different from those described herein, and those skilled in the art can make similar modifications without departing from the spirit of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0056] In the description of this invention, it should be understood that the terms "center," "longitudinal," "lateral," "length," "width," "thickness," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," "outer," "clockwise," "counterclockwise," "axial," "radial," and "circumferential" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0057] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one of that feature. In the description of this invention, "a plurality of" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0058] In this invention, unless otherwise explicitly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components, unless otherwise explicitly limited. Those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0059] In this invention, unless otherwise explicitly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "over," and "on top" of the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0060] It should be noted that when an element is referred to as being "fixed to" or "set on" another element, it can be directly on the other element or there may be an intervening element. When an element is considered to be "connected to" another element, it can be directly connected to the other element or there may be an intervening element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only possible implementation.

[0061] See Figure 1 One embodiment of this application provides a refrigeration system 100, which includes a first refrigeration module 10. The first refrigeration module 10 includes a first compressor 11, a first condenser 12, a first throttle valve 13, and a load terminal 14. The first compressor 11, the first condenser 12, the first throttle valve 13, and the load terminal 14 are sequentially connected to form a first circulation loop A. The refrigerant can circulate among the first compressor 11, the first condenser 12, the first throttle valve 13, and the load terminal 14. When the refrigerant flows through the load terminal 14, it can exchange heat with electronic components to control the temperature of the electronic components. Specifically, the load terminal 14 is provided with a flow channel, and the refrigerant exchanges heat with the electronic components when flowing in the flow channel.

[0062] Optionally, a heating device is installed on the load end 14. When the refrigerant flows through the flow channel in the load end 14, the heating device heats the load end 14, and the temperature of the load end 14 is controlled by the combined action of the refrigerant and the heating device, thereby controlling the temperature of the electronic components.

[0063] In some specific embodiments, the electronic component is a chip. It is conceivable that in other embodiments, the type of electronic component is not limited.

[0064] The first refrigeration module 10 also includes a first bypass pipe 17 and an exhaust injection valve 18. One end of the first bypass pipe 17 is connected to the portion of the first circulation loop A located between the first condenser 12 and the first throttle valve 13, that is, the first bypass pipe 17 is connected to the pipe located between the output end of the first condenser 12 and the input end of the first throttle valve 13. The other end of the first bypass pipe 17 is connected to the compression chamber of the first compressor 11. The exhaust injection valve 18 is located on the first bypass pipe 17, and the opening degree of the exhaust injection valve 18 is adjustable. That is, the exhaust injection valve 18 not only has a fully open and fully closed function, but also has an opening degree adjustment function between fully open and fully closed. When the exhaust injection valve 18 is fully closed, its opening degree is zero, and when it is fully open, its opening degree is 100%.

[0065] When the first bypass pipe 17 is opened, it mixes with the high-temperature refrigerant gas in the compression chamber, directly cooling the excessively high exhaust temperature.

[0066] It should be noted that regardless of the type of compressor, all compressors follow three core processes: intake, compression, and exhaust. The intake process involves low-temperature, low-pressure gas entering the compression chamber through the intake port (return port). The compression process reduces the gas volume through mechanical action (such as piston movement and rotor rotation), increasing the gas pressure and temperature. The exhaust process involves high-temperature, high-pressure gas being pushed from the exhaust port into the exhaust pipe and transported to the condenser.

[0067] The refrigeration system 100 provided in this application embodiment has an adjustable opening degree for the discharge injection valve 18, which is located on the first bypass pipe 17 for cooling the discharge of the first compressor 11. When cooling the discharge of the first compressor 11 is required, the opening degree of the discharge injection valve 18 can be controlled based on the relationship between the current discharge temperature of the first compressor 11 and the preset discharge temperature. Thus, for different current discharge temperatures, controlling the discharge injection valve 18 to operate at an appropriate opening degree to adjust the refrigerant flow rate achieves the purpose of reducing the discharge temperature of the first compressor 11. Compared to the prior art method of adjusting the refrigerant flow rate to reduce the discharge temperature of the first compressor 11 using a solenoid valve with only on / off function and no opening degree adjustment function, this method does not remove a significant amount of cooling capacity from the first circulation loop A, ensuring that the load end 14 can reach the target production temperature. Furthermore, controlling the discharge injection valve 18 to operate at an appropriate opening degree to adjust the refrigerant flow rate for different current discharge temperatures can prevent the current discharge temperature from rising again, reducing fluctuations in the current discharge temperature and facilitating the rapid and stable operation of the refrigeration system 100.

[0068] It should be noted that the current exhaust temperature is the real-time measured exhaust temperature of the first compressor 11. Specifically, the current exhaust temperature can be measured by a first temperature sensor located at the exhaust end of the first compressor 11.

[0069] Continue reading Figure 1 The first refrigeration module 10 also includes a second bypass pipe 15 and a return gas injection valve 16. One end of the second bypass pipe 15 is connected to the portion of the first circulation loop A located between the first condenser 12 and the first throttle valve 13, that is, the second bypass pipe 15 is connected to the pipe located between the output end of the first condenser 12 and the input end of the first throttle valve 13. The other end of the second bypass pipe 15 is connected to the return gas end of the first compressor 11. Specifically, the other end of the second bypass pipe 15 is connected to the portion of the first circulation loop A located between the load end 14 and the first compressor 11, that is, the other end of the second bypass pipe 15 is connected to the pipe located between the output end of the first circulation loop A located at the load end 14 and the input end of the first compressor 11. The return gas injection valve 16 is provided on the second bypass pipe 15, and the opening degree of the return gas injection valve 16 is adjustable. That is, the return gas injection valve 16 not only has the functions of fully open and fully closed, but also has the function of adjusting the opening degree between fully open and fully closed. When the return gas injection valve 16 is fully closed, its opening degree is zero, and when it is fully open, its opening degree is 100%.

[0070] When the second bypass line 15 is opened, it mixes with the refrigerant that returns after heat exchange at the load end 14, thereby reducing the return gas temperature of the first compressor 11. When the return gas temperature of the first compressor 11 decreases, the discharge temperature decreases.

[0071] The above configuration, with the return gas injection valve 16 located on the second bypass pipe 15 for cooling the return gas of the first compressor 11, and the opening of the return gas injection valve 16 adjustable, allows for control of the opening of the return gas injection valve 16 based on the relationship between the current exhaust temperature and the preset exhaust temperature when cooling of the first compressor 11's exhaust gas is required. Thus, by controlling the return gas injection valve 16 to operate at an appropriate opening for different current exhaust temperatures to regulate the refrigerant flow, the exhaust temperature of the first compressor 11 is reduced. Compared to the prior art method of reducing the exhaust temperature of the first compressor 11 by regulating the refrigerant flow using a solenoid valve with only on / off functionality and no opening adjustment function, this method avoids removing a significant amount of cooling capacity from the first circulation loop A, ensuring that the load end 14 can reach the target production temperature. Furthermore, controlling the return gas injection valve 16 to operate at an appropriate opening for different current exhaust temperatures to regulate the refrigerant flow prevents the current exhaust temperature from rising again, reduces fluctuations in the current exhaust temperature, and facilitates the rapid and stable operation of the refrigeration system 100.

[0072] In some embodiments, the return gas injection valve 16 is a throttle valve. In this way, the refrigerant in the second bypass line 15 is cooled and depressurized when it passes through the return gas injection valve 16, which is beneficial to the return gas cooling of the first compressor 11.

[0073] Optionally, the discharge injection valve 18 is a throttle valve. In this way, the refrigerant in the first bypass line 17 is cooled and depressurized when it passes through the discharge injection valve 18, which is beneficial to the cooling of the discharge from the first compressor 11.

[0074] In some specific embodiments, both the return gas injection valve 16 and the exhaust gas injection valve 18 are electronic expansion valves.

[0075] It is conceivable that in some other embodiments, the return gas injection valve 16 and the exhaust injection valve 18 may also be valves without throttling function, and when the return gas injection valve 16 and the exhaust injection valve 18 are throttling valves, the type of throttling valve is not limited.

[0076] In some embodiments, see further reference. Figure 1 The first refrigeration module 10 includes a main line 19, a first branch line 110, and a second branch line 120. One end of the main line 19 is connected to the portion of the first circulation loop A located between the first condenser 12 and the first throttle valve 13. One end of each of the first branch lines 110 and 120 is connected to the other end of the main line 19. The other end of the first branch line 110 is connected to the portion of the first circulation loop A located between the load end 14 and the first compressor 11. The other end of the second branch line 120 is connected to the compression chamber. The main line 19 and the first branch line 110 together form a second bypass pipe 15, and the main line 19 and the second branch line 120 together form a first bypass pipe 17. A return gas injection valve 16 is located on the first branch line 110, and an exhaust gas injection valve 18 is located on the second branch line 120.

[0077] In the above configuration, the second bypass pipe 15 and the first bypass pipe 17 share the main pipe 19, which simplifies the piping configuration of the first refrigeration module 10.

[0078] It is conceivable that in other embodiments, the second bypass pipe 15 and the first bypass pipe 17 may be configured to have no shared parts and be completely independent of each other.

[0079] In some embodiments, the first refrigeration module 10 further includes an oil separator 130, which is located between the first compressor 11 and the first condenser 12. The oil separator 130 can separate the lubricating oil in the high-pressure steam discharged from the first compressor 11 to ensure the safe and efficient operation of the first refrigeration module 10.

[0080] The first refrigeration module 10 also includes a first dryer filter 140, which is located between the exhaust end of the first compressor 11 and the input end of the first throttle valve 13 to perform the functions of impurity filtration and drying.

[0081] In some embodiments, the first refrigeration module 10 further includes a connecting pipe 150, one end of which is connected to the portion of the first circulation loop A located between the first compressor 11 and the first condenser 12, and the other end of which is connected to the portion of the first circulation loop A located between the first compressor 11 and the load end 14. The connecting pipe 150 is also equipped with an unloading valve 160 and an expansion tank 170. On one hand, the expansion tank 170 is used to store excess refrigerant; on the other hand, when the refrigeration system 100 is shut down, the pressure will be very high, and some of the refrigerant will enter the expansion tank 170 after expansion to balance the pressure. When the pressure of the refrigeration system 100 is too high, and the expansion tank 170 cannot balance the pressure, the unloading valve 160 opens to release pressure.

[0082] In some embodiments, the first refrigeration module 10 further includes a third bypass pipe 180, one end of which is connected to the discharge end of the first compressor 11, and the other end is connected to the input end of the load end 14. Specifically, the second bypass pipe 15 is connected to the portion of the first circulation loop A located between the discharge end of the first compressor 11 and the input end of the first condenser 12, and the other end is connected to the portion of the first circulation loop A located between the output end of the first throttle valve 13 and the input end of the load end 14. A first thermostatic valve 190 is provided on the third bypass pipe 180, and the opening degree of the first thermostatic valve 190 is adjustable. That is, the first thermostatic valve 190 not only has a fully open and fully closed function, but also has an opening degree adjustment function between fully open and fully closed. When the first thermostatic valve 190 is fully closed, its opening degree is zero, and when it is fully open, its opening degree is 100%.

[0083] When the current production temperature is low, resulting in a low current discharge temperature of the first compressor 11, the opening of the first thermostatic valve 190 can be controlled based on the current discharge temperature to prevent alarms caused by excessively low return gas temperature and / or current discharge temperature of the first compressor 11. When the current production temperature is high, the opening of the first thermostatic valve 190 can be controlled based on the current production temperature, working in coordination with the return gas injection valve 16 and the discharge injection valve 18 to maintain a stable and balanced state for the entire refrigeration system 100.

[0084] It should be noted that the current production temperature is the temperature of the load terminal 14 measured in real time. Specifically, the current production temperature can be measured by a second temperature sensor installed on the load terminal 14.

[0085] In some embodiments, see further reference. Figure 1The refrigeration system 100 also includes a second refrigeration module 20, which includes a second compressor 21, a second condenser 22, a second throttle valve 23, and the aforementioned first condenser 12. The second compressor 21, second condenser 22, second throttle valve 23, and first condenser 12 are sequentially connected to form a second circulation loop B. The first condenser 12 is an evaporator-condenser, and the first circulation loop A and the second circulation loop B are thermally coupled through the evaporator-condenser. The refrigerant can circulate among the second compressor 21, second condenser 22, second throttle valve 23, and first condenser 12. When the refrigerant flows through the first condenser 12, it can exchange heat with the first circulation loop A, thereby reducing the amount of refrigerant in the first circulation loop A.

[0086] It should be noted that, since the first condenser 12 is an evaporative condenser, it has a first channel forming a first circulation loop A and a second channel forming a second circulation loop B. Therefore, the first condenser 12 has two input terminals and two output terminals. The two ends of the first channel form one input terminal and one output terminal corresponding to the first circulation loop A, and the two ends of the second channel form another input terminal and another output terminal corresponding to the second circulation loop B.

[0087] It should also be noted that, since the first circulation loop A and the second circulation loop B are thermally coupled through the evaporator and condenser, the refrigeration system 100 forms a two-stage cascade refrigeration system. The second refrigeration module 20 is a high-temperature refrigeration module, and the first refrigeration module 10 is a low-temperature refrigeration module.

[0088] Furthermore, the second refrigeration module 20 also includes a second dryer filter 24, which is located between the exhaust end of the second compressor 21 and the input end of the second throttle valve 23, to perform the function of filtering and drying impurities.

[0089] The second refrigeration module 20 includes a fourth bypass pipe 25. One end of the fourth bypass pipe 25 is connected to the discharge end of the second compressor 21, and the other end is connected to the return end of the second compressor 21. Specifically, one end of the fourth bypass pipe 25 is connected to the portion of the second circulation loop B located between the discharge end of the second compressor 21 and the input end of the second condenser 22, and the other end is connected to the portion of the second circulation loop B located between the output end of the first condenser 12 and the return end of the second compressor 21. A second thermostatic valve 26 is provided on the fourth bypass pipe 25, and the opening degree of the second thermostatic valve 26 is adjustable. That is, the second thermostatic valve 26 not only has an on / off function, but also has an opening degree adjustment function between on and off. When the second thermostatic valve 26 is fully closed, its opening degree is zero, and when it is fully open, its opening degree is 100%.

[0090] When the current production temperature is low, resulting in a low exhaust temperature or low exhaust superheat, the opening of the second thermostatic valve 26 can be controlled according to the current production temperature to avoid alarms caused by excessive exhaust temperature and / or excessive exhaust temperature of the second compressor 21.

[0091] Another embodiment of this application provides a testing and sorting device, including the aforementioned refrigeration system 100. Since the refrigeration system 100 has beneficial effects, the testing and sorting device including the refrigeration system 100 also has the same beneficial effects, which will not be described in detail here.

[0092] See Figure 2 Another embodiment of this application also provides a refrigeration system control method, including:

[0093] S110: Obtain the current discharge temperature of the first compressor 11 of the refrigeration system 100;

[0094] The current exhaust temperature is the exhaust temperature of the first compressor 11 measured in real time. Specifically, the exhaust end of the first compressor 11 is equipped with a first temperature sensor, which measures and obtains the current exhaust temperature.

[0095] S120: When the current exhaust temperature is greater than or equal to the first preset exhaust temperature, the first temperature range where the current exhaust temperature is located is determined from a plurality of preset first temperature ranges as the first target temperature range, and the temperature range where the first target temperature range is located is determined from a plurality of preset temperature ranges as the target temperature range; the temperature range of each temperature range contains at least one first temperature range.

[0096] S130: Control the return gas injection valve 16 to operate at a non-zero first preset opening degree associated with the first target temperature range, and control the exhaust injection valve 18 to operate at a second preset opening degree associated with the target temperature range; the larger the temperature range, the larger the second preset opening degree associated with it.

[0097] A return gas injection valve 16 is installed on the second bypass line 15 of the refrigeration system 100 for cooling the return gas of the first compressor 11, and an exhaust gas injection valve 18 is installed on the first bypass line 17 of the refrigeration system 100 for cooling the exhaust gas of the first compressor 11. Specifically, the second bypass line 15 is connected to the portion of the first circulation loop A located between the first condenser 12 and the first throttle valve 13, and the other end is connected to the return gas end of the first compressor 11. One end of the first bypass line 17 is connected to the portion of the first circulation loop A located between the first condenser 12 and the first throttle valve 13, and the other end is connected to the compression chamber of the first compressor 11.

[0098] Under certain operating conditions (such as normal temperature and high temperature conditions), when the current production temperature of the load terminal 14 is high (e.g., greater than or equal to 0°C), the current discharge temperature of the first compressor 11 will be greater than or equal to the first preset discharge temperature. In this case, it is necessary to cool the discharge from the first compressor 11. The current production temperature is the temperature of the load terminal 14 measured in real time. Specifically, a second temperature sensor is installed on the load terminal 14, and the second temperature sensor measures the current production temperature.

[0099] The first preset exhaust temperature is set as needed. In some specific embodiments, the first preset exhaust temperature is 80°C. Of course, in other embodiments, the specific value of the first preset exhaust temperature is not limited.

[0100] The exhaust temperature, which is greater than or equal to a first preset exhaust temperature, is divided into multiple temperature ranges, each containing at least one first temperature level. Once the first temperature level at which the current exhaust temperature is located is determined from among the multiple first temperature levels, the target temperature range can be determined based on the temperature range in which the first target temperature level is located.

[0101] Each first temperature range is associated with a first preset opening, and each temperature interval is associated with a second preset opening. The larger the temperature interval, the larger the associated second preset opening. It should be noted that although each temperature range is associated with a first preset opening, the first preset opening can be the same or different for different first temperature ranges; this is not limited here. Generally, a first temperature range is an interval containing multiple temperature values. Of course, in some embodiments, the first temperature range can also be a specific temperature value. When the first temperature range is an interval, all temperature values ​​within that interval are associated with (correspond to) the same first preset opening. When the first temperature range is a temperature value, each temperature value corresponds to a first preset opening.

[0102] Optionally, the first preset opening degree corresponding to each first temperature range can be obtained experimentally, or it can be obtained empirically. Similarly, the second preset opening degree corresponding to each temperature range can be obtained experimentally, or it can be obtained empirically.

[0103] It should be noted that when the current exhaust temperature is greater than or equal to the first preset exhaust temperature, it indicates that the exhaust temperature is high. At this time, the first preset opening degree corresponding to all first temperature ranges is a non-zero opening degree. That is, when the current exhaust temperature is greater than or equal to the first preset exhaust temperature, the return gas injection valve 16 is always in the open state, so that the refrigerant in the second bypass pipe 15 mixes with the refrigerant returning from the load end 14 for use in the return gas cooling of the first compressor 11.

[0104] The refrigeration system control method provided in this application embodiment, when the current production temperature is greater than or equal to a first preset exhaust temperature, determines the first temperature range where the current production temperature is located as the first target temperature range and determines the temperature range where the first target temperature range is located as the target temperature range. It then controls the return gas injection valve 16 to operate at a first preset opening degree associated with the first target temperature range and the exhaust gas injection valve 18 to operate at a second preset opening degree associated with the target temperature range. Thus, for different current exhaust temperatures, the return gas injection valve 16 and the exhaust gas injection valve 18 are controlled to operate at appropriate opening degrees to precisely adjust the refrigerant flow in real time, thereby reducing the exhaust temperature of the first compressor 11. Compared to the prior art method of reducing the exhaust temperature of the first compressor 11 by adjusting the refrigerant flow through a solenoid valve with only on / off function and no opening adjustment function, this method does not remove a significant amount of cooling capacity from the first circulation loop A, ensuring that the load end 14 can reach the target production temperature. Furthermore, by controlling the return gas injection valve 16 and the exhaust gas injection valve 18 to operate at appropriate openings for different current exhaust temperatures, the refrigerant flow can be adjusted in real time and accurately, which can prevent the current exhaust temperature from rising again, reduce the fluctuation of the current exhaust temperature, and facilitate the rapid and stable operation of the refrigeration system 100.

[0105] It should be noted that since each temperature range includes at least one first temperature level, the temperature range covered by the temperature range is greater than or equal to the temperature range covered by the first temperature level. The opening degree of the exhaust liquid injection valve 18 is determined by the temperature range where the current exhaust temperature is located, rather than a first temperature level corresponding to a second preset opening degree. This avoids frequent adjustment of the opening degree of the exhaust liquid injection valve 18 and facilitates the rapid and stable operation of the refrigeration system 100.

[0106] In some embodiments, see Figure 3 Step S130 includes:

[0107] S131: Control the return gas injection valve 16 to operate with a non-zero first initial opening and the exhaust injection valve 18 to operate with a second initial opening;

[0108] S132: After the return gas injection valve 16 operates at the first initial opening and the exhaust injection valve 18 operates at the second initial opening for a first preset time, the return gas injection valve 16 is controlled to switch from the first initial opening to the first preset opening associated with the first target temperature range, and the exhaust injection valve 18 is controlled to switch from the second initial opening to the second preset opening associated with the target temperature range.

[0109] In the above settings, when the current exhaust temperature is greater than or equal to the first preset exhaust temperature, the return gas injection valve 16 and the exhaust gas injection valve 18 are first controlled to operate at a non-zero first initial opening and a second initial opening, respectively. After the return gas injection valve 16 operates at the first initial opening and the exhaust gas injection valve 18 operates at the second initial opening for a first preset time, the return gas injection valve 16 is controlled to switch from the first initial opening to the first preset opening and the exhaust gas injection valve 18 is controlled to switch from the second initial opening to the second preset opening. This is to avoid the return gas injection valve 16 failing to operate to the associated first preset opening in a timely manner according to the first temperature range of the current exhaust temperature and to avoid the exhaust gas injection valve 18 failing to operate to the associated second preset opening in a timely manner according to the temperature range of the current exhaust temperature, so as to avoid the exhaust of the first compressor 11 overheating.

[0110] It should be noted that the first initial opening degree, the second initial opening degree, and the first preset duration are selected as needed. In some specific embodiments, the first initial opening degree is 10%. When the current exhaust temperature is greater than or equal to the first preset exhaust temperature but less than the second preset exhaust temperature, the second initial opening degree is 0; when the current exhaust temperature is greater than or equal to the second preset exhaust temperature, the second initial opening degree is 10%.

[0111] Of course, in some other embodiments, the specific values ​​of the first initial opening and the second initial opening are not limited.

[0112] In some embodiments, the temperature range with a temperature range less than the second preset exhaust temperature is the first temperature range. The first temperature range includes multiple first temperature levels. The first preset opening degree associated with the first temperature level with a lower temperature in the first temperature range is smaller. The second preset opening degree associated with the first temperature range is zero.

[0113] Since the current exhaust temperature is greater than or equal to the first preset exhaust temperature but less than the second preset exhaust temperature, it is generally under normal operating conditions. The heat generated at the load end 14 is relatively small, and the current exhaust temperature is not very high. Therefore, the second preset opening related to the first temperature range is zero, meaning the exhaust injection valve 18 does not need to be opened. The exhaust temperature of the first compressor 11 can be stabilized by adjusting the opening of the return gas injection valve 16 itself. Furthermore, the opening of the return gas injection valve 16 is determined based on the first temperature range of the current exhaust temperature, effectively controlling the low-temperature refrigerant flow in the second bypass pipe 15, thereby reducing the refrigerant mixing temperature returning after heat exchange with the load end 14 and reducing fluctuations in the exhaust temperature of the first compressor 11.

[0114] The second preset exhaust temperature is higher than the first preset exhaust temperature, and the second preset exhaust temperature is set as needed. In some specific embodiments, the second preset exhaust temperature is 100°C. Of course, in other embodiments, the specific value of the second preset exhaust temperature is not limited.

[0115] In some specific embodiments, the first preset exhaust temperature is 80°C, and the second preset exhaust temperature is 100°C. See also... Figure 4 The first temperature range is set to include four first temperature levels, and the first preset opening degree corresponding to different first temperature levels is shown in the table below:

[0116]

[0117] It is conceivable that in some other embodiments, the number of first temperature ranges included in the first temperature range is not limited, nor is the first preset opening degree corresponding to each first temperature range limited.

[0118] In some embodiments, the temperature range with a temperature range greater than or equal to the second preset exhaust temperature is the second temperature range. Each second temperature range includes a first temperature level. The smaller the temperature of the second temperature range, the smaller the non-zero second preset opening degree associated with it. The first preset opening degree associated with the first temperature level included in all second temperature ranges is a first fixed opening degree.

[0119] Among them, the first preset opening degree associated with the first temperature range whose temperature range is less than the second preset exhaust temperature is less than the first fixed opening degree.

[0120] It should be noted that the first fixed opening degree corresponding to the first temperature range included in all the second temperature ranges can be the same or different, and this is not limited here. Generally, for ease of control, the first preset opening degree associated with the first temperature range included in all the second temperature ranges is set to the same first fixed opening degree.

[0121] When the current production temperature is greater than or equal to the second preset exhaust temperature, it is generally in a high-temperature operating condition. The load end 14 generates a lot of heat, and the current exhaust temperature is high. At this time, relying solely on the return gas injection valve 16 cannot suppress the rapid rise in the current exhaust temperature. Therefore, the return gas injection valve 16 maintains a large first fixed opening, controlling the exhaust injection valve 18 to operate at a non-zero second preset opening. After the exhaust injection valve 18 is opened, the low-temperature liquid refrigerant in the first bypass pipe 17 mixes with the high-temperature gas refrigerant in the compression chamber, directly cooling the excessively high exhaust temperature of the first compressor 11, reducing the risk of shutdown due to an alarm caused by an instantaneous high exhaust temperature of the first compressor 11 (such as when the exhaust temperature of the first compressor 11 is greater than or equal to 110°C).

[0122] Furthermore, when the current exhaust temperature is greater than or equal to the second preset exhaust temperature, the second preset opening gradually increases as the temperature value in the second temperature range increases. That is, the second preset opening is larger for the second temperature range with a larger temperature value, so as to increase the exhaust cooling effect on the first compressor 11.

[0123] For some specific implementation methods, please refer to [link / reference]. Figure 4 The second temperature range has three sections, and the second preset opening degree corresponding to different second temperature ranges is shown in the table below:

[0124]

[0125]

[0126] Optionally, the first fixed opening is 35%.

[0127] It is conceivable that in some other embodiments, the number of second temperature ranges is not limited, nor is the second preset opening degree corresponding to each second temperature range limited. Furthermore, the first fixed opening degree is also not limited.

[0128] Furthermore, when the current exhaust temperature is lower than the third preset exhaust temperature, both the first preset opening and the second preset opening are zero. The third preset exhaust temperature is lower than the first preset exhaust temperature. In one specific embodiment, the third preset exhaust temperature is 75°C.

[0129] When the current exhaust temperature is lower than the third preset exhaust temperature, it proves that the exhaust temperature of the first compressor 11 is not over-temperature, and there is no need to open the return gas injection valve 16 and the exhaust injection valve 18.

[0130] In some embodiments, the refrigeration system control method further includes:

[0131] Obtain the current production temperature of the load terminal 14 of the refrigeration system 100;

[0132] When the current production temperature is greater than the first preset production temperature but less than the second preset production temperature, the second temperature range where the current production temperature is located is determined from a plurality of preset second temperature ranges as the second target temperature range.

[0133] The first thermostatic valve 190 is controlled to operate at a third preset opening degree associated with the second target temperature range.

[0134] Among multiple second temperature ranges, the third preset opening degree increases with the increase of the temperature value. That is, each second temperature range corresponds to a third preset opening degree, and the third preset opening degree associated with or corresponding to the second temperature range with a larger temperature value is also larger. Optionally, the third preset opening degree corresponding to each second temperature range can be obtained experimentally, or it can be obtained based on experience. The first thermostatic valve 190 is provided on the third bypass pipe 180 of the refrigeration system 100, and the third bypass pipe 180 connects the inlet end of the load end 14 and the discharge end of the first compressor 11.

[0135] It should also be noted that, generally, the second temperature range is a range containing multiple temperature values. Of course, in some embodiments, the second temperature range can also be a specific temperature value. When the second temperature range is a range, all temperature values ​​within that range correspond to the same third preset opening degree. When the second temperature value is a single temperature value, each temperature value corresponds to a third preset opening degree.

[0136] When the current production temperature is higher than the first preset production temperature, it indicates that the refrigeration system 100 is operating under normal temperature or high temperature conditions. When the current production temperature is only slightly higher than the first preset production temperature, the demand for heating and cooling is at its maximum, heat exchange is relatively sufficient, and the return gas temperature and exhaust temperature of the first compressor 11 are relatively stable. To avoid weakening the cooling capacity, the opening of the first thermostatic valve 190 is kept small. As the current production temperature increases, the required heat is greater and the cooling capacity is less, and the exhaust temperature is prone to becoming too high. To ensure that the refrigeration system 100 is more stable and efficient, the opening of the first thermostatic valve 190 is increased to weaken some of the cooling capacity in advance. The first thermostatic valve 190, the return gas injection valve 16, and the exhaust gas injection valve 18 work together to adjust the system to achieve a stable equilibrium state, resulting in better cooling performance.

[0137] The first and second preset production temperatures are set as needed. In some specific embodiments, the first preset production temperature is 0°C and the second preset production temperature is 130°C.

[0138] In some embodiments, the third preset opening degree corresponding to different second temperature ranges is shown in the table below:

[0139]

[0140] It is conceivable that in some other embodiments, the number of second temperature ranges that are greater than the first preset production temperature and less than the second preset production temperature is not limited, and the third preset opening degree corresponding to each second temperature range is also not limited.

[0141] In some embodiments, the refrigeration system control method further includes:

[0142] When the current production temperature is greater than or equal to the second preset production temperature, the opening degree of the first thermostatic valve 190 is controlled to be zero.

[0143] When the current production temperature is greater than or equal to the second preset production temperature, the current production temperature is too high. At the extreme high temperature, the current production temperature is mainly controlled by the heating device, and the exhaust temperature of the first compressor 11 is adjusted by the return gas injection valve 16 and the exhaust gas injection valve 18. At this time, the first thermostatic valve 190 is closed.

[0144] Specifically, when the second preset production temperature is set to 130°C, and the current production temperature is greater than or equal to 130°C, the opening degree of the first thermostatic valve 190 is zero.

[0145] In some embodiments, the refrigeration system control method further includes:

[0146] When the current exhaust temperature is less than or equal to the fourth preset exhaust temperature, the third temperature range where the current exhaust temperature is located is determined from the multiple preset third temperature ranges as the third target temperature range.

[0147] The first thermostatic valve 190 is controlled to operate at a non-zero fourth preset opening degree associated with the third target temperature range;

[0148] The fourth preset exhaust temperature is lower than the first preset exhaust temperature, and further, the fourth preset exhaust temperature is lower than the third preset exhaust temperature. Among the multiple third temperature ranges, the fourth preset opening decreases as the temperature value increases. That is, each third temperature range corresponds to a fourth preset opening, and the larger the temperature value of the third temperature range, the smaller the fourth preset opening. Optionally, the fourth preset opening corresponding to each third temperature range can be obtained experimentally, or it can be obtained based on experience. The first thermostatic valve 190 is installed on the third bypass pipe 180 of the refrigeration system 100, and the third bypass pipe 180 connects the inlet end of the load end 14 and the exhaust end of the first compressor 11.

[0149] It should also be noted that, generally, the third temperature range is a range containing multiple temperature values. Of course, in some embodiments, the third temperature range can also be a specific temperature value. When the third temperature range is a range, all temperature values ​​within that range correspond to the same third preset opening degree. When the third temperature range is a single temperature value, each temperature value corresponds to a third preset opening degree.

[0150] With the above settings, when the current exhaust temperature is less than or equal to the fourth preset exhaust temperature, it proves that the exhaust temperature of the first compressor 11 is low and it is necessary to increase the exhaust temperature of the first compressor 11. The first thermostatic valve 190 is controlled to operate at the non-zero fourth preset opening degree associated with or corresponding to the third target temperature setting, so that the first thermostatic valve 190 adjusts the exhaust temperature of the first compressor 11 to a reasonable range with an appropriate opening degree.

[0151] In some specific embodiments, the fourth preset exhaust temperature is 65°C, and the fourth preset opening degree corresponding to different third temperature ranges is shown in the table below:

[0152] Current exhaust temperature T (°C) Fourth preset opening % T＜55 15 55≤T＜58 10 58≤T＜62 8 62≤T≤65 5

[0153] It is conceivable that in some other implementations, the number of third temperature ranges is not limited, nor is the fourth preset opening degree corresponding to each third temperature range limited.

[0154] Specifically, when the current exhaust temperature is greater than 70°C, the first thermostatic valve 190 can be closed.

[0155] In some embodiments, the refrigeration system control method further includes:

[0156] Obtain the current production temperature of the load end 14 of the refrigeration system 100 and the current discharge superheat of the second compressor 21;

[0157] When the current exhaust superheat is less than the preset exhaust superheat, the fourth temperature range associated with the current exhaust superheat is determined from a plurality of preset fourth temperature ranges as the fourth target temperature range.

[0158] Control the second thermostatic valve 26 to operate at the fifth preset opening degree associated with the fourth target temperature range;

[0159] Discharge superheat is the difference between the temperature of the gas discharged from the compressor in the refrigeration system 100 and its saturation temperature at the current pressure, used to determine the system's operating status and performance. The normal range is typically 20℃-35℃. The current discharge superheat of the second compressor 21 is the difference between the discharge temperature of the gas discharged from the second compressor 21 and the saturation temperature of the discharged gas at the current pressure. Specifically, the discharge end of the second compressor 21 is equipped with a third temperature sensor and a first pressure sensor. The third temperature sensor detects the discharge temperature of the second compressor 21, and the first pressure sensor detects the discharge pressure. The saturation temperature is obtained through the discharge pressure, and the discharge superheat is calculated based on the discharge temperature of the second compressor 21 and the obtained saturation temperature.

[0160] Among the multiple fourth temperature ranges, the fifth preset opening decreases as the temperature value increases. That is, each fourth temperature range corresponds to a fifth preset opening, and the higher the temperature value of the fourth temperature range, the smaller the fifth preset opening. Optionally, the fifth preset opening corresponding to each fourth temperature range can be obtained experimentally, or it can be obtained based on experience. The second thermostatic valve 26 is located on the fourth bypass pipe 25 of the refrigeration system 100, and the fourth bypass pipe 25 connects to the exhaust end and the return end of the second compressor 21.

[0161] It should also be noted that, generally, the fourth temperature range is a range containing multiple temperature values. Of course, in some embodiments, the fourth temperature range can also be a specific temperature value. When the fourth temperature range is a range, all temperature values ​​within that range correspond to a fifth preset opening degree. When the fourth temperature range is a single temperature value, each temperature value corresponds to a fifth preset opening degree.

[0162] When operating under low-temperature conditions (such as temperatures less than or equal to 0°C), the cooling capacity required by the load end 14 for the low-temperature stage refrigeration module is less, and correspondingly, the cooling capacity of the low-temperature stage refrigeration module for the high-temperature stage refrigeration module decreases accordingly. To prevent a significant reduction in heat exchange in the evaporator-condenser of the high-temperature stage refrigeration module, resulting in excessively low return temperature for extended periods and the risk of liquid-laden operation in the second compressor 21, a judgment is made based on the exhaust superheat under low-temperature conditions. When the current exhaust superheat is less than the preset exhaust superheat, the second thermostatic valve 26 is controlled to operate at the fourth target temperature level or the corresponding fifth preset opening. That is, the second thermostatic valve 26 is controlled to operate at an appropriate opening based on the production temperature to avoid the situation where the exhaust superheat of the second compressor 21 is too low.

[0163] In some specific implementations, the preset exhaust superheat is 25°C. The fifth preset opening corresponding to different fourth temperature ranges is shown in the table below:

[0164] Current production temperature T (°C) Fifth preset opening percentage -55≤T＜-40 25 -40≤T＜-20 10 -20≤T≤0 5 0<T 0

[0165] It is conceivable that in some other implementations, the number of fourth temperature settings is not limited, nor is the fifth preset opening degree corresponding to each fourth temperature setting limited.

[0166] Another embodiment of this application provides a refrigeration system control device, including:

[0167] The acquisition module is used to acquire the current discharge temperature of the first compressor 11 of the refrigeration system 100;

[0168] The determination module is used to determine the first temperature range where the current exhaust temperature is located as the first target temperature range from a plurality of preset first temperature ranges when the current exhaust temperature is greater than or equal to the first preset exhaust temperature, and to determine the temperature range where the first target temperature range is located as the target temperature range from a plurality of preset temperature ranges; the temperature range of each temperature range includes at least one first temperature range.

[0169] The control module is used to control the return gas injection valve 16 to operate at a non-zero first preset opening degree associated with the first target temperature range, and to control the exhaust gas injection valve 18 to operate at a second preset opening degree associated with the target temperature range; the larger the temperature range, the larger the second preset opening degree associated with it.

[0170] The return gas injection valve 16 is provided on the second bypass line 15 of the refrigeration system 100 for the return gas cooling of the first compressor 11, and the exhaust gas injection valve 18 is provided on the first bypass line 17 of the refrigeration system 100 for the exhaust gas cooling of the first compressor 11.

[0171] Each module in the aforementioned refrigeration system control device can be implemented entirely or partially through software, hardware, or a combination thereof. These modules can be embedded in the processor of a computer device in hardware form or independent of it, or stored in the memory of a computer device in software form, so that the processor can call and execute the operations corresponding to each module.

[0172] The aforementioned refrigeration system control device, when the current production temperature is greater than or equal to the first preset exhaust temperature, determines the first temperature range where the current production temperature is located as the first target temperature range and the temperature range where the first target temperature range is located as the target temperature range. It then controls the return gas injection valve 16 to operate at a first preset opening degree associated with the first target temperature range and the exhaust gas injection valve 18 to operate at a second preset opening degree associated with the target temperature range. Thus, for different current exhaust temperatures, the return gas injection valve 16 and the exhaust gas injection valve 18 are controlled to operate at appropriate opening degrees to precisely adjust the refrigerant flow in real time, thereby reducing the exhaust temperature of the first compressor 11. Compared to the prior art method of reducing the exhaust temperature of the first compressor 11 by adjusting the refrigerant flow through a solenoid valve with only on / off functionality and no opening degree adjustment function, this method does not remove a significant amount of cooling capacity from the first circulation loop A, ensuring that the load end 14 can reach the target production temperature. Furthermore, by controlling the return gas injection valve 16 and the exhaust gas injection valve 18 to operate at appropriate openings for different current exhaust temperatures, the refrigerant flow can be adjusted in real time and accurately, which can prevent the current exhaust temperature from rising again, reduce the fluctuation of the current exhaust temperature, and facilitate the rapid and stable operation of the refrigeration system 100.

[0173] The technical features of the above embodiments can be combined in any way. For the sake of brevity, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0174] The embodiments described above are merely illustrative of several implementations of the present invention, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the invention patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of the present invention, and these all fall within the protection scope of the present invention. Therefore, the protection scope of this invention patent should be determined by the appended claims.

Claims

1. A method for controlling a refrigeration system, characterized in that, include: Obtain the current discharge temperature of the first compressor (11) of the refrigeration system (100); When the current exhaust temperature is greater than or equal to the first preset exhaust temperature, the first temperature range in which the current exhaust temperature is located is determined from a plurality of preset first temperature ranges as the first target temperature range, and the temperature range in which the first target temperature range is located is determined from a plurality of preset temperature ranges as the target temperature range; each temperature range contains at least one first temperature range. The return gas injection valve (16) is controlled to operate at a non-zero first preset opening degree associated with the first target temperature range, and the exhaust gas injection valve (18) is controlled to operate at a second preset opening degree associated with the target temperature range; the second preset opening degree associated with the temperature range with a larger temperature is larger. The return gas injection valve (16) is located on the second bypass line (15) of the refrigeration system (100) for the return gas cooling of the first compressor (11), and the exhaust gas injection valve (18) is located on the first bypass line (17) of the refrigeration system (100) for the exhaust gas cooling of the first compressor (11).

2. The refrigeration system control method according to claim 1, characterized in that, The temperature range that is less than the second preset exhaust temperature is the first temperature range. The first temperature range includes multiple first temperature levels. The first temperature level with a lower temperature in the first temperature range is associated with a smaller first preset opening. The second preset opening associated with the first temperature range is zero. The second preset exhaust temperature is greater than the first preset exhaust temperature.

3. The refrigeration system control method according to claim 1, characterized in that, The temperature range with a temperature range greater than or equal to the second preset exhaust temperature is the second temperature range. Each second temperature range includes a first temperature level. The smaller the temperature of the second temperature range, the smaller the non-zero second preset opening degree associated with it. The first preset opening degree associated with the first temperature level included in all the second temperature ranges is a first fixed opening degree. The second preset exhaust temperature is greater than the first preset exhaust temperature, and the first preset opening degree associated with the first temperature range that is less than the second preset exhaust temperature is less than the first fixed opening degree.

4. The refrigeration system control method according to claim 1, characterized in that, Also includes: When the current exhaust temperature is less than the third preset exhaust temperature, the return gas injection valve (16) and the exhaust gas injection valve (18) are both controlled to operate at zero opening. The third preset exhaust temperature is lower than the first preset exhaust temperature.

5. The refrigeration system control method according to claim 1, characterized in that, Controlling the return gas injection valve (16) to operate at a non-zero first preset opening degree associated with the first target temperature range, and controlling the exhaust gas injection valve (18) to operate at a second preset opening degree associated with the target temperature range, includes: The return gas injection valve (16) is operated with a non-zero first initial opening and the exhaust injection valve (18) is operated with a second initial opening. After the return gas injection valve (16) operates at the first initial opening and the exhaust injection valve (18) operates at the second initial opening for a first preset time, the return gas injection valve (16) is controlled to switch from the first initial opening to the first preset opening associated with the first target temperature range and the exhaust injection valve (18) is controlled to switch from the second initial opening to the second preset opening associated with the target temperature range.

6. The refrigeration system control method according to claim 1, characterized in that, Also includes: Obtain the current production temperature of the load terminal (14) of the refrigeration system (100); When the current production temperature is greater than the first preset production temperature but less than the second preset production temperature, the second temperature range where the current production temperature is located is determined from a plurality of preset second temperature ranges as the second target temperature range. Control the first thermostatic valve (190) to operate at a third preset opening degree associated with the second target temperature range; The higher the temperature of the second temperature range, the greater the associated third preset opening degree; The first thermostatic valve (190) is located on the third bypass pipe (180) of the refrigeration system (100), and the third bypass pipe (180) is connected to the inlet end of the load end (14) and the exhaust end of the first compressor (11).

7. The refrigeration system control method according to claim 6, characterized in that, Also includes: When the current production temperature is greater than or equal to the second preset production temperature, the opening degree of the first thermostatic valve (190) is controlled to be zero.

8. The refrigeration system control method according to any one of claims 1-7, characterized in that, Also includes: When the current exhaust temperature is less than or equal to the fourth preset exhaust temperature, the third temperature range where the current exhaust temperature is located is determined from a plurality of preset third temperature ranges as the third target temperature range. The first thermostatic valve (190) is controlled to operate at a non-zero fourth preset opening degree associated with the third target temperature range; The fourth preset exhaust temperature is lower than the first preset exhaust temperature, and the fourth preset opening degree associated with the third temperature range is smaller as the temperature increases. The first thermostatic valve (190) is located on the third bypass pipe (180) of the refrigeration system (100), and the third bypass pipe (180) is connected to the inlet end of the load end (14) and the exhaust end of the first compressor (11).

9. The refrigeration system control method according to any one of claims 1-7, characterized in that, Also includes: Obtain the current production temperature of the load end (14) of the refrigeration system (100) and the current discharge superheat of the second compressor (21); When the current exhaust superheat is less than the preset exhaust superheat, the fourth temperature range associated with the current exhaust superheat is determined from a plurality of preset fourth temperature ranges as the fourth target temperature range. Control the second thermostatic valve (26) to operate at the fifth preset opening degree associated with the fourth target temperature range; The higher the temperature of the fourth temperature setting, the smaller the associated fifth preset opening. The second thermostatic valve (26) is located on the fourth bypass pipe (25) of the refrigeration system (100), and the fourth bypass pipe (25) is connected to the exhaust end and the return end of the second compressor (21).

10. A refrigeration system control device, characterized in that, include: The acquisition module is used to acquire the current discharge temperature of the first compressor (11) of the refrigeration system (100); The determining module is configured to, when the current exhaust temperature is greater than or equal to a first preset exhaust temperature, determine the first temperature range in which the current exhaust temperature is located as a first target temperature range from a plurality of preset first temperature ranges, and determine the temperature range in which the first target temperature range is located as a target temperature range from a plurality of preset temperature ranges; each temperature range contains at least one first temperature range. The control module is used to control the return gas injection valve (16) to operate at a non-zero first preset opening degree associated with the first target temperature range, and to control the exhaust injection valve (18) to operate at a second preset opening degree associated with the target temperature range; the second preset opening degree associated with the temperature range with a larger temperature is larger. The return gas injection valve (16) is located on the second bypass line (15) of the refrigeration system (100) for the return gas cooling of the first compressor (11), and the exhaust gas injection valve (18) is located on the first bypass line (17) of the refrigeration system (100) for the exhaust gas cooling of the first compressor (11).

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