Refrigeration system

Abstract

The utility model relates to a refrigeration system. The refrigerating system comprises a first refrigerating module. The first refrigerating module comprises a first compressor, a first condenser, a first throttling valve, a second throttling valve and a heat exchanger. The first compressor, the first condenser, the first throttling valve and the heat exchanger are sequentially communicated to form a first closed loop, the first compressor, the first condenser, the second throttling valve and the heat exchanger are sequentially communicated to form a second closed loop, and the adjusting calibers of the first throttling valve and the second throttling valve are different. According to the refrigerating system, the temperature control precision can be improved, and the temperature control range can be widened.

Description

Technical Field

[0001] This application relates to the field of temperature control technology, specifically to a refrigeration system. Background Technology

[0002] Two-stage compression cascade refrigeration systems are commonly found in various refrigeration systems. These systems consist of a high-temperature stage refrigeration module and a low-temperature stage refrigeration module, with the low-temperature stage module ultimately providing the intermediate or low-temperature refrigerant. The refrigerant supplied by the low-temperature stage module exchanges heat with the electronic components through a heat exchanger, maintaining the components at the target intermediate or low temperature to facilitate testing.

[0003] Refrigeration systems typically have two operating modes: high temperature and low temperature. To ensure the test results, when the refrigeration system is running in high temperature mode and low temperature mode, it is necessary to keep the outlet liquid temperature and evaporation temperature of the refrigerant entering the heat exchanger constant within different temperature ranges.

[0004] In traditional technology, to ensure that the outlet liquid temperature of the refrigeration system remains constant within a certain temperature range in high-temperature mode, a bypass branch is drawn from the discharge end of the low-temperature compressor. This bypass branch mixes with the low-temperature liquid refrigerant that has been throttled and cooled by the expansion valve. The outlet liquid temperature (i.e., the temperature of the refrigerant before it enters the heat exchanger in high-temperature mode) is controlled by adjusting the mixing ratio of the two refrigerants. However, because the high-temperature gaseous refrigerant in the bypass branch often experiences temperature fluctuations, the temperature control accuracy is not up to standard. When it mixes with the throttled low-temperature liquid refrigerant, the outlet liquid temperature becomes difficult to control, ultimately resulting in a significant deviation in the outlet liquid temperature.

[0005] Furthermore, when the refrigeration system operates in low-temperature mode, the evaporation temperature (i.e., the temperature of the refrigerant before it enters the heat exchanger in low-temperature mode) fluctuates significantly below -68°C, resulting in low temperature control accuracy. Because of this low temperature control accuracy, the selection of temperature control parameters in low-temperature mode is limited, leading to a narrower temperature control range. Utility Model Content

[0006] Therefore, it is necessary to provide a refrigeration system that can improve temperature control accuracy and broaden the temperature control range to address the above problems.

[0007] A refrigeration system, the refrigeration system including a first refrigeration module, the first refrigeration module including a first compressor, a first condenser, a first throttle valve, a second throttle valve and a heat exchanger;

[0008] The first compressor, the first condenser, the first throttle valve, and the heat exchanger are sequentially connected to form a first closed loop, and the first compressor, the first condenser, the second throttle valve, and the heat exchanger are sequentially connected to form a second closed loop. The first throttle valve and the second throttle valve have different adjustment diameters.

[0009] In some embodiments, the first refrigeration module further includes a first bypass pipe, a first control valve, a first pipeline, a second pipeline, and a refrigerant mixer;

[0010] One end of the first bypass pipe is connected to the first closed loop between the first compressor and the first condenser, and the other end of the first bypass pipe is connected to one of the inlets of the refrigerant mixer. The first control valve is disposed on the first bypass pipe.

[0011] The first pipeline, as part of the second closed loop, is connected between the second throttle valve and another inlet of the refrigerant mixer, and the second pipeline, as part of the second closed loop, is connected between the outlet of the refrigerant mixer and the heat exchanger;

[0012] The regulating diameter of the second throttle valve is smaller than that of the first throttle valve.

[0013] In some embodiments, the first refrigeration module further includes a second bypass pipe and a second control valve;

[0014] One end of the second bypass pipe is connected to the first closed loop between the first throttling valve and the heat exchanger, and the other end of the second bypass pipe intersects and connects with the first bypass pipe. The intersection point of the second bypass pipe and the first bypass pipe is located downstream of the first control valve, and the second control valve is disposed on the second bypass pipe.

[0015] In some embodiments, the first refrigeration module further includes a third control valve, which is disposed on the first bypass pipe and located downstream of the junction of the second bypass pipe and the first bypass pipe.

[0016] In some embodiments, the first cooling module further includes a first temperature sensor;

[0017] The first temperature sensor is used to detect the refrigerant temperature at the first position, and the first control valve or the first throttle valve is configured to adjust the opening degree according to the refrigerant temperature at the first position until the refrigerant temperature at the first position is within the closed interval of the first temperature threshold and the second temperature threshold.

[0018] The first position is located between the intersection of the second bypass pipe and the first bypass pipe and the third control valve.

[0019] In some embodiments, the first cooling module further includes a second temperature sensor;

[0020] The second temperature sensor is used to detect the refrigerant temperature at the second position, and the second throttle valve is configured to adjust its opening according to the refrigerant temperature at the second position until the refrigerant temperature at the first position is within the closed interval of the first temperature threshold and the second temperature threshold, and the refrigerant temperature at the first position is greater than the sum of the refrigerant temperature at the second position and 5°C.

[0021] The second position is located between the outlet of the refrigerant mixer and the heat exchanger.

[0022] In some embodiments, the first refrigeration module further includes a fourth control valve and a third pipeline, wherein the third pipeline is connected between the first throttling valve and the heat exchanger as part of the first closed loop, and the fourth control valve is disposed on the third pipeline;

[0023] One end of the second bypass pipe intersects and connects with the third pipe, and the intersection of the second bypass pipe and the third pipe is located upstream of the fourth control valve.

[0024] In some embodiments, the first refrigeration module further includes an oil separator located on the first closed loop and the second closed loop, and the oil separator has a first port, a second port and a third port, the first port being connected to the exhaust end of the first compressor, the second port being connected to the first condenser, and the third port being connected to the oil return port of the first compressor.

[0025] In some embodiments, the refrigeration system further includes at least one second refrigeration module, each second refrigeration module including a second compressor, a second condenser, a third throttle valve and an evaporator, the second compressor, the second condenser, the third throttle valve and the evaporator being sequentially connected to form a third closed loop; the second condenser and the evaporator of two adjacent second refrigeration modules are integrated into one unit to form a first evaporator-condenser;

[0026] The first condenser of the first refrigeration module and the evaporator of the second refrigeration module with the lowest temperature level are integrated into one unit to form a second evaporator-condenser.

[0027] In some embodiments, the refrigeration system further includes a cooling mechanism for cooling the second condenser of the second refrigeration module at the highest temperature level.

[0028] Compared with the prior art, this application has the following beneficial effects:

[0029] The aforementioned refrigeration system, by setting throttle valves with different regulating diameters, can fully utilize the accuracy of throttle valves with different regulating diameters to achieve the purpose of widening the temperature control range and improving accuracy. Attached Figure Description

[0030] Figure 1 This is a schematic diagram of a refrigeration system provided in one embodiment of this application;

[0031] Figure 2 This is a schematic diagram of a refrigeration system provided in another embodiment of this application.

[0032] Icon labels:

[0033] 1. Refrigeration system;

[0034] 10. First refrigeration module; 30. Second refrigeration module;

[0035] 11. First compressor; 12. Oil separator; 13. First condenser; 14. First throttle valve; 15. Fourth control valve; 16. Third pipeline; 17. Second temperature sensor; 18. Heat exchanger; 19. Second throttle valve; 21. First pipeline; 22. Refrigerant mixer; 23. Second pipeline; 24. First bypass pipe; 25. First control valve; 26. Second bypass pipe; 27. Second control valve; 28. First temperature sensor; 29. ​​Third control valve; 31. Second compressor; 32. Second condenser; 33. Third throttle valve; 34. Evaporator. Detailed Implementation

[0036] To make the above-mentioned objectives, features, and advantages of this application more apparent and understandable, the specific embodiments of this application are 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 this application. However, this application can be implemented 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 this application. Therefore, this application is not limited to the specific embodiments disclosed below.

[0037] In the description of this application, 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", "circumferential", etc., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application 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, and therefore should not be construed as a limitation of this application.

[0038] 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 application, "multiple" means at least two, such as two, three, etc., unless otherwise explicitly specified.

[0039] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "joining," 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 expressly limited. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0040] In this application, unless otherwise expressly 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," "on top of," and "over" 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.

[0041] 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.

[0042] See Figure 1 One embodiment of this application provides a cooling system 1 for controlling the temperature of an electronic component. Specifically, the electronic component is a chip, and the cooling system 1 is used to control the temperature of the chip. Of course, in other embodiments, the type of electronic component used for temperature control in the cooling system 1 is not limited.

[0043] The refrigeration system 1 includes a first refrigeration module 10, which includes a first compressor 11, a first condenser 13, a first throttle valve 14, a second throttle valve 19, and a heat exchanger 18. The first compressor 11, the first condenser 13, the first throttle valve 14, and the heat exchanger 18 are sequentially connected to form a first closed loop, and the first compressor 11, the first condenser 13, the second throttle valve 19, and the heat exchanger 18 are sequentially connected to form a second closed loop. The first throttle valve 14 and the second throttle valve 19 have different adjustment diameters.

[0044] Heat exchanger 18 is heat exchanger 18. Heat exchanger 18 exchanges heat with electronic components to keep the electronic components at the target medium temperature or target low temperature, so as to facilitate the testing of electronic components.

[0045] Specifically, both the first throttle valve 14 and the second throttle valve 19 are electronic expansion valves, and the opening degree of the first throttle valve 14 and the second throttle valve 19 is adjustable.

[0046] When the first closed loop starts, the first compressor 11 draws in the high-temperature, low-pressure gaseous refrigerant output from the heat exchanger 18, compresses it into a high-temperature, high-pressure gaseous refrigerant, and discharges it from the exhaust end of the first compressor 11 to the first condenser 13. As the refrigerant passes through the first condenser 13, it is condensed into a medium-temperature, high-pressure liquid refrigerant, and then expands and depressurizes through the first throttle valve 14 into a low-temperature, low-pressure liquid refrigerant, which is finally reintroduced into the heat exchanger 18 from its input end. When the low-temperature, low-pressure liquid refrigerant enters the heat exchanger 18, it can exchange heat with the electronic components, thereby controlling the temperature of the electronic components. After heat exchange, the refrigerant re-enters the first compressor 11 from the output end of the heat exchanger 18, and this cycle repeats. The specific circulation path of the refrigerant in the first closed loop is: a→b→c→d→e.

[0047] The working principle of the second closed loop is the same as that of the first closed loop, so it will not be repeated here. The specific circulation path of the refrigerant in the second closed loop is: a→b→f→g→h→e.

[0048] It is worth mentioning that the first closed loop and the second closed loop operate selectively. When the first closed loop is activated, the second closed loop is closed. At this time, the first throttle valve 14 is open and the second throttle valve 19 is closed. When the second closed loop is activated, the first closed loop is closed. At this time, the first throttle valve 14 is closed and the second throttle valve 19 is open.

[0049] Furthermore, in this embodiment, when the first closed loop is operating, the temperature of the refrigerant before it exits through the first throttling valve 14 and enters the heat exchanger 18 is the evaporation temperature. When the second closed loop is operating, the temperature of the refrigerant before it exits through the second throttling valve 19 and enters the heat exchanger 18 is the evaporation temperature. The first throttling valve 14 and the second throttling valve 19 have different adjustment orifices. The adjustment orifice of the throttling valve refers to the opening diameter through which the refrigerant flows. Different adjustment orifices result in different levels of adjustment precision. Generally speaking, within a suitable adjustment orifice range, the smaller the orifice, the higher the sensitivity of the throttling valve, and thus the higher the precision of refrigerant flow regulation and the more precise the temperature control of the evaporation temperature.

[0050] As an example, the regulating diameter of the second throttle valve 19 can be smaller than that of the first throttle valve 14, so that the temperature control accuracy of the second closed loop is higher than that of the first closed loop.

[0051] In this embodiment, the temperature control accuracy of the refrigerant evaporation temperature in the first closed loop is relatively low. The first closed loop can be set to operate in a first low-temperature mode, with the temperature control range for the evaporation temperature within the range of (-68℃, -50℃). Conversely, the temperature control accuracy of the refrigerant evaporation temperature in the second closed loop is relatively high. The second closed loop can be set to operate in a second low-temperature mode, with the temperature control range for the evaporation temperature within the range of [-75℃, -68℃].

[0052] Specifically, because the regulating diameter of the second throttle valve 19 is smaller than that of the first throttle valve 14, the second throttle valve 19 controls the refrigerant flow more accurately. Therefore, when the refrigeration system 1 is in the second low-temperature mode, selecting an evaporating temperature lower than that in the first low-temperature mode reduces the probability of unstable evaporating temperature control and greatly improves the temperature control accuracy of the refrigeration system 1. Furthermore, due to the improved temperature control accuracy, a lower evaporating temperature can be selected when standardizing the parameters for the temperature control range, thus widening the temperature control range.

[0053] As can be seen from the above, in this application, by setting throttle valves with different regulating diameters, the accuracy of throttle valves with different regulating diameters can be fully utilized to achieve the purpose of widening the temperature control range and accuracy.

[0054] Of course, the size of the regulating orifice of the first throttle valve 14 and the second throttle valve 19 is not limited to the above one. In some other embodiments, the regulating orifice of the second throttle valve 19 can also be set to be larger than the regulating orifice of the first throttle valve 14.

[0055] In some embodiments, the first refrigeration module 10 further includes a first bypass pipe 24, a first control valve 25, a first pipeline 21, a second pipeline 23, and a refrigerant mixer 22. One end of the first bypass pipe 24 is connected to a first closed loop between the first compressor 11 and the first condenser 13, and the other end of the first bypass pipe 24 is connected to one inlet of the refrigerant mixer 22. The first control valve 25 is disposed on the first bypass pipe 24. The first pipeline 21, as part of a second closed loop, is connected between the second throttle valve 19 and the other inlet of the refrigerant mixer 22. The second pipeline 23, as part of a second closed loop, is connected between the outlet of the refrigerant mixer 22 and the heat exchanger 18. The regulating diameter of the second throttle valve 19 is smaller than the regulating diameter of the first throttle valve 14.

[0056] Specifically, the first control valve 25 is an electronic expansion valve, and its opening degree is adjustable.

[0057] The refrigeration system 1 also has a high-temperature mode. When the refrigeration system 1 operates in high-temperature mode, both the first throttle valve 14 and the first control valve 25 are open. The high-temperature, high-pressure gaseous refrigerant discharged from the exhaust end of the first compressor 11 is divided into two paths. One path enters the refrigerant mixer 22 through the first control valve 25 and the first bypass pipe 24 (the specific flow path of the refrigerant is: a→j→k→m). The other path is condensed by the first condenser 13 and throttled by the second throttle valve 19 to form a low-temperature, low-pressure liquid refrigerant, which flows into the refrigerant mixer 22 through the first pipe 21 (the specific flow path of the refrigerant is: a→b→f→g). The two refrigerants with different temperatures and phases mix to form a high-temperature mixed refrigerant, the temperature of which is the outlet liquid temperature. Afterward, the mixed refrigerant enters the heat exchanger 18 through the second pipe 23, exchanges heat with the electronic components, and then returns to the first compressor 11 to complete the cycle (the specific flow path of the refrigerant is: h→e).

[0058] By configuring the first bypass pipe 24, the first control valve 25, the first pipeline 21, the second pipeline 23, and the refrigerant mixer 22, the refrigeration system 1 also features a high-temperature mode, thus expanding its temperature regulation range. Furthermore, by adjusting the opening of the first control valve 25 and / or the second throttle valve 19, the mixing ratio of the two refrigerants entering the refrigerant mixer 22 can be differentiated, thereby achieving the purpose of regulating the outlet liquid temperature.

[0059] Preferably, since the regulating diameter of the second throttle valve 19 is small, the mixing ratio of the two refrigerants entering the refrigerant mixer 22 can be adjusted by adjusting the opening of the second throttle valve 19 alone. The outlet temperature of the mixed refrigerant fluctuates less and is easier to control, thus improving the temperature control accuracy of the outlet temperature.

[0060] Furthermore, in some embodiments, the first refrigeration module 10 further includes a second bypass pipe 26 and a second control valve 27. One end of the second bypass pipe 26 is connected to the first closed loop between the first throttle valve 14 and the heat exchanger 18, and the other end of the second bypass pipe 26 intersects and connects with the first bypass pipe 24. The intersection point of the second bypass pipe 26 and the first bypass pipe 24 is located downstream of the first control valve 25, and the second control valve 27 is disposed on the second bypass pipe 26.

[0061] In this embodiment, when the refrigeration system 1 operates in high-temperature mode, the first throttle valve 14 and the second control valve 27 are also opened. The high-temperature, high-pressure gaseous refrigerant discharged from the exhaust end of the first compressor 11 is divided into three paths. The first path serves as a hot gas bypass, passing through the first control valve 25 and the first bypass pipe 24. The second path, after being condensed by the first condenser 13, is throttled by the first throttle valve 14 to form a low-temperature, low-pressure liquid refrigerant, which then flows from the second bypass pipe 26 into the first bypass pipe 24 (the refrigerant flow...). The specific flow path is: a→b→c→n→p), which mixes with the high-temperature, high-pressure gaseous refrigerant passing through the first control valve 25 to form a mixed-liquid refrigerant. This mixed refrigerant then flows through the first bypass pipe 24 into the refrigerant mixer 22. The third refrigerant then sequentially passes through the first condenser 13 for condensation and the second throttling valve 19 for throttling, forming a low-temperature, low-pressure liquid refrigerant. This liquid refrigerant flows through the first pipe 21 into the refrigerant mixer 22, where it mixes thoroughly with the aforementioned mixed-liquid refrigerant to form the final mixed refrigerant. Afterward, the mixed refrigerant enters the heat exchanger 18 through the second pipe 23, exchanges heat with the electronic components, and then returns to the first compressor 11 to complete the cycle.

[0062] In this application, the refrigerant needs to be mixed twice. The first mixing forms a liquid refrigerant, and the second mixing forms a mixed refrigerant. The temperature of the mixed refrigerant formed after the second mixing is the outlet temperature.

[0063] Specifically, the second control valve 27 is a solenoid valve, which only has the function of opening and closing, and does not have the function of adjusting the opening degree.

[0064] By setting a second bypass pipe 26 and a second control valve 27, which work in conjunction with the first bypass pipe 24, the first pipeline 21, the second pipeline 23, the first control valve 25, and the refrigerant mixer 22, the refrigerant can be mixed twice, making the outlet temperature control more flexible and the temperature control range wider.

[0065] In this embodiment, by adjusting the opening degree of at least one of the first throttle valve 14, the second throttle valve 19, and the first control valve 25, the mixing ratio of the two refrigerants entering the refrigerant mixer 22 can be adjusted, thereby achieving the purpose of regulating the outlet liquid temperature. After adjustment, the temperature control range of the outlet liquid temperature of the mixed refrigerant is within the temperature range of [-39℃, 0℃].

[0066] Preferably, the mixing ratio of the two refrigerants forming the mixed refrigerant is adjusted by adjusting the opening of the first control valve 25, and the mixing ratio of the two refrigerants forming the mixed refrigerant is adjusted by adjusting the opening of the second throttle valve 19. Because the regulating orifice of the second throttle valve 19 is small, adjusting the opening of the second throttle valve 19 to adjust the mixing ratio of the two refrigerants forming the mixed refrigerant results in smaller fluctuations in the outlet temperature of the mixed refrigerant, making it easier to control and improving the accuracy of outlet temperature control.

[0067] Furthermore, in some embodiments, the first refrigeration module 10 further includes a third control valve 29, which is disposed on the first bypass pipe 24 and located downstream of the junction of the second bypass pipe 26 and the first bypass pipe 24.

[0068] Specifically, the third control valve 29 is a solenoid valve, which only has opening and closing functions and does not have opening degree adjustment functions.

[0069] By configuring the third control valve 29, when the refrigeration system 1 is in high-temperature mode, the third control valve 29 opens, ensuring that the mixed refrigerant flows into the refrigerant mixer 22 and mixes with the refrigerant flowing in from the first pipe 21. When the refrigeration system 1 is in the first low-temperature mode or the second low-temperature mode, the third control valve 29 closes, ensuring that the refrigerant does not enter the refrigerant mixer 22 through the first bypass pipe 24 and the second bypass pipe 26. In summary, the design of the third control valve 29 improves the reliability of refrigerant switching in the refrigeration system 1.

[0070] In some embodiments, the first refrigeration module 10 further includes a first temperature sensor 28. The first temperature sensor 28 is used to detect the refrigerant temperature at a first position, and the first control valve 25 or the first throttle valve 14 is configured to adjust its opening according to the refrigerant temperature at the first position until the refrigerant temperature at the first position is within a closed interval of a first temperature threshold and a second temperature threshold; the first position is located between the junction of the second bypass pipe 26 and the first bypass pipe 24 and the third control valve 29.

[0071] Specifically, the temperature of the mixed refrigerant is set as T1, the first temperature threshold is T2, the second temperature threshold is T3, and T1 is within the temperature range of [T2, T3].

[0072] In this embodiment, when the refrigeration system 1 is running in high-temperature mode, the temperature of the mixed refrigerant formed in the first bypass pipe 24 is read on the first temperature sensor 28. Based on the temperature read by the first temperature sensor 28, the opening of the first control valve 25 or the first throttle valve 14 is adjusted until the temperature of the mixed refrigerant is within the temperature range of [T2, T3].

[0073] By designing the first temperature sensor 28, the opening degree of the first control valve 25 or the first throttle valve 14 can be controlled according to the temperature read by the first temperature sensor 28, so as to facilitate the adjustment of the temperature of the mixed refrigerant.

[0074] In some embodiments, the refrigeration system 1 includes a controller. The first temperature sensor 28, the first control valve 25, and the first throttle valve 14 are all electrically connected to the controller. The temperature read by the first temperature sensor 28 is fed back to the controller. The controller controls the first control valve 25 or the first throttle valve 14 to adjust the temperature of the mixed refrigerant according to the temperature fed back by the first temperature sensor 28. This method is simple, convenient, and reliable.

[0075] In some embodiments, the first refrigeration module 10 further includes a second temperature sensor 17. The second temperature sensor 17 is used to detect the refrigerant temperature at a second position. The second throttle valve 19 is configured to adjust its opening according to the refrigerant temperature at the second position until the refrigerant temperature at the first position is within a closed interval between a first temperature threshold and a second temperature threshold, and the refrigerant temperature at the first position is greater than the sum of the refrigerant temperature at the second position and 5°C. The second position is located between the outlet of the refrigerant mixer 22 and the heat exchanger 18.

[0076] In this embodiment, when the refrigeration system 1 operates in high-temperature mode, the mixed refrigerant formed by the refrigerant mixer 22 is output and read from the second temperature sensor 17. Based on the temperature read by the second temperature sensor 17, the opening of the second throttle valve 19 is adjusted until the temperature of the mixed refrigerant is greater than the sum of the temperature of the mixed refrigerant and 5°C. The temperature of the mixed refrigerant is set to T, i.e., until T1 > T + 5°C.

[0077] By designing a second temperature sensor 17, the opening of the second throttle valve 19 can be controlled based on the temperature read by the second temperature sensor 17, thus facilitating the adjustment of the mixed refrigerant temperature. Furthermore, in this embodiment, the opening of the second throttle valve 19 is adjusted until the outlet temperature T is near the mixed refrigerant temperature, specifically, T1 > T + 5°C. Because the second throttle valve 19 provides more precise regulation of the refrigerant flow, this second fine adjustment will result in more stable and accurate outlet temperature control. Therefore, this method improves the temperature control accuracy of the outlet temperature in high-temperature mode.

[0078] In some embodiments, both the second throttle valve 19 and the second temperature sensor 17 are electrically connected to the controller. The temperature read by the second temperature sensor 17 is fed back to the controller, and the controller controls the second throttle valve 19 to adjust the temperature of the mixed refrigerant based on the temperature feedback from the second temperature sensor 17. Adjusting the temperature of the mixed refrigerant by controlling the second throttle valve 19 through the controller is a simple, convenient, and reliable method.

[0079] In some embodiments, the first refrigeration module 10 further includes a fourth control valve 15 and a third pipeline 16. The third pipeline 16 is connected between the first throttle valve 14 and the heat exchanger 18 as part of a first closed loop, and the fourth control valve 15 is disposed on the third pipeline 16. One end of the second bypass pipe 26 intersects and connects with the third pipeline 16, and the junction of the second bypass pipe 26 and the third pipeline 16 is located upstream of the fourth control valve 15.

[0080] Specifically, the fourth control valve 15 is a solenoid valve, which only has the function of opening and closing, and does not have the function of adjusting the opening degree.

[0081] In this embodiment, when the refrigeration system 1 is operating in the first low-temperature mode, the fourth control valve 15 is opened to allow the refrigerant to circulate within the first closed loop. When the refrigeration system 1 is operating in the second low-temperature mode or the high-temperature mode, the fourth control valve 15 is closed to prevent the refrigerant from flowing within the first closed loop, thereby improving the reliability of the refrigeration system 1.

[0082] In some embodiments, the first refrigeration module 10 further includes an oil separator 12, which is located on the first closed loop and the second closed loop. The oil separator 12 has a first port, a second port, and a third port. The first port is connected to the discharge end of the first compressor 11, the second port is connected to the first condenser 13, and the third port is connected to the oil return port of the first compressor 11. The oil separator 12 can separate the lubricating oil in the high-temperature, high-pressure gaseous refrigerant discharged from the first compressor 11 to ensure the safe and efficient operation of the refrigeration system 1.

[0083] Please refer to the following: Figure 1 and Figure 2 In some embodiments, the refrigeration system 1 further includes at least one second refrigeration module 30. Each second refrigeration module 30 includes a second compressor 31, a second condenser 32, a third throttle valve 33, and an evaporator 34. The second compressor 31, the second condenser 32, the third throttle valve 33, and the evaporator 34 are sequentially connected to form a third closed loop. The second condenser 32 and the evaporator 34 of two adjacent second refrigeration modules 30 are integrated into one to form a first evaporative condenser. The first condenser 13 of the first refrigeration module 10 and the evaporator 34 of the lowest temperature stage second refrigeration module 30 are integrated into one to form a second evaporative condenser.

[0084] In this design, the first condenser 13 of the first refrigeration module 10 and the evaporator 34 of the lowest-temperature stage second refrigeration module 30 are integrated into a single unit to form a second evaporative condenser. That is, the first condenser 13 of the first refrigeration module 10 serves as the evaporator 34 of the lowest-temperature stage second refrigeration module 30. The first refrigeration module 10 and the second refrigeration module 30 are thermally coupled through the second evaporative condenser formed by the integration of the first condenser 13 and the evaporator 34 of the lowest-temperature stage second refrigeration module 30. In other words, all the second refrigeration modules 30 collectively function as a cooling device for the first refrigeration module 10, cooling the refrigerant flowing in the first condenser 13 of the first refrigeration module 10.

[0085] It should be noted that the term "lowest temperature level second refrigeration module 30" refers to the second refrigeration module 30 that is at the lowest temperature level among all the second refrigeration modules 30.

[0086] When the second refrigeration module 30 is operating, the second compressor 31 draws in the high-temperature, low-pressure gaseous refrigerant output from the evaporator 34 and compresses it into a high-temperature, high-pressure gaseous refrigerant, which is then discharged from the exhaust end of the second compressor 31 to the second condenser 32. As the refrigerant passes through the second condenser 32, it is condensed into a medium-temperature, high-pressure liquid refrigerant, and then expands and depressurizes through the third throttle valve 33 into a low-temperature, low-pressure liquid refrigerant, which is finally reintroduced into the evaporator 34 from its input end. When the low-temperature, low-pressure liquid refrigerant enters the evaporator 34, it can exchange heat with the low-temperature stage of the second refrigeration module 30 or with the first refrigeration module 10. After heat exchange, the refrigerant re-enters the second compressor 31 from the output end of the evaporator 34, and this cycle repeats continuously. Specifically, the refrigerant circulation path in the second refrigeration module 30 is: q→r→s→t.

[0087] In some embodiments, the refrigeration system 1 includes a first-stage second refrigeration module 30, thus forming a two-stage compression cascade refrigeration system 1. Of course, in other embodiments, the number of second refrigeration modules 30 included in the refrigeration system 1 is not limited. Alternatively, in still other embodiments, the second refrigeration module 30 may be omitted from the refrigeration system 1.

[0088] In some embodiments, the refrigeration system 1 further includes a cooling mechanism for cooling the second condenser 32 of the second refrigeration module 30 at the highest temperature level, so as to dissipate heat from the second refrigeration module 30.

[0089] It should be noted that the term "highest temperature level second refrigeration module 30" refers to the second refrigeration module 30 that is at the highest temperature level among all the second refrigeration modules 30.

[0090] The working principle of the refrigeration system 1 in one embodiment is as follows:

[0091] When the refrigeration system 1 is in the first low-temperature mode, the first throttle valve 14 and the fourth control valve 15 are both open, while the second throttle valve 19, the first control valve 25, the second control valve 27, and the third control valve 29 are all closed. The refrigerant circulates through the first compressor 11, the first condenser 13, the first throttle valve 14, the first control valve 25, and the heat exchanger 18.

[0092] When the refrigeration system 1 is in the second low-temperature mode, the second throttle valve 19 is open, and the first throttle valve 14, the first control valve 25, the second control valve 27, the third control valve 29, and the fourth control valve 15 are all closed. The refrigerant circulates through the first compressor 11, the first condenser 13, the second throttle valve 19, and the heat exchanger 18.

[0093] When the refrigeration system 1 is in high-temperature mode, the first throttle valve 14, the second throttle valve 19, the first control valve 25, the second control valve 27 and the third control valve 29 are all open, the fourth control valve 15 is closed, and the opening degree of the second throttle valve 19 is fixed. The refrigerant output from the first compressor 11 is divided into three streams. The first stream, acting as a hot gas bypass, passes through the first control valve 25 and the first bypass pipe 24. The second stream, after being condensed by the first condenser 13, is throttled by the first throttle valve 14 to form a low-temperature, low-pressure liquid refrigerant, which then flows through the second bypass pipe 26 into the first bypass pipe 24. There, it mixes with the high-temperature, high-pressure gaseous refrigerant passing through the first control valve 25 to form a mixed-liquid refrigerant, which then flows through the first bypass pipe 24 into the refrigerant mixer 22. The third stream of refrigerant is condensed by the first condenser 13 and throttled by the second throttle valve 19 to form a low-temperature, low-pressure liquid refrigerant, which flows through the first pipe 21 into the refrigerant mixer 22. There, it mixes thoroughly with the aforementioned mixed-liquid refrigerant to form the final mixed refrigerant. Afterward, the mixed refrigerant enters the heat exchanger 18 through the second pipe 23, exchanges heat with the electronic components, and then returns to the first compressor 11 to complete the cycle.

[0094] 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.

[0095] The embodiments described above are merely illustrative of several implementation methods of this application, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the patent application. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this application, and these all fall within the protection scope of this application. Therefore, the protection scope of this patent application should be determined by the appended claims.

Claims

1. A refrigeration system characterized by, The refrigeration system comprises a first refrigeration module (10), the first refrigeration module (10) comprising a first compressor (11), a first condenser (13), a first throttle valve (14), a second throttle valve (19) and a heat exchanger (18); The first compressor (11), the first condenser (13), the first throttle valve (14) and the heat exchanger (18) are sequentially communicated to form a first closed loop, the first compressor (11), the first condenser (13), the second throttle valve (19) and the heat exchanger (18) are sequentially communicated to form a second closed loop, and the regulating diameters of the first throttle valve (14) and the second throttle valve (19) are different.

2. The refrigeration system of claim 1, wherein, The first refrigeration module (10) further comprises a first bypass pipe (24), a first control valve (25), a first pipe (21), a second pipe (23) and a refrigerant mixer (22); One end of the first bypass pipe (24) is communicated on the first closed loop between the first compressor (11) and the first condenser (13), the other end of the first bypass pipe (24) is communicated with one inlet of the refrigerant mixer (22), and the first control valve (25) is arranged on the first bypass pipe (24); The first pipe (21) is communicated between the second throttle valve (19) and the other inlet of the refrigerant mixer (22) as part of the second closed loop, and the second pipe (23) is communicated between the outlet of the refrigerant mixer (22) and the heat exchanger (18) as part of the second closed loop; The regulating diameter of the second throttle valve (19) is smaller than the regulating diameter of the first throttle valve (14).

3. The refrigeration system of claim 2, wherein, The first refrigeration module (10) further comprises a second bypass pipe (26) and a second control valve (27); One end of the second bypass pipe (26) is communicated on the first closed loop between the first throttle valve (14) and the heat exchanger (18), the other end of the second bypass pipe (26) intersects with the first bypass pipe (24) and is communicated, and the intersection point of the second bypass pipe (26) and the first bypass pipe (24) is located downstream of the first control valve (25), and the second control valve (27) is arranged on the second bypass pipe (26).

4. The refrigeration system of claim 3, wherein, The first refrigeration module (10) further comprises a third control valve (29), the third control valve (29) is arranged on the first bypass pipe (24) and located downstream of the intersection point of the second bypass pipe (26) and the first bypass pipe (24).

5. The refrigeration system of claim 4, wherein, The first refrigeration module (10) further comprises a first temperature sensor (28); The first temperature sensor (28) is used for detecting the refrigerant temperature at a first position, and the first control valve (25) or the first throttle valve (14) is configured to adjust the opening degree according to the refrigerant temperature at the first position until the refrigerant temperature at the first position is within a closed interval of a first temperature threshold and a second temperature threshold; The first position is located between the intersection of the second bypass pipe (26) and the first bypass pipe (24) and the third control valve (29).

6. The refrigeration system of claim 5, wherein, The first refrigeration module (10) further comprises a second temperature sensor (17); The second temperature sensor (17) is configured to detect the refrigerant temperature at a second position, and the second throttling valve (19) is configured to adjust the opening degree according to the refrigerant temperature at the second position, until the refrigerant temperature at the first position is within the closed interval of the first temperature threshold and the second temperature threshold, and the refrigerant temperature at the first position is greater than the sum of the refrigerant temperature at the second position and 5℃. The second position is located between the outlet of the refrigerant mixer (22) and the heat exchanger (18).

7. The refrigeration system of claim 3 wherein, The first refrigeration module (10) further comprises a fourth control valve (15) and a third pipeline (16), the third pipeline (16) is connected between the first throttling valve (14) and the heat exchanger (18) as part of the first closed loop, and the fourth control valve (15) is arranged on the third pipeline (16). One end of the second bypass pipe (26) intersects and communicates with the third pipeline (16), and the intersection of the second bypass pipe (26) and the third pipeline (16) is located upstream of the fourth control valve (15).

8. The refrigeration system of claim 1, wherein, The first refrigeration module (10) further comprises an oil separator (12), the oil separator (12) is located on the first closed loop and the second closed loop, and the oil separator (12) has a first port, a second port and a third port, the first port communicates with the exhaust end of the first compressor (11), the second port communicates with the first condenser (13), and the third port communicates with the oil return port of the first compressor (11).

9. The refrigeration system of any of claims 1-8, wherein, The refrigeration system further comprises at least one second refrigeration module (30), each second refrigeration module (30) comprises a second compressor (31), a second condenser (32), a third throttling valve (33) and an evaporator (34), the second compressor (31), the second condenser (32), the third throttling valve (33) and the evaporator (34) are sequentially connected to form a third closed loop; the second condenser (32) and the evaporator (34) of adjacent two second refrigeration modules (30) are integrated to form a first evaporative condenser; The first condenser (13) of the first refrigeration module (10) and the evaporator (34) of the second refrigeration module (30) at the lowest temperature level are integrated to form a second evaporative condenser.

10. The refrigeration system of claim 9, wherein, The refrigeration system further comprises a cooling mechanism for cooling the second condenser (32) of the second refrigeration module (30) at the highest temperature level.

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