Liquid cooling system and control method thereof, electronic device

Abstract

The application discloses a liquid cooling system and a control method thereof and electronic equipment, and relates to the technical field of heat dissipation. The liquid cooling system comprises a circulating pipeline, a pump, an evaporation assembly, a condenser, a detection assembly, a liquid storage unit and a control unit. The circulating pipeline is used for flowing of a liquid cooling medium. The evaporation assembly comprises at least one evaporator in contact with a heat source. The control unit is in communication connection with the pump, the detection assembly and the liquid storage unit respectively. The detection assembly is used for detecting a performance parameter of the liquid cooling medium and a temperature of the heat source. The outlet of the pump is in communication with the inlet of the evaporator through the circulating pipeline. The outlet of the evaporator is in communication with the inlet of the condenser through the circulating pipeline. The outlet of the condenser is in communication with the inlet of the liquid storage unit through the circulating pipeline. The outlet of the liquid storage unit is in communication with the inlet of the pump through the circulating pipeline. The liquid cooling medium comprises at least two working substances with a boiling point difference of no less than 10 DEG C. The liquid cooling system effectively reduces a heat transfer temperature difference, realizes accurate matching of multiple heat source temperatures, and improves heat dissipation efficiency.

Description

Technical Field

[0001] This invention relates to the field of heat dissipation technology, and in particular to a liquid cooling system and its control method, as well as electronic devices using the liquid cooling system. Background Technology

[0002] With the rapid development of artificial intelligence, high-performance computing, and data centers, the heat flux density of high-performance chips, represented by CPUs and GPUs, has exceeded the limits of traditional air cooling. Liquid cooling technology has become an inevitable choice for solving the problem of high heat flux density. Among various liquid cooling technologies, pump-driven two-phase liquid cooling systems, which utilize the latent heat of the working fluid for heat transfer, have extremely high heat transfer coefficients and excellent temperature uniformity, and are considered the most promising next-generation heat dissipation solution.

[0003] In related technologies, current mainstream two-phase liquid cooling systems typically use a single pure working fluid, such as R134a or water. Under constant system pressure, the phase change process of the pure working fluid is isothermal. However, the heat source temperature continuously increases from the working fluid inlet to the outlet (temperature rise can reach 10°C~30°C), while the pure working fluid maintains a constant temperature for evaporation within the evaporator. This necessitates maintaining a large heat transfer temperature difference at the outlet to meet heat dissipation demands, resulting in significant heat loss and limiting the system's coefficient of performance (COP) to a low level. Simultaneously, the power consumption and surface temperature of heat sources within the server, such as the CPU, GPU, and memory, vary. The fixed boiling point of a single working fluid cannot simultaneously match multiple heat sources with different temperatures, causing some heat sources to fail to undergo phase change heat transfer at their optimal temperature. Furthermore, dynamic changes in system load, ambient temperature fluctuations, and pressure drops during flow all alter local pressure, thereby changing the local saturation temperature of the single working fluid. This can easily lead to the working fluid failing to undergo phase change at certain locations within the system, resulting in heat dissipation failure and impacting heat dissipation efficiency. Summary of the Invention

[0004] The main objective of this invention is to provide a liquid cooling system and its control method and electronic equipment, aiming to solve the problems of uneven temperature matching, low energy efficiency, and poor adaptability caused by the use of a single pure working fluid. The liquid cooling system of this invention overcomes the disadvantage of isothermal phase change process of pure working fluid under constant system pressure, and can better adapt to the characteristic of continuous temperature increase of heat source from working fluid inlet to outlet, effectively reducing the heat transfer temperature difference at the outlet end, significantly improving the system energy efficiency (COP) level, and breaking through the energy efficiency limitations of traditional systems. At the same time, it effectively solves the problem of different power consumption and surface temperatures of heat sources such as CPU, GPU, and memory in servers. Through flexible adjustment of working fluid component concentration, it achieves precise temperature matching of multiple heat sources, ensuring that each heat source can undergo phase change heat transfer at the optimal temperature point, and comprehensively improving heat dissipation efficiency.

[0005] To achieve the above objectives, the present invention proposes a liquid cooling system, which includes a circulation pipeline, a pump, an evaporation assembly, a condenser, a detection assembly, a liquid storage unit, and a control unit. The circulation pipeline is used to supply liquid cooling medium for flow. The evaporation assembly includes at least one evaporator for contact with a heat source. The control unit is communicatively connected to the pump, the detection assembly, and the liquid storage unit. The detection assembly is used to detect the performance parameters of the liquid cooling medium and the temperature of the heat source. The outlet of the pump is connected to the inlet of the evaporator through the circulation pipeline, the outlet of the evaporator is connected to the inlet of the condenser through the circulation pipeline, the outlet of the condenser is connected to the inlet of the liquid storage unit through the circulation pipeline, and the outlet of the liquid storage unit is connected to the inlet of the pump through the circulation pipeline. The liquid cooling medium includes at least two working fluids with a boiling point difference of not less than 10°C.

[0006] In one embodiment, the liquid cooling medium includes at least one first working medium and at least one second working medium, wherein the first working medium is a low-boiling-point working medium and the second working medium is a high-boiling-point working medium; The first working medium includes one or more of R32, R1234yf, R1234ze(E), and R290, and the second working medium includes one or more of R245fa, R1233zd(E), R1336mzz(Z), R600a, water, ethanol, and fluorinated liquid. And / or, the boiling point difference between the first working fluid and the second working fluid is 20℃-50℃; And / or, the mass ratio of the first working fluid to the second working fluid is 1:5 to 5:1; And / or, the temperature slip between the first working fluid and the second working fluid is 3℃~15℃.

[0007] In one embodiment, the evaporator includes a top cover, a biomimetic liquid distribution structure, and an evaporation phase change structure. The top cover and the evaporation phase change structure enclose a cavity. The biomimetic liquid distribution structure is disposed between the top cover and the evaporation phase change structure, so that the top cover, the biomimetic liquid distribution structure, and the evaporation phase change structure enclose a liquid inlet channel, a gas outlet channel, and a biomimetic liquid distribution zone and an evaporation phase change zone located and interconnected between the liquid inlet channel and the gas outlet channel. The liquid inlet channel is connected to the biomimetic liquid distribution zone, and the gas outlet channel is connected to the evaporation phase change zone. The top cover is provided with a liquid inlet that connects to the liquid inlet channel and an air outlet that connects to the air outlet channel. The liquid inlet forms the inlet of the evaporator, and the air outlet forms the outlet of the evaporator.

[0008] In one embodiment, the evaporation phase change structure includes a base plate and a plurality of partitions, wherein the plurality of partitions are spaced apart on the base plate and arranged at intervals along the center of the base plate toward the edge of the base plate to form a first central region and a plurality of annular regions surrounding the first central region on the base plate. The biomimetic liquid distribution structure includes a central component and multiple branch components. The central component forms a second central region, which is connected to the first central region to form the liquid inlet channel. The multiple branch components are distributed at intervals along the outer periphery of the central component, and one end of each branch component is connected to the central component. The other end of each branch component extends toward the edge of the base plate. Each branch component has a branch region that is connected to the second central region. In this configuration, each branch region is connected to multiple annular regions to form the biomimetic liquid separation zone, extending from the center of the base plate to its edge. Multiple annular regions located between two adjacent branch members cooperate with the two adjacent branch members to form the evaporation phase change zone. The top cover, together with the outermost partition and the end of the multiple branch members furthest from the center member, forms the gas outlet channel.

[0009] In one embodiment, the liquid inlet, the second central region, and the first central region are all located at the center of the evaporator and are arranged sequentially along the thickness direction of the evaporator. And / or, the top cover includes a top plate and a side plate disposed around the periphery of the top plate, the top plate being opposite to and spaced from the bottom plate, the side plate extending toward the bottom plate and connected to the bottom plate, the top plate being provided with the liquid inlet, and the side plate being provided with the air outlet; And / or, the plurality of said branch components and the central component are integrally formed; And / or, the hydraulic diameter D of each branch region near the end of the central member 中心 The thickness ranges from 0.1mm to 5mm. And / or, the hydraulic diameter D of each branch region at the end furthest from the central member 边缘 The thickness ranges from 0.5mm to 10mm. And / or, from the center of the base plate to the edge of the base plate, the cross-sectional dimension of each branch region gradually increases, and the hydraulic diameter increase rate γ of each branch region is 0.02~1; where γ=(D 边缘 -D 中心 ) / R, where R is the radius of the biomimetic liquid separation zone; And / or, the inner wall of each of the branch regions is provided with a hydrophobic layer; wherein the contact angle of the hydrophobic layer is >120°; And / or, the inner walls of the first central region and the plurality of annular regions are provided with a hydrophilic layer; wherein the contact angle of the hydrophilic layer is <30°.

[0010] In one embodiment, the inner walls of the first central region and the plurality of annular regions are provided with a first recess structure, the first recess structure being an array structure formed by the first recesses; wherein, the diameter of the first recess is 5μm~50μm, the depth of the first recess is 2μm~20μm, and the spacing between the first recesses is 10μm~100μm; and / or, from the center of the base plate to the edge of the base plate, the density of the first recesses gradually increases; and / or, from the center of the base plate to the edge of the base plate, the diameter of the first recesses gradually decreases. Alternatively, the inner walls of the first central region and the plurality of annular regions are provided with a porous structure, wherein the porous structure is an array structure formed by micropores; wherein the pore size of the micropores is 50nm~500nm; and / or, the porosity of the micropores is 30%~70%; and / or, the density of the micropores gradually increases from the center of the base plate to the edge of the base plate; and / or, the diameter of the micropores gradually decreases from the center of the base plate to the edge of the base plate.

[0011] In one embodiment, along the flow direction of the liquid cooling medium, the condenser has at least two heat exchange sections, the at least two heat exchange sections including a first heat exchange section located on the inlet side of the condenser and a second heat exchange section located on the outlet side of the condenser. A first condensation channel is formed in the first heat exchange section, and the first heat exchange section is provided with a plurality of first fins. A second condensation channel is formed in the second heat exchange section, and the second heat exchange section is provided with a plurality of second fins. The first condensation channel is configured as a variable cross-section microchannel, and the hydraulic diameter of the first condensation channel gradually decreases along the flow direction of the liquid cooling medium. And / or, the density of the plurality of first fins gradually decreases along the flow direction of the liquid cooling medium; And / or, the inner wall of the first condensation channel is provided with a second pit structure, the second pit structure being an array structure formed by the second pits; wherein, the diameter of the second pit is 10μm~50μm, the depth of the second pit is 5μm~20μm, and the spacing between the second pits is 20μm~100μm. And / or, the second condensation channel is configured as a microchannel with an equal cross-section.

[0012] In one embodiment, the detection component includes: Multiple temperature and pressure sensors are installed in the circulation pipeline, located respectively at the inlet side of the evaporator, the outlet side of the evaporator, and the outlet side of the condenser, for detecting the temperature and pressure of the liquid cooling medium. The multiple temperature and pressure sensors are communicatively connected to the control unit. A void fraction sensor is installed in the circulation pipeline and located at the outlet side of the evaporator or the inlet side of the condenser. It is used to detect the void fraction of the liquid cooling medium and is communicatively connected to the control unit.

[0013] In one embodiment, the cavitation fraction sensor is a dielectric constant sensor, a capacitance tomography sensor, or an ultrasonic sensor. And / or, the detection component further includes a flow sensor, which is disposed in the circulation pipeline and located at the outlet side of the pump, for detecting the flow rate of the liquid cooling medium in the circulation pipeline, and the flow sensor is communicatively connected to the control unit; And / or, the detection component further includes a plurality of temperature sensors disposed on the surface of the heat source, the plurality of temperature sensors being arranged in an array along the flow direction of the liquid cooling medium for detecting the temperature of the surface of the heat source, and the plurality of temperature sensors being communicatively connected to the control unit.

[0014] In one embodiment, the liquid storage unit has a gas phase separation chamber and a liquid phase separation chamber. The gas phase separation chamber is connected to the inlet of the condenser through a first pipeline, and the liquid phase separation chamber is connected to the inlet of the pump through the circulation pipeline. The liquid phase separation chamber is used to separate different working fluids. The liquid phase separation chamber includes multiple liquid phase chambers, the number of which corresponds one-to-one with the amount of the working fluid of the liquid cooling medium. Each liquid phase chamber is connected to the circulation pipeline through a second pipeline. The liquid storage unit also includes a flow control valve located in each of the second pipelines, and the flow control valve is communicatively connected to the control unit. And / or, the liquid storage unit further includes a one-way valve disposed in the first pipeline.

[0015] In one embodiment, the evaporation assembly includes a plurality of evaporators for contact with the heat source, the plurality of evaporators being arranged in parallel, the outlet of the pump being connected to the inlet of the plurality of evaporators via the circulation pipeline, and the outlet of the plurality of evaporators being connected to the inlet of the condenser via the circulation pipeline; And / or, the performance parameters of the liquid cooling medium include temperature, pressure, and cavitation fraction; And / or, the control unit adopts a two-layer control architecture, the control unit includes a bottom-layer controller and an upper-layer optimizer, the bottom-layer controller controls the pump working fluid according to the performance parameters detected by the detection component, and the upper-layer optimizer dynamically calculates the target working fluid component concentration of the liquid cooling medium according to the temperature of the heat source and the performance of the liquid cooling medium, and transmits it to the bottom-layer controller.

[0016] The present invention also proposes a control method for the above-described liquid cooling system, the control method comprising: The temperature, pressure, and empty shot fraction of the current liquid cooling medium are acquired in real time by the detection component, and the real-time working fluid component concentration C_r of the liquid cooling medium is calculated based on the temperature, pressure, and empty shot fraction. The temperature of the heat source is acquired in real time by the detection component, and the target working fluid component concentration C_t of the liquid cooling medium is calculated based on the temperature of the heat source and the thermodynamic property data of the liquid cooling medium. Based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, the flow control valve is controlled to adjust the flow rate of different working fluids, thereby adjusting the real-time component concentration of the liquid medium in the circulation pipeline.

[0017] In one embodiment, the step of acquiring the temperature of the heat source collected in real time by the detection component, and calculating the target working fluid component concentration C_t of the liquid cooling medium based on the temperature of the heat source and the thermodynamic property data of the liquid cooling medium includes: Acquire the temperature of the heat source in real time from the detection component; The surface temperature distribution curve T_h(x,t) of the heat source is generated based on the temperature of the heat source. Based on the surface temperature distribution curve T_h(x,t) of the heat source, and combined with the preset system energy efficiency optimization target, the ideal target working fluid phase change temperature glide curve T_gt(p,x,t) is calculated; where p is the system pressure, x is the spatial coordinate along the flow direction of the evaporator, and t is time; Based on the temperature glide curve T_gt(p,x,t), combined with the current system pressure p and the preset thermodynamic properties of the liquid cooling medium, the target working fluid component concentration C_t of the liquid cooling medium required to reach the temperature glide curve T_gt(p,x,t) is calculated in reverse.

[0018] In one embodiment, the step of controlling the flow control valve to adjust the flow rate of different working fluids based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, so as to adjust the real-time component concentration of the liquid medium in the circulation pipeline, includes: Determine whether the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium exceeds a preset threshold. If so, the flow control valve is used to adjust the flow rate of different working fluids in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline; If not, cycle according to the current working fluid composition concentration of the liquid cooling medium.

[0019] The present invention also proposes an electronic device comprising the liquid cooling system described above.

[0020] The liquid cooling system of this invention connects a pump, evaporation assembly, condenser, and liquid storage unit sequentially through a circulation pipeline to form a circulation path. The circulation pipeline provides a flow path for the liquid cooling medium, and the pump provides driving force for the liquid cooling medium within the circulation pipeline. This drives the liquid cooling medium output from the liquid storage unit to the evaporator in the evaporation assembly, where it contacts the heat source. In the evaporator, the liquid cooling medium exchanges heat with the heat source to form a gaseous liquid cooling medium, which is then output from the evaporator to the condenser for cooling, reverting to liquid form before returning to the liquid storage unit for the next cooling cycle. This pump ensures continuous flow of the liquid cooling medium within the system, avoiding flow stagnation caused by uneven temperature, thereby improving the system's stability and reliability. Furthermore, by using a non-azeotropic mixture of at least two working fluids with a boiling point difference of not less than 10°C as the liquid cooling medium, it can… This system overcomes the isothermal limitation of a single pure working fluid during phase change under constant system pressure, enabling it to better adapt to the continuous increase in heat source temperature from the working fluid inlet to the outlet. This effectively reduces the heat transfer temperature difference at the outlet, significantly improving the system's coefficient of performance (COP) and breaking through the energy efficiency limitations of traditional systems. Furthermore, the use of a non-azeotropic mixed working fluid allows the system to undergo phase change at different temperatures, effectively solving the problem of varying power consumption and surface temperatures of heat sources such as CPUs, GPUs, and memory within servers. Further, by setting up detection components and control units, the detection components monitor the performance parameters of the liquid cooling medium and the temperature of the heat sources. The control units are communicatively connected to the pump, detection components, and storage unit, respectively. This allows for flexible adjustment of the working fluid component concentration, precise matching of multiple heat source temperatures, and ensures that each heat source can undergo phase change heat transfer at its optimal temperature, comprehensively improving heat dissipation efficiency. Attached Figure Description

[0021] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on the structures shown in these drawings without creative effort.

[0022] Figure 1 This is a schematic diagram of a structure of an embodiment of the liquid cooling system provided by the present invention; Figure 2 This is a schematic diagram of the structure of an embodiment of the evaporator provided by the present invention; Figure 3 This is a cross-sectional schematic diagram of an embodiment of the evaporator provided by the present invention; Figure 4 A cross-sectional schematic diagram from another perspective in one embodiment of the evaporator provided by the present invention; Figure 5 This is an exploded view of an embodiment of the evaporator provided by the present invention; Figure 6 A top view of an embodiment of the evaporator provided by the present invention with the top cover removed; Figure 7 A partially enlarged cross-sectional schematic diagram of an embodiment of the evaporation phase change structure provided by the present invention; Figure 8 A partially enlarged cross-sectional schematic diagram of another embodiment of the evaporation phase change structure provided by the present invention; Figure 9 A schematic diagram of the connection structure between the control unit, the detection component, the pump, and the flow control valve in one embodiment of the liquid cooling system provided by the present invention.

[0023] Explanation of icon numbers: 100. Liquid cooling system; 1. Circulation pipeline; 2. Pump; 3. Evaporation assembly; 31. Evaporator; 311. Top cover; 3111. Top plate; 3112. Liquid inlet; 3113. Side plate; 3114. Gas outlet; 312. Bionic liquid distribution structure; 3121. Central component; 3122. Second central region; 3123. Branch component; 3124. Branch region; 313. Evaporation phase change structure; 3131. Bottom plate; 3132. Partition; 3133. First central region; 3134. Annular region; 3135. First recess structure; 3136. First recess; 3137. Porous structure; 3138. 314. Micropores; 315. Liquid inlet channel; 316. Gas outlet channel; 317. Bionic liquid separation zone; 318. Evaporation phase change zone; 4. Condenser; 41. First heat exchange section; 42. Second heat exchange section; 5. Detection components; 51. Temperature and pressure sensor; 52. Cavity fraction sensor; 53. Flow sensor; 54. Temperature sensor; 6. Liquid storage unit; 61. Gas phase separation chamber; 62. Liquid phase separation chamber; 621. Liquid phase chamber; 63. First pipeline; 64. Second pipeline; 65. Flow control valve; 66. Check valve; 7. Control unit; 71. Bottom layer controller; 72. Upper layer optimizer; 73. Prediction module.

[0024] The realization of the objective, functional features and advantages of the present invention will be further explained in conjunction with the embodiments and with reference to the accompanying drawings. Detailed Implementation

[0025] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present invention.

[0026] It should be noted that all directional indications (such as up, down, left, right, front, back, etc.) in the embodiments of the present invention are only used to explain the relative positional relationship and movement of each component in a certain specific posture (as shown in the figure). If the specific posture changes, the directional indication will also change accordingly.

[0027] Meanwhile, the meaning of "and / or" or "and / or" appearing throughout the text is that it includes three options. Taking "A and / or B" as an example, it includes option A, option B, or an option that satisfies both A and B.

[0028] Furthermore, in this invention, descriptions involving "first," "second," etc., are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of that feature. Additionally, the technical solutions of the various embodiments can be combined with each other, but only on the basis of being achievable by those skilled in the art. When the combination of technical solutions is contradictory or impossible to implement, such a combination of technical solutions should be considered non-existent and not within the scope of protection claimed by this invention.

[0029] This invention proposes a liquid cooling system 100, which is applied to electronic devices containing electrical components such as CPUs and GPUs, whose thermal design power exceeds kilowatt levels. The CPUs and GPUs in the electronic devices act as heat sources and are mounted in contact with the evaporator 31 of the evaporation assembly 3 of the liquid cooling system 100. Heat exchange is achieved through the phase change principle of the liquid cooling medium in the liquid cooling system 100 absorbing heat and evaporating in the evaporator 31 of the evaporation assembly 3, and then condensing in the condenser 4, thereby dissipating heat from the CPUs and GPUs.

[0030] Please refer to the reference. Figures 1 to 9As shown, in this embodiment of the invention, the liquid cooling system 100 includes a circulation pipeline 1, a pump 2, an evaporation assembly 3, a condenser 4, a detection assembly 5, a liquid storage unit 6, and a control unit 7. The circulation pipeline 1 is used to supply the liquid cooling medium. The evaporation assembly 3 includes at least one evaporator 31 for contact with a heat source. The control unit 7 is communicatively connected to the pump 2, the detection assembly 5, and the liquid storage unit 6. The detection assembly 5 is used to detect the performance parameters of the liquid cooling medium and the temperature of the heat source. The outlet of the pump 2 is connected to the inlet of the evaporator 31 through the circulation pipeline 1. The outlet of the evaporator 31 is connected to the inlet of the condenser 4 through the circulation pipeline 1. The outlet of the condenser 4 is connected to the inlet of the liquid storage unit 6 through the circulation pipeline 1. The outlet of the liquid storage unit 6 is connected to the inlet of the pump 2 through the circulation pipeline 1. The liquid cooling medium includes at least two working fluids with a boiling point difference of not less than 10°C.

[0031] In this embodiment, the circulation pipeline 1 provides a flow path for the liquid cooling medium. The circulation pipeline 1 can be a pipe or flow channel, etc., with a channel or cavity structure for containing the liquid cooling medium. It is understood that the circulation pipeline 1 can be a metal pipe or a plastic pipe, etc., and is not limited here.

[0032] Understandably, the pump 2, evaporator 3, condenser 4, and liquid storage unit 6 are sequentially connected through circulation pipe 1 to form a closed loop. That is, the outlet of pump 2 is connected to the inlet of evaporator 31 through circulation pipe 1, the outlet of evaporator 31 is connected to the inlet of condenser 4 through circulation pipe 1, the outlet of condenser 4 is connected to the inlet of liquid storage unit 6 through circulation pipe 1, and the outlet of liquid storage unit 6 is connected to the inlet of pump 2 through circulation pipe 1, so that the liquid cooling medium can circulate in the closed loop.

[0033] In this embodiment, pump 2 provides driving force for the liquid cooling medium in the closed-loop circuit, enabling the liquid cooling medium to flow continuously within the closed-loop circuit. This avoids flow stagnation caused by uneven temperature, thereby improving the stability and reliability of the liquid cooling system 100. It is understood that the inlet and outlet of pump 2 are connected to the liquid storage unit 6 and the evaporator 31-condenser 4, respectively. This allows the liquid cooling medium output from the liquid storage unit 6 to be transported to the evaporator 31, and the gaseous liquid cooling medium output from the evaporator 31 to be transported to the condenser 4.

[0034] Understandably, pump 2 is a circulating pump, which can be a centrifugal pump. Optionally, the centrifugal pump model is XA65 / 16, with a flow rate of 16 kg / h and a head of 65 meters; or, the centrifugal pump model is XA80 / 20, with a flow rate of 20 kg / h and a head of 80 meters, without any specific limitation.

[0035] In this embodiment, the evaporation assembly 3 is in contact with the heat source of the electronic device. That is, the evaporation assembly 3 includes at least one evaporator 31 for contact with the heat source. The liquid cooling medium undergoes heat exchange as it flows through the evaporator 31, thereby cooling and dissipating heat from the heat source. It is understood that the pump 2 drives the liquid cooling medium to the evaporator 31. The liquid cooling medium receives heat from the heat source within the evaporator 31, undergoes heat exchange, absorbs heat, and evaporates to form a gaseous liquid cooling medium. The gaseous liquid cooling medium is then transported from the evaporator 31 to the condenser 4 for cooling and condensation to form a liquid cooling medium, and finally returns to the storage unit 6 for the next cycle.

[0036] Understandably, the evaporator 31 can be a circular structure. Of course, the evaporator 31 can also be square or other shapes, depending on the shape and contour of the heat source, and is not limited here. In this embodiment, the condenser 4 can be a plate condenser. The condenser 4 adopts a multi-stage condensing plate design, and the inlet and outlet of the condenser 4 are provided with independent flow channels to prevent backflow of the liquefied liquid cooling medium or the liquid cooling medium entrained in the gaseous cooling medium.

[0037] Optionally, the length of the condenser 4 is 150mm or 180mm, the width of the condenser 4 is 100mm or 120mm, and the multi-stage condenser plate is designed to have 5 stages with a spacing of 25mm between each stage, which is not limited here.

[0038] It should be noted that existing liquid cooling systems typically use a single pure working fluid, such as R134a or water. Under constant system pressure, the phase change process of the pure working fluid is isothermal. However, the heat source temperature continuously increases from the working fluid inlet to the outlet (temperature rise can reach 10°C~30°C), while the pure working fluid maintains a constant temperature for evaporation within the evaporator. This necessitates maintaining a large heat transfer temperature difference at the outlet to meet heat dissipation demands, resulting in significant heat loss and limiting the system's coefficient of performance (COP) to a low level. Furthermore, the power consumption and surface temperature of heat sources within a server, such as the CPU, GPU, and memory, vary. The fixed boiling point of a single working fluid cannot simultaneously match multiple heat sources with different temperatures, causing some heat sources to fail to undergo phase change heat transfer at their optimal temperature. In addition, dynamic changes in system load, fluctuations in ambient temperature, and pressure drops during flow all alter local pressure, thereby changing the local saturation temperature of the single working fluid. This can easily lead to the working fluid failing to undergo phase change at certain locations within the system, resulting in heat dissipation failure and impacting cooling efficiency.

[0039] The liquid cooling system 100 of the present invention connects the pump 2, the evaporation assembly 3, the condenser 4, and the liquid storage unit 6 in sequence through the circulation pipeline 1 to form the circulation flow path of the liquid cooling system 100. The circulation pipeline 1 provides a flow path for the liquid cooling medium, and the pump 2 provides driving force for the liquid cooling medium in the circulation pipeline 1 to transport the liquid cooling medium output from the liquid storage unit 6 to the evaporator 31 in the evaporation assembly 3, which is in contact with the heat source. After exchanging heat with the heat source in the evaporator 31, the liquid cooling medium forms a gaseous liquid cooling medium, which is then output from the evaporator 31 to the condenser 4 for cooling and then returns to the liquid storage unit 6 for the next cooling cycle. In this way, the pump 2 ensures the continuous flow of the liquid cooling medium in the liquid cooling system 100, avoids the flow stagnation caused by uneven temperature, and thus improves the stability and reliability of the system.

[0040] Meanwhile, by setting the liquid cooling medium as a non-azeotropic mixture of at least two working fluids with a boiling point difference of not less than 10°C, the shortcomings of the isothermal phase change process of a single pure working fluid under constant system pressure can be overcome. This allows the liquid cooling system 100 to better adapt to the characteristic of the heat source temperature continuously rising from the inlet to the outlet of the liquid cooling medium, effectively reducing the heat transfer temperature difference at the outlet end, significantly improving the system energy efficiency (COP) level, breaking through the energy efficiency limitations of traditional systems, and the use of the non-azeotropic mixture allows the liquid cooling system 100 to undergo phase change at different temperatures, effectively solving the problem of different power consumption and surface temperatures of heat sources such as CPU, GPU, and memory in the server.

[0041] In this embodiment, as Figure 1 and Figure 9 As shown, by setting up a detection component 5 and a control unit 7, the detection component 5 detects the performance parameters of the liquid cooling medium and the temperature of the heat source, and the control unit 7 is communicatively connected to the pump 2, the detection component 5, and the liquid storage unit 6. This enables flexible adjustment of the working fluid component concentration, precise matching of multiple heat source temperatures, and ensures that each heat source can undergo phase change heat transfer at its optimal temperature, thereby comprehensively improving heat dissipation efficiency. Optionally, the performance parameters of the liquid cooling medium include temperature, pressure, and cavitation fraction.

[0042] It should be noted that the control unit 7 can be a control system, a control circuit, or a control program integrated on a circuit board, etc., and is not limited here. The control unit 7 can communicate with the pump 2, the detection component 5, and the liquid storage unit 6 via a wired connection, that is, to achieve signal transmission. Of course, the control unit 7 can also communicate with the pump 2, the detection component 5, and the liquid storage unit 6 via a wireless connection, as per existing technology, and is not limited here.

[0043] In one embodiment, the liquid cooling medium includes at least one first working medium and at least one second working medium, wherein the first working medium is a low-boiling-point working medium and the second working medium is a high-boiling-point working medium.

[0044] In this embodiment, by setting the liquid cooling medium as a mixed working medium composed of at least one first working substance and at least one second working substance, with the first working substance being a low-boiling-point working substance and the second working substance being a high-boiling-point working substance, the mixed working medium is made into a non-azeotropic mixture. This overcomes the disadvantage of isothermal phase change processes of a single pure working substance under constant system pressure, allowing the liquid cooling system 100 to better adapt to the characteristic of the heat source temperature continuously increasing from the inlet to the outlet of the liquid cooling medium, effectively reducing the heat transfer temperature difference at the outlet end, significantly improving the system energy efficiency (COP) level, breaking through the energy efficiency limitations of traditional systems. Furthermore, the use of a non-azeotropic mixture allows the liquid cooling system 100 to undergo phase change at different temperatures, effectively solving the problem of varying power consumption and surface temperatures of heat sources such as CPU, GPU, and memory within the server. The liquid cooling system 100 of the present invention solves the problems of uneven temperature matching, low energy efficiency, and poor adaptability caused by the use of a single pure working substance in existing two-phase liquid cooling systems.

[0045] Optionally, the first working medium includes one or more of R32, R1234yf, R1234ze(E), and R290, and the second working medium includes one or more of R245fa, R1233zd(E), R1336mzz(Z), R600a, water, ethanol, and fluorinated liquid.

[0046] In this embodiment, the first working fluid is a low-boiling-point working fluid, which can be one or more of R32, R1234yf, R1234ze(E), and R290. It is understood that R32 is difluoromethane refrigerant with a boiling point of -52°C; R1234yf is a single-component HFO (hydrofluoroolefin) refrigerant (2,3,3,3-tetrafluoropropylene) with a boiling point of -29°C; R1234ze is a new type of environmentally friendly refrigerant belonging to the HFO (hydrofluoroolefin) class (trans-1,3,3,3-tetrafluoropropylene) with a boiling point of -19°C; and R290 is propane refrigerant (propane) with a boiling point of -42°C.

[0047] In this embodiment, the second working fluid is a high-boiling-point working fluid, which can be one or more of R245fa, R1233zd(E), R1336mzz(Z), R600a, water, ethanol, and fluorinated liquid. It is understood that R245fa is an environmentally friendly HFC refrigerant (1,1,1,3,3-pentafluoropropane) with a boiling point of 15°C; R1233zd(E) is an HFO (hydrofluoroolefin) refrigerant (trans-1-chloro-3,3,3-trifluoropropene) with a boiling point of 18°C; R1336mzz(Z) is an HFO (hydrofluoroolefin) refrigerant (cis-1,1,1,4,4,4-hexafluoro-2-butene) with a boiling point of 33°C; and R600a is an isobutane refrigerant (isobutane) with a boiling point of -12°C.

[0048] Understandably, water, ethanol, and fluorinated liquid are conventional working fluids. Water has a boiling point of 100℃; ethanol has a boiling point of 78℃. Optionally, the fluorinated liquid can be FC-72 (boiling point 56℃); FC-770 (boiling point 95℃); Novec7000 (boiling point 34℃); Novec7100 (boiling point 61℃); Novec7200 (boiling point 76℃); Novec7300 (boiling point 98℃), but this is not limited to these specific types.

[0049] In this embodiment, the boiling point difference between the first working medium and the second working medium in the liquid cooling medium is not less than 10°C. Optionally, the boiling point difference between the first working medium and the second working medium in the liquid cooling medium is 20°C to 50°C. It is understood that the boiling point difference between the first working medium and the second working medium can be 20°C, 23°C, 25°C, 28°C, 30°C, 33°C, 35°C, 38°C, 40°C, 43°C, 45°C, 48°C, 50°C, etc., and is not limited here.

[0050] Understandably, this setup overcomes the isothermal drawback of a single pure working fluid undergoing phase change under constant system pressure. This allows the liquid cooling system 100 to better adapt to the characteristic of the heat source temperature continuously increasing from the inlet to the outlet of the liquid cooling medium, effectively reducing the heat transfer temperature difference at the outlet, significantly improving the system's coefficient of performance (COP), breaking through the energy efficiency limitations of traditional systems. Furthermore, the use of a non-azeotropic mixed working fluid enables the liquid cooling system 100 to undergo phase change at different temperatures, effectively solving the problem of varying power consumption and surface temperatures of heat sources such as CPU, GPU, and memory within the server. This addresses the issues of uneven temperature matching, low energy efficiency, and poor adaptability caused by the use of a single pure working fluid in existing two-phase liquid cooling systems.

[0051] Optionally, the mass ratio of the first working fluid to the second working fluid in the liquid cooling medium is 1:5 to 5:1. In this embodiment, the mass ratio of the first working fluid to the second working fluid is 0.2 to 5. Optionally, the mass ratio of the first working fluid to the second working fluid can be 0.2, 0.5, 1, 1.5, 2, 2.5, 3, 3.5, 4, 4.5, 5, etc., and is not limited here. It is understood that a mass ratio of the first working fluid to the second working fluid in the liquid cooling medium within the range of 1:5 to 5:1 can effectively ensure the performance of the liquid cooling medium, thereby meeting the heat dissipation requirements under different operating conditions.

[0052] Optionally, the temperature glide value between the first and second working fluids in the liquid cooling medium is 3℃ to 15℃. In this embodiment, the temperature glide value is defined as the difference between the dew point temperature T_dew and the bubble point temperature T_bubble. By keeping the temperature glide value ΔT of the liquid cooling medium between 3℃ and 15℃ under the rated operating pressure of the liquid cooling system, the liquid cooling medium achieves precise temperature matching of multiple heat sources, ensuring that each heat source can undergo phase change heat transfer at the optimal temperature point, thus comprehensively improving heat dissipation efficiency.

[0053] In one embodiment, the first working medium in the non-azeotropic mixture of liquid cooling medium is R1234ze(E), and the second working medium is R245fa. The mass ratio of the first working medium to the second working medium is 3:7. The boiling point difference between the first working medium and the second working medium is greater than 30°C. Under the rated operating pressure of 2.0 MPa of the system, the temperature slip ΔT between the first working medium and the second working medium is 10°C, which is between 3°C and 15°C.

[0054] In another embodiment, the first working medium in the non-azeotropic mixture of liquid cooling medium is R32, the second working medium is fluorinated liquid, the mass ratio of the first working medium to the second working medium is 1:1, the boiling point difference between the first working medium and the second working medium is greater than 30°C, and the temperature glide value ΔT is 8°C under the rated working pressure of 3.0 MPa, which is between 3°C and 15°C.

[0055] In one embodiment, the evaporator 31 includes a top cover 311, a biomimetic liquid distribution structure 312, and an evaporation phase change structure 313. The top cover 311 and the evaporation phase change structure 313 enclose a cavity. The biomimetic liquid distribution structure 312 is disposed between the top cover 311 and the evaporation phase change structure 313, so that the top cover 311, the biomimetic liquid distribution structure 312, and the evaporation phase change structure 313 enclose a liquid inlet channel 314 and a gas outlet channel 315 located within the cavity. The biomimetic liquid separation zone 316 and the evaporation phase change zone 317 are connected to and interconnected with the air outlet channel 315. The liquid inlet channel 314 is connected to the biomimetic liquid separation zone 316, and the air outlet channel 315 is connected to the evaporation phase change zone 317. The top cover 311 is provided with a liquid inlet 3112 connected to the liquid inlet channel 314 and an air outlet 3114 connected to the air outlet channel 315. The liquid inlet 3112 forms the inlet of the evaporator 31, and the air outlet 3114 forms the outlet of the evaporator 31.

[0056] In this embodiment, as Figures 2 to 6 As shown, by configuring the evaporator 31 as a top cover 311, a biomimetic liquid distribution structure 312, and an evaporation phase change structure 313, the top cover 311 and the evaporation phase change structure 313 enclose a cavity, and the biomimetic liquid distribution structure 312 is disposed between the top cover 311 and the evaporation phase change structure 313. The top cover 311, the biomimetic liquid distribution structure 312, and the evaporation phase change structure 313 of the evaporator 31 enclose a liquid inlet channel 314, an air outlet channel 315, and an air outlet channel 315 located within the cavity. The biomimetic liquid separation zone 316 and the evaporation phase change zone 317 are connected between the liquid inlet channel 314 and the gas outlet channel 315. The top cover 311 is provided with a liquid inlet 3112 connected to the liquid inlet channel 314 and a gas outlet 3114 connected to the gas outlet channel 315. In this way, the evaporation phase change structure 313 of the evaporator 31 is thermally coupled to the heat source on the side facing away from the top cover 311. The liquid inlet 3112 is used for the inflow of liquid cooling medium, and the gas outlet 3114 is used for the outflow of gaseous or two-phase liquid cooling medium.

[0057] Understandably, the liquid cooling medium flows in from the inlet 3112 and enters the biomimetic liquid distribution zone 316. Under the guidance and constraint of the biomimetic liquid distribution structure 312, the liquid cooling medium flows radially from the center to the surrounding edges within the biomimetic liquid distribution zone 316. During the radial flow, the liquid cooling medium penetrates downward through the biomimetic liquid distribution structure 312 into the evaporation phase change zone 317. The liquid cooling medium entering the evaporation phase change zone 317 absorbs heat under the heating effect of the heat source below and rapidly vaporizes into steam. The vaporized steam flows upward and continues to flow to the surrounding edges outside the biomimetic liquid distribution zone 316, eventually flowing out from the exhaust channel 315 on the side of the top cover 311 and from the exhaust port 3114 into the condenser 4.

[0058] In one embodiment, the evaporation phase change structure 313 includes a base plate 3131 and a plurality of partitions 3132. The partitions 3132 are spaced apart on the base plate 3131 and arranged at intervals along the center of the base plate 3131 toward the edge of the base plate 3131 to form a first central region 3133 and a plurality of annular regions 3134 surrounding the first central region 3133 on the base plate 3131. The biomimetic liquid separation structure 312 includes a central member 3121 and a plurality of branch members 3123. The central member 3121 forms a second central region 3122, which is correspondingly connected to the first central region 3133 to form a liquid inlet channel 314. The plurality of branch members 3123 are spaced apart along the outer periphery of the central member 3121, and each branch member... One end of 3123 is connected to the central component 3121, and the other end of each branch component 3123 extends toward the edge of the base plate 3131. Each branch component 3123 has a branch region 3124 that communicates with the second central region 3122. In the direction from the center of the base plate 3131 to the edge of the base plate 3131, each branch region 3124 communicates with multiple annular regions 3134 to form a biomimetic liquid separation zone 316. Multiple annular regions 3134 located between two adjacent branch components 3123 cooperate with the two adjacent branch components 3123 to form an evaporation phase change zone 317. The top cover 311 cooperates with the outermost partition 3132 and the end of the multiple branch components 3123 away from the central component 3121 to form an exhaust channel 315.

[0059] In this embodiment, as Figures 3 to 6As shown, the surface of the base plate 3131 of the evaporation phase change structure 313 facing away from the partition plate 3132 is thermally coupled to the heat source. Multiple partition plates 3132 are spaced apart on the base plate 3131 and are arranged at intervals along the center of the base plate 3131 toward the edge of the base plate 3131, so that the base plate 3131 located at the center of the base plate 3131 forms an annular first central region 3133. Other partition plates 3132 are all spaced around the first central region 3133, so that an annular region 3134 is formed between two adjacent partition plates 3132. Multiple partition plates are arranged at intervals along the center of the base plate 3131 toward the edge of the base plate 3131.

[0060] Understandable, such as Figure 5 and Figure 6 As shown, the biomimetic liquid distribution structure 312 adopts a lotus leaf-inspired design, so that the central component 3121 of the biomimetic liquid distribution structure 312 forms a second central region 3122 corresponding to and connected with the first central region 3133. At this time, the second central region 3122 and the first central region 3133 are correspondingly connected to form a liquid inlet channel 314. One end of multiple branch components 3123 is connected to the central component 3121, and the other end of multiple branch components 3123 extends toward the edge of the bottom plate 3131. That is, multiple branch components 3123 are arranged radially with the central component 3121 as the center, and each branch component 3123 forms a branch region 3124 that is connected to the second central region 3122. At this time, the multiple branch components 3123 of the biomimetic liquid distribution structure 312 are located between the multiple partitions 3132 and the top cover 311 of the evaporation phase change structure 313, so that the biomimetic liquid distribution structure... Each branch region 3124 of 312 is connected to the corresponding multiple annular regions 3134 to form a biomimetic liquid distribution region 316. The multiple annular regions 3134 located between two adjacent branch members 3123 cooperate with the two adjacent branch members 3123 to form an evaporation phase change region 317. That is, the biomimetic liquid distribution region 316 and the evaporation phase change region 317 are alternately arranged along the periphery of the liquid inlet channel 314, and the biomimetic liquid distribution region 316 and the evaporation phase change region 317 are alternately arranged radially along the periphery of the liquid inlet channel 314.

[0061] In this embodiment, the liquid cooling medium flows into the evaporator 31 from the inlet 3112, first entering the first central region 3133 of the inlet channel 314 through the inlet 3112. After the first central region 3133 is filled, it enters the second central region 3122. At this time, under the guidance constraint of the biomimetic liquid distribution structure 312, it flows radially from the second central region 3122 along multiple branch regions 3124, that is, it enters the biomimetic liquid distribution zone 316. In the biomimetic liquid distribution zone 316, the liquid cooling medium flows radially from the central region to the surrounding edges. During the radial flow, the liquid cooling medium flows through the biomimetic liquid distribution structure 312 towards... The liquid coolant penetrates downwards into multiple annular regions 3134 and, constrained by these regions, permeates circumferentially into the evaporation phase change region 317. The liquid coolant entering the evaporation phase change region 317 absorbs heat under the heating effect of the heat source below, rapidly vaporizing to form steam, indicating that the liquid coolant is in the phase change evaporation stage. The vaporized steam flows upwards and continues to flow towards the surrounding edges outside the biomimetic liquid separation region 316, eventually exiting through the exhaust channel 315 on the side of the top cover 311, indicating that the steam coolant is in the reflux and collection stage, and flowing out from the exhaust port 3114 into the condenser 4.

[0062] In one embodiment, the top cover 311 includes a top plate 3111 and a side plate 3113 disposed around the periphery of the top plate 3111. The top plate 3111 is opposite to and spaced from the bottom plate 3131. The side plate 3113 extends toward the bottom plate 3131 and is connected to the bottom plate 3131. The top plate 3111 is provided with a liquid inlet 3112 and the side plate 3113 is provided with an air outlet 3114.

[0063] In this embodiment, as Figures 3 to 5 As shown, the top plate 3111 of the top cover 311 and the bottom plate 3131 of the evaporation phase change structure 313 are optionally arranged opposite to each other and parallel to each other. The top cover 311 is connected to the bottom plate 3131 of the evaporation phase change structure 313 through the side plate 3113, and supports the top plate 3111 and the bottom plate 3131 to be opposite to each other and spaced apart, so as to provide installation space for the partition 3132 and the biomimetic liquid separation structure 312.

[0064] Understandably, the side plate 3113 of the top cover 311 extends toward the bottom plate 3131 and connects with the bottom plate 3131, such that the side plate 3113 of the top cover 311 and the outermost partition plate 3132 form an air outlet channel 315. Optionally, the branch member 3123 of the biomimetic liquid distribution structure 312 may extend from the partition plate 3132 located at the center of the bottom plate 3131 to the outermost partition plate 3132.

[0065] In this embodiment, the liquid inlet 3112 is located on the top plate 3111, optionally at the center of the top plate 3111. The air outlet 3114 is located on the side plate 3113, which facilitates the rapid output of the liquid cooling medium from the air outlet channel 315 through the air outlet 3114. Of course, in other embodiments, the air outlet 3114 can also be located on the top plate 3111, at the edge of the top plate 3111, that is, at the position corresponding to the air outlet channel 315, and is not limited here.

[0066] Optionally, the top cover 311 is made of stainless steel, and its thickness can be selected as 1mm. Understandably, the biomimetic liquid distribution structure 312 can be made of stainless steel or copper foil. When the biomimetic liquid distribution structure 312 is made of copper foil, the surface of the copper foil is nickel-plated for corrosion protection to prevent corrosion from the liquid cooling medium. The thickness of the biomimetic liquid distribution structure 312 can be selected as 0.5mm.

[0067] Optionally, the liquid inlet 3112, the second central region 3122 and the first central region 3133 are all located at the center of the evaporator 31 and are arranged in a corresponding manner along the thickness direction of the evaporator 31.

[0068] In this embodiment, as Figures 2 to 6 As shown, by placing the liquid inlet 3112, the second central region 3122, and the first central region 3133 at the center of the evaporator 31, the liquid cooling medium can quickly enter the liquid inlet channel 314 through the liquid inlet 3112. Furthermore, the biomimetic liquid distribution structure 312 enables the liquid cooling medium to uniformly enter the biomimetic liquid distribution zone 316 and the evaporation phase change zone 317, thereby improving the heat exchange efficiency of the evaporator 31.

[0069] Optionally, the multiple branch members 3123 of the biomimetic liquid distribution structure 312 are integrally formed with the central member 3121. In this embodiment, as... Figure 5 and Figure 6 As shown, by setting the central component 3121 and multiple branch components 3123 as an integrated structure, the strength of the structure can be increased, and the multiple branch regions 3124 of the multiple branch components 3123 and the second central region 3122 of the central component 3121 can be smoothly connected, ensuring that the liquid cooling medium can smoothly enter the biomimetic liquid distribution zone 316 and the evaporation phase change zone 317.

[0070] In this embodiment, the hydraulic diameter of each branch region 3124 near the center member 3121 is defined as D. 中心 The hydraulic diameter D of each branch region 3124 near the center component 3121 is... 中心 The diameter can be selected from 0.1mm to 5mm. Optionally, the hydraulic diameter D of each branch region is 3124. 中心The thicknesses are 0.1mm, 0.5mm, 1mm, 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, and 5mm, and are not limited here.

[0071] In this embodiment, the hydraulic diameter of the end of each branch region 3124 furthest from the central member 3121 is defined as D. 边缘 The hydraulic diameter D of each branch region 3124 at the end furthest from the central component 3121. 边缘 The diameter is 0.5mm to 10mm. Optionally, the hydraulic diameter D of each branch region is 3124. 边缘 The thicknesses are 0.5mm, 1mm, 1.5mm, 2mm, 2.5mm, 3mm, 3.5mm, 4mm, 4.5mm, 5mm, 5.5mm, 6mm, 6.5mm, 7mm, 7.5mm, 8mm, 8.5mm, 9mm, 9.5mm, and 10mm, and are not limited here.

[0072] Understandable, such as Figure 5 and Figure 6 As shown, the cross-sectional dimensions of each branch region 3124 gradually increase from the center of the base plate 3131 towards its edge. Optionally, the hydraulic diameter increase rate γ of each branch region 3124 is 0.02~1; where γ = (D 边缘 -D 中心 ) / R, where R is the radius of the biomimetic liquid separation zone 316.

[0073] In this embodiment, by setting the cross-sectional dimensions of each branch region 3124 to gradually increase from the center of the base plate 3131 towards its edge, the hydraulic diameter increase rate γ is positively correlated with the increase rate of the gas phase ratio of the liquid cooling medium during radial flow. It should be noted that the hydraulic diameter increase rate γ of each branch region 3124 can adopt any of the following methods: linear increase, exponential increase, or piecewise increase; no limitation is made here.

[0074] Understandably, during the radial flow of the liquid cooling medium, as it continuously permeates downwards into the evaporation phase change zone 317 and the vapor generated by evaporation back-mixes upwards, the cavitation fraction of the gas-liquid two-phase mixture in the biomimetic liquid separation zone 316 gradually increases radially. By gradually increasing the hydraulic diameter of the flow channel along the flow direction, the increase in cavitation fraction can be accommodated, maintaining a stable two-phase flow velocity and avoiding excessive pressure drop or flow blockage caused by excessively high flow velocity.

[0075] In one embodiment, the inner wall of each branch region 3124 is provided with a hydrophobic layer. Optionally, the contact angle of the hydrophobic layer is >120°. It is understood that by providing a hydrophobic layer on the surface of the biomimetic liquid distribution structure 312, the flow resistance of the liquid cooling medium flowing in the biomimetic liquid distribution region 316 can be reduced.

[0076] It should be noted that the hydrophobic layer on the surface of the biomimetic liquid separation structure 312 can adopt a technical approach that combines surface coating modification and micro / nano structure construction. The hydrophobic layer is mainly applied to the surface of the biomimetic liquid separation structure 312 through dip coating / spin coating, chemical vapor deposition, self-assembled monolayer, sol-gel method, plasma treatment + graft polymerization, etc. For specific details, refer to existing technologies and no limitations are made here.

[0077] In this embodiment, the lower surface of the evaporation phase change structure 313 is in close contact with the heat source, and the interior of the evaporation phase change structure 313 is provided with a micro-nano composite structure to enhance boiling heat transfer.

[0078] In one implementation, such as Figure 7 As shown, the inner walls of the first central region 3133 and the multiple annular regions 3134 are provided with first recessed structures 3135, which are array structures formed by the first recesses 3136. It can be understood that by providing the first recessed structures 3135 on the bottom plate 3131 and the partition plate 3132 of the evaporation phase change structure 313, the vaporization nuclei can be increased and boiling heat transfer enhanced when the liquid cooling medium enters the first central region 3133 and the multiple annular regions 3134 of the evaporation phase change structure 313.

[0079] Optionally, the diameter of the first pit 3136 is 5μm to 50μm. In this embodiment, the diameter of the first pit 3136 is 5μm, 10μm, 15μm, 20μm, 25μm, 30μm, 35μm, 40μm, 45μm, 50μm, etc., and is not limited here. It is understood that the diameter of the first pit 3136 is preferably 10μm to 30μm, and is not limited here.

[0080] Optionally, the depth of the first pit 3136 is 2μm to 20μm. In this embodiment, the depth of the first pit 3136 is 2μm, 5μm, 8μm, 10μm, 13μm, 15μm, 18μm, 20μm, etc., and is not limited here. It is understood that the depth of the first pit 3136 is preferably 5μm to 15μm, and is not limited here.

[0081] Optionally, the spacing between the first dimples 3136 is 10μm to 100μm. In this embodiment, the spacing between the first dimples 3136 is 10μm, 15μm, 20μm, 25μm, 30μm, 35μm, 40μm, 45μm, 50μm, 55μm, 60μm, 65μm, 70μm, 75μm, 80μm, 85μm, 90μm, 95μm, 100μm, etc., and is not limited here. It is understood that the spacing between the first dimples 3136 is preferably 20μm to 50μm, and is not limited here.

[0082] In this embodiment, the density or size of the first recess structure 3135 exhibits a gradient distribution along the flow direction of the liquid cooling medium (from the center outwards). Optionally, the density of the first recess 3136 gradually increases from the center of the base plate 3131 towards its edge. Optionally, the diameter of the first recess 3136 gradually decreases from the center of the base plate 3131 towards its edge.

[0083] Understandably, in the central region, the liquid cooling medium is mainly liquid, and the first pit 3136 has a lower density and a larger size, which can promote nucleated boiling; in the edge region, the proportion of gas phase in the liquid cooling medium is high, and the first pit 3136 has a higher density and a smaller size, which can enhance capillary force and prevent drying.

[0084] In another embodiment, such as Figure 8 As shown, the inner walls of the first central region 3133 and the multiple annular regions 3134 are provided with porous structures 3137, which are array structures formed by micropores 3138. It can be understood that by providing porous structures 3137 on the bottom plate 3131 and partition plate 3132 of the evaporation phase change structure 313, the capillary capacity can be increased, vaporization nuclei can be increased, and boiling heat transfer can be enhanced when the liquid cooling medium enters the first central region 3133 and the multiple annular regions 3134 of the evaporation phase change structure 313.

[0085] Optionally, the pore size of the micropore 3138 is 50nm to 500nm. In this embodiment, the pore size of the micropore 3138 is 50nm, 55nm, 60nm, 65nm, 70nm, 75nm, 80nm, 85nm, 90nm, 95nm, 100nm, 150nm, 200nm, 250nm, 300nm, 350nm, 400nm, 450nm, 500nm, etc., and is not limited here. It is understood that the pore size of the micropore 3138 is preferably 100nm to 300nm, and is not limited here.

[0086] Optionally, the porosity of the micropores 3138 is 30% to 70%. In this embodiment, the porosity of the micropores 3138 is 30%, 35%, 40%, 45%, 50%, 55%, 60%, 65%, 70%, etc., and is not limited thereto. It is understood that the porosity of the micropores 3138 is preferably 40% to 60%, and is not limited thereto.

[0087] In this embodiment, the density or size of the porous structure 3137 exhibits a gradient distribution along the flow direction of the liquid cooling medium (from the center outwards). Optionally, the density of the micropores 3138 gradually increases from the center of the base plate 3131 towards its edge. Optionally, the diameter of the micropores 3138 gradually decreases from the center of the base plate 3131 towards its edge.

[0088] Understandably, in the central region, the liquid cooling medium is mainly liquid, and the micropores 3138 have a lower density and larger size, which can promote nucleate boiling; in the edge region, the liquid cooling medium has a higher proportion of gas phase, and the micropores 3138 have a higher density and smaller size, which can enhance capillary force and prevent drying.

[0089] In one embodiment, the inner walls of the first central region 3133 and the plurality of annular regions 3134 are provided with a hydrophilic layer. Optionally, the contact angle of the hydrophilic layer is <30°.

[0090] In this embodiment, the hydrophilic layer can be applied using surface coating methods (dip coating, spray coating, spin coating), plasma surface treatment, photolithographic patterning deposition, and in-situ polymerization / self-assembly techniques. For example, it can be applied to the surfaces of the base plate 3131 and the partition plate 3132 through liquid phase coating, plasma modification, photolithographic patterning deposition, multilayer film structure construction, chemical self-assembly and grafting processes. The specific application is based on existing technologies and is not limited here.

[0091] Understandably, by providing a hydrophilic layer on the surface of the bottom plate 3131 and the partition plate 3132 of the evaporation phase change structure 313, the capillary force of the hydrophilic layer is used to draw in the liquid cooling medium and transport it circumferentially, thereby achieving rapid liquid replenishment to areas with high dryness. At the same time, the hydrophilic layer can make the liquid surface spread quickly, preventing the gaseous liquid cooling medium from adhering to the wall surface and being difficult to detach, increasing the steam thermal resistance, preventing film boiling, increasing nucleation boiling, and enhancing the heat exchange capacity.

[0092] In this embodiment, the multiple branch regions 3124 of the biomimetic liquid distribution structure 312 in the evaporator 31 are configured as radially gradient flow channels to achieve uniform distribution of the liquid cooling medium from the center to the periphery, avoiding local drying. Furthermore, a hydrophobic layer is provided on the surface of the biomimetic liquid distribution structure 312 to effectively reduce flow resistance, causing the hydraulic diameter of the branch regions 3124 to increase with the flow direction, adapting to changes in the cavitation fraction and reducing pressure drop by 20%~30%. The surface of the evaporation phase change structure 313 in the evaporator 31 is provided with a first recessed structure 3135 or a porous structure 3137, increasing the boiling heat transfer coefficient by 30%~50%. A hydrophilic layer is also provided on the surface of the evaporation phase change structure 313 to reduce flow resistance, facilitate capillary replenishment, and increase gas escape velocity. The radial flow path design of the biomimetic liquid distribution structure 312 in the evaporator 31, combined with the multiple annular regions 3134 in the evaporation phase change structure 313, results in a compact structure that effectively reduces the overall size of the evaporator 31, making it suitable for space-constrained applications.

[0093] Optionally, the evaporation phase change structure 313 is made of oxygen-free copper, the thickness of the bottom plate 3131 and the partition plate 3132 in the evaporation phase change structure 313 is 2.0 mm, and the flatness of the contact surface between the bottom plate 3131 and the heat source in the evaporation phase change structure 313 is 0.01 mm.

[0094] In one embodiment, the surface of the evaporation phase change structure 313 is provided with a first pit structure 3135. The diameter of the first pit 3136 located in the central region of the first pit structure 3135 can be selected as 25 μm, and the density of the first pit 3136 can be selected as 300 pits / mm². The diameter of the first pit 3136 located in the edge region can be selected as 12 μm, and the density of the first pit 3136 can be selected as 600 pits / mm².

[0095] In another embodiment, the surface of the evaporation phase change structure 313 is formed by electrochemical deposition of nano-copper to form a porous structure 3137, in which the micropores 3138 have a pore size of 150 nm and a porosity of 50%.

[0096] In one embodiment, the evaporation assembly 3 includes a plurality of evaporators 31 for contact with a heat source, the plurality of evaporators 31 being arranged in parallel, the outlet of the pump 2 being connected to the inlet of the plurality of evaporators 31 via a circulation pipe 1, and the outlet of the plurality of evaporators 31 being connected to the inlet of the condenser 4 via a circulation pipe 1.

[0097] In this embodiment, as Figure 1 As shown, multiple evaporators 31 of the evaporation assembly 3 can simultaneously contact a single heat source. Of course, the multiple evaporators 31 of the evaporation assembly 3 can also contact different heat sources separately, which is not limited here.

[0098] It should be noted that the external outline and dimensions of the multiple evaporators 31 can be the same or different. The specific design of the external outline and dimensions of the evaporator 31 is based on the shape and outline of the heat source. It is understood that the multiple evaporators 31 all include a top cover 311, a biomimetic liquid separation structure 312, and an evaporation phase change structure 313. The structures of the top cover 311, the biomimetic liquid separation structure 312, and the evaporation phase change structure 313 refer to the structures described above and are not limited here.

[0099] Understandably, multiple evaporators 31 are arranged at intervals and in parallel, and the liquid cooling medium flow paths of the multiple evaporators 31 are arranged in parallel. That is, the outlet of pump 2 is connected to the inlet of multiple evaporators 31 through circulation pipe 1, and the outlet of multiple evaporators 31 is connected to the inlet of condenser 4 through circulation pipe 1. In this way, the liquid cooling medium delivered by the outlet of pump 2 can simultaneously enter multiple evaporators 31 through circulation pipe 1 to cool and dissipate heat from one or more heat sources, thereby ensuring heat dissipation efficiency.

[0100] In one embodiment, along the flow direction of the liquid cooling medium, the condenser 4 is formed with at least two heat exchange sections, including a first heat exchange section 41 located on the inlet side of the condenser 4 and a second heat exchange section 42 located on the outlet side of the condenser 4. A first condensation channel is formed in the first heat exchange section 41, and the first heat exchange section 41 is provided with a plurality of first fins. A second condensation channel is formed in the second heat exchange section 42, and the second heat exchange section 42 is provided with a plurality of second fins.

[0101] In this embodiment, as Figure 1 As shown, condenser 4 can be a plate condenser. By dividing condenser 4 into at least two independent and optimized heat exchange sections along the flow direction of the liquid cooling medium, the fin density, channel size and surface microstructure of each section are independently designed according to the heat exchange characteristics of the liquid cooling medium at different condensation stages.

[0102] Optionally, the condenser 4 forms two heat exchange sections. In this embodiment, as... Figure 1 As shown, the two heat exchange sections include a first heat exchange section 41 located on the inlet side of the condenser 4 and a second heat exchange section 42 located on the outlet side of the condenser 4.

[0103] Understandably, the first heat exchange section 41 is located at the end of the condenser 4 near the inlet side and is a two-phase condensation section. The first heat exchange section 41 is used to gradually condense the liquid cooling medium from the dew point to the bubble point within the temperature glide range. The second heat exchange section 42 is located at the end of the condenser 4 near the outlet side and is a liquid phase subcooling section. The second heat exchange section 42 is used to subcool the saturated liquid to prevent pump cavitation.

[0104] Optionally, the first condensation channel of the first heat exchange section 41 is configured as a variable cross-section microchannel, with the hydraulic diameter of the first condensation channel gradually decreasing along the flow direction of the liquid cooling medium. This effectively condenses the liquid cooling medium from the dew point to the bubble point within the temperature glide range.

[0105] Optionally, the density of the multiple first fins in the first heat exchange section 41 gradually decreases along the flow direction of the liquid cooling medium. This effectively condenses the liquid cooling medium from the dew point to the bubble point within the temperature glide range.

[0106] In one embodiment, the inner wall of the first condensation channel is provided with a second recess structure, which is an array structure formed by the second recesses; wherein, the diameter of the second recess is 10μm~50μm, the depth of the second recess is 5μm~20μm, and the spacing between the second recesses is 20μm~100μm.

[0107] In this embodiment, by providing a second recessed structure on the inner wall of the first condensation channel in the first heat exchange section 41, the vaporization nuclei can be increased, thus enhancing boiling heat transfer. Optionally, the diameter of the second recess can be 10μm, 15μm, 20μm, 25μm, 30μm, 35μm, 40μm, 45μm, 50μm, etc., and is not limited here. Optionally, the depth of the second recess can be 5μm, 8μm, 10μm, 13μm, 15μm, 18μm, 20μm, etc., and is not limited here. Optionally, the spacing of the second pits can be 20μm, 25μm, 30μm, 35μm, 40μm, 45μm, 50μm, 55μm, 60μm, 65μm, 70μm, 75μm, 80μm, 85μm, 90μm, 95μm, 100μm, etc., and is not limited here.

[0108] Optionally, the inner wall of the first condensation channel is provided with a hydrophobic layer. This reduces the flow resistance of the first condensation channel.

[0109] In this embodiment, the second condensation channel is configured as a microchannel with a constant cross-section. This ensures that the saturated liquid is subcooled to prevent pump cavitation.

[0110] Understandably, by adopting the above-mentioned partitioned optimization design for condenser 4, the total pressure drop of condenser 4 is reduced by more than 15%, and the local heat transfer coefficient of the two-phase condensation section is increased by more than 30%.

[0111] In one embodiment, the detection component 5 includes a plurality of temperature and pressure sensors 51 and a void fraction sensor 52. The plurality of temperature and pressure sensors 51 are disposed in the circulation pipeline 1 and are respectively located at the inlet side of the evaporator 31, the outlet side of the evaporator 31 and the outlet side of the condenser 4, for detecting the temperature and pressure of the liquid cooling medium. The plurality of temperature and pressure sensors 51 are communicatively connected to the control unit 7. The void fraction sensor 52 is disposed in the circulation pipeline 1 and is located at the outlet side of the evaporator 31 or the inlet side of the condenser 4, for detecting the void fraction of the liquid cooling medium. The void fraction sensor 52 is communicatively connected to the control unit 7.

[0112] In this embodiment, as Figure 1 and Figure 9 As shown, by setting the detection component 5 as a sensor array and adopting a distributed layout, it is placed at key nodes of the closed loop in the liquid cooling system 100, thus measuring the temperature and pressure of the liquid cooling medium at each key node. Understandably, multiple temperature and pressure sensors 51 are located at the inlet side of the evaporator 31, the outlet side of the evaporator 31, and the outlet side of the condenser 4, respectively, to detect the temperature and pressure of the liquid cooling medium.

[0113] Understandably, the temperature and pressure sensor 51 installed at the inlet side of the evaporator 31 can detect the temperature and pressure of the liquid cooling medium in real time, i.e., T1 / P1; the temperature and pressure sensor 51 installed at the outlet side of the evaporator 31 can detect the temperature and pressure of the liquid cooling medium in real time, i.e., T2 / P2; and the temperature and pressure sensor 51 installed at the outlet side of the condenser 4 can detect the temperature and pressure of the liquid cooling medium in real time, i.e., T3 / P3. The superheat at the outlet of the evaporator 31 can be calculated based on T2 / P2, and the subcooling at the outlet of the condenser 4 can be calculated based on T3 / P3.

[0114] Optionally, the temperature and pressure sensor 51 uses a platinum resistance temperature sensor and a pressure sensor, with a measurement range of -50℃ to 120℃ and 0 to 5MPa.

[0115] In this embodiment, as Figure 1 As shown, the void fraction sensor 52 can be installed on the outlet side of the evaporator 31; alternatively, the void fraction sensor 52 can also be installed on the inlet side of the condenser 4, without limitation. The void fraction sensor 52 is used to detect the void fraction of the liquid cooling medium.

[0116] Optionally, the void fraction sensor 52 is a dielectric constant sensor, a capacitance tomography sensor, or an ultrasonic sensor. In this embodiment, the void fraction sensor 52 is at least one of a dielectric constant sensor, a capacitance tomography sensor, and an ultrasonic sensor, and is installed non-invasively.

[0117] Understandably, by placing the cavitation fraction sensor 52 at the outlet of the evaporator 31, close to the downstream of the temperature and pressure sensor 51, it is used to measure the real-time cavitation fraction of the liquid cooling medium at the outlet of the evaporator 31. Combined with the temperature and pressure data detected by the temperature and pressure sensor 51, the real-time component concentration C_r of the current liquid cooling medium can be deduced.

[0118] In this embodiment, the void fraction sensor 52 is a dielectric constant sensor with a measurement range of 0~100%; or, the void fraction sensor is a capacitance tomography sensor with a measurement range of 0~110%, which is not limited here.

[0119] In one embodiment, the detection component 5 further includes a flow sensor 53, which is disposed in the circulation pipeline 1 and located at the outlet side of the pump 2, for detecting the flow rate of the liquid cooling medium in the circulation pipeline 1. The flow sensor 53 is communicatively connected to the control unit 7.

[0120] In this embodiment, as Figure 1 and Figure 9 As shown, a flow sensor 53 is used to detect the flow rate of the liquid cooling medium in the circulation pipeline 1. It is understood that the flow sensor 53 is located at the outlet of pump 2 and is used to measure the total circulating flow rate of the main circuit of the liquid cooling system 100. Optionally, the flow sensor 53 is an electromagnetic flow meter with a measurement range of 0~30 kg / h.

[0121] In one embodiment, the detection component 5 further includes a plurality of temperature sensors 54 disposed on the surface of the heat source. The plurality of temperature sensors 54 are arranged in an array along the flow direction of the liquid cooling medium and are used to detect the temperature of the surface of the heat source. The plurality of temperature sensors 54 are communicatively connected to the control unit 7.

[0122] In this embodiment, as Figure 1 and Figure 9 As shown, by setting multiple temperature sensors 54 on the surface of the heat source, the multiple temperature sensors 54 are arranged in an array along the flow direction of the liquid cooling medium. In this way, the temperature of the heat source surface is detected by multiple temperature sensors 54, thereby generating a high-resolution temperature distribution curve of the heat source surface.

[0123] It should be noted that existing systems lack the ability to actively, accurately, and dynamically match the working fluid phase change temperature curve with the heat source / cold source temperature change curve, making it difficult to further improve system energy efficiency and temperature uniformity. Furthermore, dynamic changes in system load, ambient temperature fluctuations, and pressure drops during flow can all alter local pressure, thereby changing the local saturation temperature of a single working fluid. This can easily lead to the working fluid failing to undergo phase change at certain locations within the system, resulting in heat dissipation failure.

[0124] In this embodiment, the real-time data collected by the temperature and pressure sensor 51, the air bubble fraction sensor 52, the flow sensor 53, and the temperature sensor 54 of the detection component 5 are input to the control unit 7. Through fusion calculation, the thermodynamic state (enthalpy, dryness fraction, bubble point / dew point temperature, and real-time component concentration) of the liquid cooling medium is accurately reconstructed, providing a complete data foundation for the intelligent control of the liquid cooling system 100. By sensing the state of the liquid cooling system 100 in real time and dynamically adjusting the working fluid component concentration of the liquid cooling medium, the problems of dynamic load changes, ambient temperature fluctuations, and local saturation temperature changes caused by pressure drop during flow are effectively solved. This significantly improves the heat dissipation effect of the liquid cooling system 100 under different operating conditions and effectively prevents heat dissipation failure caused by pressure changes.

[0125] In one embodiment, a gas phase separation chamber 61 and a liquid phase separation chamber 62 are formed in the liquid storage unit 6. The gas phase separation chamber 61 is connected to the inlet of the condenser 4 through the first pipeline 63, and the liquid phase separation chamber 62 is connected to the inlet of the pump 2 through the circulation pipeline 1. The liquid phase separation chamber 62 is used to separate different working fluids.

[0126] In this embodiment, as Figure 1 As shown, the gas-phase separation chamber 61 of the liquid storage unit 6 is used to return the uncondensed gaseous liquid cooling medium to the condenser 4, and the liquid-phase separation chamber 62 of the liquid storage unit 6 is used to separate the different components of the liquid cooling medium. Optionally, the liquid-phase separation chamber 62 can use tools such as a rotary separator to separate different working media according to their different densities or boiling points. It should be noted that the structures of the gas-phase separation chamber 61 and the liquid-phase separation chamber 62 of the liquid storage unit 6 can refer to the existing gas / liquid phase separation chamber structures, and are not limited here.

[0127] Optionally, the liquid storage unit 6 also includes a one-way valve 66 located in the first pipeline 63. This ensures that the gas phase separation chamber 61 is used to return the uncondensed gas phase liquid cooling medium to the condenser 4, preventing the gas phase liquid cooling medium output from the evaporator 31 from flowing into the gas phase separation chamber 61 through the first pipeline 63.

[0128] In one embodiment, the liquid phase separation chamber 62 includes a plurality of liquid phase chambers 621, the number of which corresponds one-to-one with the amount of working fluid of the liquid cooling medium. Each liquid phase chamber 621 is connected to the circulation pipeline 1 through a second pipeline 64. The liquid storage unit 6 also includes a flow control valve 65 disposed in each second pipeline 64, and the flow control valve 65 is communicatively connected to the control unit 7.

[0129] In this embodiment, as Figure 1 As shown, the multiple liquid phase chambers 621 of the liquid phase separation chamber 62 are used to contain and store different working fluids respectively, and the liquid phase separation chamber 62 is used to separate liquid working fluids with different boiling point components into multiple liquid phase chambers 621.

[0130] Optionally, the number of liquid phase chambers 621 is the same as the number of working fluid in the liquid cooling medium. In this embodiment, the number of second pipelines 64 and flow control valves 65 is the same as the number of liquid phase chambers 621, and is not limited here.

[0131] Understandably, by setting a flow control valve 65 on the second pipeline 64, the flow control valve 65 is located between the liquid phase separation chamber 62 of the liquid storage unit 6 and the pump 2, and the flow control valve 65 is electrically connected to the control unit 7, so as to adjust the proportion of different components and input them into the pump 2 according to the instructions of the control unit 7.

[0132] Optionally, the flow control valve 65 is model SMV-01 with a flow range of 0~200ml / min; or, the flow control valve 65 is model SMV-02 with a flow range of 0~300ml / min, which is not limited here.

[0133] It should be noted that the existing system has shortcomings in the adjustment and control of the concentration of working fluid components. It is difficult to make dynamic adjustments according to real-time temperature changes and load conditions, resulting in poor system adaptability and difficulty in meeting the heat dissipation requirements under different operating conditions.

[0134] The design in this embodiment can calculate the deviation between the actual thermodynamic performance and the target performance based on the current working fluid component concentration and the thermodynamic performance index of the system, calculate the required change in the working fluid component concentration, and then adjust the working fluid ratio of the liquid cooling medium in the liquid cooling system 100, thereby improving the energy efficiency of the liquid cooling system 100.

[0135] Optionally, the volume of the gas phase separation chamber 61 and the liquid phase separation chamber 62 of the liquid storage unit 6 is 5L each; or, the volume of the gas phase separation chamber 61 and the liquid phase separation chamber 62 of the liquid storage unit 6 is 10L each.

[0136] In one embodiment, the control unit 7 adopts a two-layer control architecture. The control unit 7 includes a bottom controller 71 and an upper optimizer 72. The bottom controller 71 controls the working fluid of the pump 2 according to the performance parameters detected by the detection component 5. The upper optimizer 72 dynamically calculates the target working fluid component concentration of the liquid cooling medium according to the temperature of the heat source and the performance of the liquid cooling medium, and transmits it to the bottom controller 71.

[0137] In this embodiment, as Figure 9As shown, by adopting a two-layer control architecture, the bottom controller 71 of the control unit 7 is based on a PID control algorithm. Based on the performance parameters detected by the detection component 5, and using the system pressure P and the evaporator 31 outlet superheat ΔT as controlled variables, it outputs adjustment signals to the pump 2 and the flow control valve 65, thereby maintaining the stability of the basic operating parameters of the liquid cooling system 100. The upper optimizer 72 of the control unit 7 is based on a reinforcement learning or model predictive control algorithm. Based on the temperature of the heat source and the performance of the liquid cooling medium, and using at least one of the following as the reward function or optimization objective—heat source temperature uniformity, system energy efficiency ratio (COP), or total energy loss—it dynamically calculates the target working fluid component concentration of the liquid cooling medium and outputs adjustment commands to the bottom controller 71 or directly drives the liquid storage unit 6. This dual-layer control structure enables precise adjustment and optimization of the liquid cooling system 100, ensuring its efficient operation under different conditions. It can solve the problem of active, accurate, and dynamic matching of the working fluid phase change temperature curve with the heat source / cold source temperature change curve. The liquid cooling system 100 can effectively improve system energy efficiency, improve temperature uniformity, and enhance operating condition adaptability to meet the growing heat dissipation needs of data centers.

[0138] In one embodiment, the control unit 7 further includes a prediction module 73, which is used to predict the phase change characteristics of the working fluid at different component concentrations based on the real-time temperature and pressure of the liquid cooling medium and in conjunction with a database of the thermodynamic properties of the liquid cooling medium.

[0139] In this embodiment, as Figure 9 As shown, by setting up the prediction module 73, the prediction module 73 can predict the phase change characteristics of the working fluid at different component concentrations based on real-time temperature and pressure data, combined with a database of the thermodynamic properties of non-azeotropic working fluids. The coordinated operation of the detection component 5 and the various modules of the control unit 7 provides strong technical support for the intelligence and automation of the liquid cooling system 100, ensuring the efficient operation and stability of the liquid cooling system 100.

[0140] Understandably, in each control cycle, control unit 7 first calculates the system's thermodynamic performance indicators based on the current working fluid component concentration of the liquid cooling medium; then, based on the deviation between the current actual thermodynamic performance and the target performance, it calculates the required change in the working fluid component concentration; finally, based on the required change in the working fluid component concentration, it fine-tunes the working fluid composition through the liquid storage unit 6. Through this method, the liquid cooling system 100 achieves adaptive operation, improving the overall efficiency and stability of the system.

[0141] The present invention also proposes a control method for a liquid cooling system 100, wherein the liquid cooling system 100 is the liquid cooling system 100 described above. The specific structure of the liquid cooling system 100 is as described in the foregoing embodiments. Since the control method of the liquid cooling system 100 adopts all the technical solutions of all the foregoing embodiments, it has at least all the beneficial effects brought about by the technical solutions of the foregoing embodiments, which will not be described in detail here.

[0142] In this embodiment, the control method for the liquid cooling system 100 includes: S1. Obtain the temperature, pressure and empty shot ratio of the current liquid cooling medium collected in real time by the detection component 5, and calculate the real-time working fluid component concentration C_r of the liquid cooling medium based on the temperature, pressure and empty shot ratio. S2. Obtain the temperature of the heat source collected in real time by the detection component 5, and calculate the target working fluid component concentration C_t of the liquid cooling medium based on the temperature of the heat source and the thermodynamic characteristics of the liquid cooling medium. S3. Based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, control the flow control valve 65 to adjust the flow rate of different working fluids in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline 1.

[0143] In this embodiment, as Figures 1 to 9 As shown, the liquid cooling system 100 includes a circulation pipeline 1, a pump 2, an evaporation assembly 3, a condenser 4, a detection assembly 5, a liquid storage unit 6, and a control unit 7. The circulation pipeline 1 connects the pump 2, the evaporation assembly 3, the condenser 4, and the liquid storage unit 6 in sequence to form a closed loop. The circulation pipeline 1 provides a flow path for the liquid cooling medium, and the pump 2 provides driving force for the liquid cooling medium in the closed loop. The evaporation assembly 3 is in contact with the heat source of the electronic equipment, that is, the evaporation assembly 3 includes at least one evaporator 31 for contacting the heat source. The liquid cooling medium undergoes heat exchange when flowing through the evaporator 31, thereby cooling and dissipating heat from the heat source.

[0144] Optionally, the liquid cooling medium includes at least one first working fluid and at least one second working fluid; wherein the first working fluid is a low-boiling-point working fluid, and the second working fluid is a high-boiling-point working fluid. In this embodiment, the liquid cooling medium is a non-azeotropic mixture composed of working fluids with different boiling points.

[0145] Understandably, pump 2 drives the liquid cooling medium to evaporator 31. The liquid cooling medium receives heat from the heat source in evaporator 31, exchanges heat and evaporates to form gaseous cooling medium. The gaseous cooling medium is transported from evaporator 31 to condenser 4 for cooling and condensation to form liquid cooling medium, and finally returns to storage unit 6 for the next cycle.

[0146] In this embodiment, as Figure 1 and Figure 9As shown, the control unit 7 is electrically connected to the pump 2, the detection assembly 5, and the liquid storage unit 6. It is understood that the detection assembly 5 is a sensor array with a distributed layout. The detection assembly 5 includes multiple temperature and pressure sensors 51, a void fraction sensor 52, a flow sensor 53, and multiple temperature sensors 54, all of which are electrically connected to the control unit 7.

[0147] Understandably, multiple temperature and pressure sensors 51 are located at the inlet side, outlet side, and outlet side of the evaporator 31, respectively, to detect the temperature and pressure of the liquid cooling medium. A void fraction sensor 52 is located at the outlet side of the evaporator 31 or the inlet side of the condenser 4 to detect the void fraction of the liquid cooling medium. A flow sensor 53 is located at the outlet of the pump 2 to measure the total circulating flow rate of the main loop of the liquid cooling system 100. Multiple temperature sensors 54 are located on the surface of the heat source and arranged in an array along the flow direction of the liquid cooling medium to detect the temperature of the heat source surface.

[0148] In this embodiment, the liquid storage unit 6 includes a gas phase separation chamber 61, a liquid phase separation chamber 62, a first pipeline 63, multiple second pipelines 64, a one-way valve 66, and multiple flow control valves 65. All multiple flow control valves 65 are electrically connected to the control unit 7.

[0149] Understandably, in step S1, the performance parameters of the liquid cooling medium detected in real time by the detection component 5 are obtained, and the real-time working fluid component concentration C_r of the liquid cooling medium is calculated based on the performance parameters.

[0150] In this embodiment, the temperature (T), pressure (P), and real-time cavitation fraction (α, the ratio of gas phase to liquid phase) data of key nodes in the liquid cooling system 100 are collected in real time by multiple temperature and pressure sensors 51 and cavitation fraction sensors 52 of the detection component 5; the control unit 7 acquires the temperature (T), pressure (P), and real-time cavitation fraction (α, the ratio of gas phase to liquid phase) data collected in real time by multiple temperature and pressure sensors 51 and cavitation fraction sensors 52 of the detection component 5, and calculates the real-time working fluid component concentration C_r in the liquid cooling medium based on the temperature (T), pressure (P), and real-time cavitation fraction (α, the ratio of gas phase to liquid phase) data.

[0151] In one embodiment, step S2, acquiring the temperature of the heat source collected in real time by the detection component 5, and calculating the target working fluid component concentration C_t of the liquid cooling medium based on the temperature of the heat source and the thermodynamic property data of the liquid cooling medium, includes: Step S21: Obtain the temperature of the heat source collected in real time by the detection component 5; Step S22: Generate the surface temperature distribution curve T_h(x,t) of the heat source based on the temperature of the heat source; Step S23: Based on the surface temperature distribution curve T_h(x,t) of the heat source, and combined with the preset system energy efficiency optimization target, calculate the ideal target working fluid phase change temperature glide curve T_gt(p,x,t); where p is the system pressure, x is the spatial coordinate along the flow direction of the evaporator 31, and t is time; Step S24: Based on the temperature glide curve T_gt(p,x,t), combined with the current system pressure p and the preset thermodynamic properties of the liquid cooling medium, calculate in reverse the target working fluid component concentration C_t of the liquid cooling medium required to reach the temperature glide curve T_gt(p,x,t).

[0152] In this embodiment, the temperature distribution of the heat source is collected in real time by multiple temperature sensors 54 of the detection component 5, the control unit 7 obtains the temperature data of the heat source collected in real time by multiple temperature sensors 54 of the detection component 5, and generates a high-resolution heat source surface temperature distribution curve T_h(x,t) based on the temperature data of the heat source.

[0153] Understandably, the control unit 7 takes the surface temperature distribution curve T_h(x,t) of the heat source as input, and combines it with the preset system energy efficiency optimization target (i.e., the target thermodynamic performance) to dynamically calculate the ideal target working fluid phase change temperature glide curve T_gt(p,x,t) under this operating condition through an intelligent optimization algorithm, where p is the system pressure, x is the spatial coordinate along the flow direction of the evaporator 31, and t is time, which is the calculation of the optimal temperature glide curve.

[0154] Based on the temperature glide curve T_gt(p,x,t) and the current system pressure p, the control unit 7 calculates the target working fluid component concentration C_t required to reach the temperature glide curve T_gt(p,x,t) using the built-in thermodynamic property database of non-azeotropic working fluids (i.e., liquid cooling media).

[0155] In one embodiment, step S3, controlling the flow control valve 65 to adjust the flow rate of different working fluids based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline 1, includes: Step S31: Determine whether the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium exceeds a preset threshold. Step S32: If so, control the flow control valve 65 to adjust the flow rate of different working fluids in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline 1. Step S33: If not, cycle according to the current working fluid component concentration of the liquid cooling medium.

[0156] In this embodiment, the control unit 7 calculates the deviation ΔC based on the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium. The deviation ΔC is the difference between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium. The control unit 7 determines whether the absolute value of the deviation ΔC, |ΔC|, exceeds a preset threshold.

[0157] Understandably, if the absolute value |ΔC| exceeds the preset threshold, the control unit 7 sends a precision drive command to the liquid storage unit 6, adjusting the flow rate of different working fluids through multiple flow control valves 65 to achieve online adjustment of the real-time component concentration of the circulating working fluid. If the absolute value |ΔC| does not exceed the preset threshold, the circulation proceeds according to the current working fluid component concentration of the liquid cooling medium.

[0158] In this embodiment, steps S1 to S3 are repeated at a preset cycle, and the control parameters of the intelligent optimization algorithm of the control unit 7 are updated based on the control effect of the previous cycle, so as to realize the adaptive optimization of the control strategy of the liquid cooling system 100.

[0159] The control method of the liquid cooling system 100 of the present invention can sense the system status in real time and dynamically adjust the concentration of the working fluid components of the liquid cooling medium, effectively solving the problems of dynamic load changes, ambient temperature fluctuations, and local saturation temperature changes caused by pressure drop during the flow process in the liquid cooling system 100. This dynamic adaptability significantly improves the heat dissipation effect of the liquid cooling system 100 under different operating conditions and effectively prevents heat dissipation failure caused by pressure changes. At the same time, through real-time monitoring by the working fluid characteristic sensor array (i.e., detection component 5) and precise adjustment of the liquid storage unit 6 by the control unit 7, the phase change temperature curve of the liquid cooling medium is actively, accurately, and dynamically matched with the temperature change curve of the heat source / cold source, which not only improves the temperature uniformity of the liquid cooling system 100, but also significantly improves the overall thermal efficiency of the liquid cooling system 100. Furthermore, by constructing the surface temperature distribution curve of the heat source and the real-time phase change characteristic model of the working fluid of the liquid cooling medium, the accurate description and prediction of the state of the liquid cooling system 100 are realized. This method can dynamically calculate the concentration of the target working fluid component based on real-time data, and adjust the input ratio of different components through the control unit 7, which greatly improves the intelligence level and adaptability of the liquid cooling system 100.

[0160] The present invention also proposes an electronic device comprising the aforementioned liquid cooling system 100. The specific structure of the liquid cooling system 100 is as described in the foregoing embodiments. Since this electronic device employs all the technical solutions of all the foregoing embodiments, it possesses at least all the beneficial effects brought about by the technical solutions of the foregoing embodiments, which will not be elaborated upon here.

[0161] The above description is merely an optional embodiment of the present invention and does not limit the patent scope of the present invention. Any equivalent structural transformations made under the concept of the present invention using the description and drawings of the present invention, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present invention.

Claims

1. A liquid cooling system, characterized in that, The liquid cooling system includes a circulation pipeline, a pump, an evaporation assembly, a condenser, a detection assembly, a liquid storage unit, and a control unit. The circulation pipeline is used to supply the liquid cooling medium. The evaporation assembly includes at least one evaporator for contact with a heat source. The control unit is communicatively connected to the pump, the detection assembly, and the liquid storage unit. The detection assembly is used to detect the performance parameters of the liquid cooling medium and the temperature of the heat source. The outlet of the pump is connected to the inlet of the evaporator through the circulation pipeline, the outlet of the evaporator is connected to the inlet of the condenser through the circulation pipeline, the outlet of the condenser is connected to the inlet of the liquid storage unit through the circulation pipeline, and the outlet of the liquid storage unit is connected to the inlet of the pump through the circulation pipeline. The liquid cooling medium includes at least two working fluids with a boiling point difference of not less than 10°C.

2. The liquid cooling system as described in claim 1, characterized in that, The liquid cooling medium includes at least one first working medium and at least one second working medium, wherein the first working medium is a low-boiling-point working medium and the second working medium is a high-boiling-point working medium; The first working medium includes one or more of R32, R1234yf, R1234ze(E), and R290, and the second working medium includes one or more of R245fa, R1233zd(E), R1336mzz(Z), R600a, water, ethanol, and fluorinated liquid. And / or, the boiling point difference between the first working fluid and the second working fluid is 20℃-50℃; And / or, the mass ratio of the first working fluid to the second working fluid is 1:5 to 5:1; And / or, the temperature slip between the first working fluid and the second working fluid is 3℃~15℃.

3. The liquid cooling system as described in claim 1, characterized in that, The evaporator includes a top cover, a biomimetic liquid distribution structure, and an evaporation phase change structure. The top cover and the evaporation phase change structure enclose a cavity. The biomimetic liquid distribution structure is disposed between the top cover and the evaporation phase change structure, so that the top cover, the biomimetic liquid distribution structure, and the evaporation phase change structure enclose a liquid inlet channel, a gas outlet channel, and a biomimetic liquid distribution area and an evaporation phase change area located and interconnected between the liquid inlet channel and the gas outlet channel. The liquid inlet channel is connected to the biomimetic liquid distribution area, and the gas outlet channel is connected to the evaporation phase change area. The top cover is provided with a liquid inlet that connects to the liquid inlet channel and an air outlet that connects to the air outlet channel. The liquid inlet forms the inlet of the evaporator, and the air outlet forms the outlet of the evaporator.

4. The liquid cooling system as described in claim 3, characterized in that, The evaporation phase change structure includes a base plate and multiple partitions. The multiple partitions are spaced apart on the base plate and arranged at intervals along the center of the base plate toward the edge of the base plate to form a first central region and multiple annular regions surrounding the first central region on the base plate. The biomimetic liquid distribution structure includes a central component and multiple branch components. The central component forms a second central region, which is connected to the first central region to form the liquid inlet channel. The multiple branch components are distributed at intervals along the outer periphery of the central component, and one end of each branch component is connected to the central component. The other end of each branch component extends toward the edge of the base plate. Each branch component has a branch region that is connected to the second central region. In this configuration, each branch region is connected to multiple annular regions to form the biomimetic liquid separation zone, extending from the center of the base plate to its edge. Multiple annular regions located between two adjacent branch members cooperate with the two adjacent branch members to form the evaporation phase change zone. The top cover, together with the outermost partition and the end of the multiple branch members furthest from the center member, forms the gas outlet channel.

5. The liquid cooling system as described in claim 4, characterized in that, The liquid inlet, the second central region, and the first central region are all located at the center of the evaporator and are arranged sequentially along the thickness direction of the evaporator. And / or, the top cover includes a top plate and a side plate disposed around the periphery of the top plate, the top plate being opposite to and spaced from the bottom plate, the side plate extending toward the bottom plate and connected to the bottom plate, the top plate being provided with the liquid inlet, and the side plate being provided with the air outlet; And / or, the plurality of said branch components and the central component are integrally formed; And / or, the hydraulic diameter D of each branch region near the end of the central member 中心 The thickness ranges from 0.1mm to 5mm. And / or, the hydraulic diameter D of each branch region at the end furthest from the central member 边缘 The thickness ranges from 0.5mm to 10mm. And / or, from the center of the base plate to the edge of the base plate, the cross-sectional dimension of each branch region gradually increases, and the hydraulic diameter increase rate γ of each branch region is 0.02~1; where γ=(D 边缘 -D 中心 ) / R, where R is the radius of the biomimetic liquid separation zone; And / or, the inner wall of each of the branch regions is provided with a hydrophobic layer; wherein the contact angle of the hydrophobic layer is >120°; And / or, the inner walls of the first central region and the plurality of annular regions are provided with a hydrophilic layer; wherein the contact angle of the hydrophilic layer is <30°.

6. The liquid cooling system as described in claim 4, characterized in that, The inner walls of the first central region and the plurality of annular regions are provided with a first recess structure, which is an array structure formed by the first recesses; wherein, the diameter of the first recess is 5μm~50μm, the depth of the first recess is 2μm~20μm, and the spacing between the first recesses is 10μm~100μm; and / or, from the center of the base plate to the edge of the base plate, the density of the first recesses gradually increases; and / or, from the center of the base plate to the edge of the base plate, the diameter of the first recesses gradually decreases. Alternatively, the inner walls of the first central region and the plurality of annular regions are provided with a porous structure, wherein the porous structure is an array structure formed by micropores; wherein the pore size of the micropores is 50nm~500nm; and / or, the porosity of the micropores is 30%~70%; and / or, the density of the micropores gradually increases from the center of the base plate to the edge of the base plate; and / or, the diameter of the micropores gradually decreases from the center of the base plate to the edge of the base plate.

7. The liquid cooling system as described in claim 1, characterized in that, Along the flow direction of the liquid cooling medium, the condenser forms at least two heat exchange sections, the at least two heat exchange sections including a first heat exchange section located on the inlet side of the condenser and a second heat exchange section located on the outlet side of the condenser. A first condensation channel is formed in the first heat exchange section, and the first heat exchange section is provided with a plurality of first fins. A second condensation channel is formed in the second heat exchange section, and the second heat exchange section is provided with a plurality of second fins. The first condensation channel is configured as a variable cross-section microchannel, and the hydraulic diameter of the first condensation channel gradually decreases along the flow direction of the liquid cooling medium. And / or, the density of the plurality of first fins gradually decreases along the flow direction of the liquid cooling medium; And / or, the inner wall of the first condensation channel is provided with a second pit structure, the second pit structure being an array structure formed by the second pits; wherein, the diameter of the second pit is 10μm~50μm, the depth of the second pit is 5μm~20μm, and the spacing between the second pits is 20μm~100μm. And / or, the second condensation channel is configured as a microchannel with an equal cross-section.

8. The liquid cooling system as described in claim 1, characterized in that, The detection component includes: Multiple temperature and pressure sensors are installed in the circulation pipeline, located respectively at the inlet side of the evaporator, the outlet side of the evaporator, and the outlet side of the condenser, for detecting the temperature and pressure of the liquid cooling medium. The multiple temperature and pressure sensors are communicatively connected to the control unit. A void fraction sensor is installed in the circulation pipeline and located at the outlet side of the evaporator or the inlet side of the condenser. It is used to detect the void fraction of the liquid cooling medium and is communicatively connected to the control unit.

9. The liquid cooling system as described in claim 8, characterized in that, The cavitation fraction sensor is a dielectric constant sensor, a capacitance tomography sensor, or an ultrasonic sensor. And / or, the detection component further includes a flow sensor, which is disposed in the circulation pipeline and located at the outlet side of the pump, for detecting the flow rate of the liquid cooling medium in the circulation pipeline, and the flow sensor is communicatively connected to the control unit; And / or, the detection component further includes a plurality of temperature sensors disposed on the surface of the heat source, the plurality of temperature sensors being arranged in an array along the flow direction of the liquid cooling medium for detecting the temperature of the surface of the heat source, and the plurality of temperature sensors being communicatively connected to the control unit.

10. The liquid cooling system as described in claim 1, characterized in that, The liquid storage unit has a gas phase separation chamber and a liquid phase separation chamber. The gas phase separation chamber is connected to the inlet of the condenser through a first pipeline, and the liquid phase separation chamber is connected to the inlet of the pump through the circulation pipeline. The liquid phase separation chamber is used to separate different working fluids. The liquid phase separation chamber includes multiple liquid phase chambers, the number of which corresponds one-to-one with the amount of the working fluid of the liquid cooling medium. Each liquid phase chamber is connected to the circulation pipeline through a second pipeline. The liquid storage unit also includes a flow control valve located in each of the second pipelines, and the flow control valve is communicatively connected to the control unit. And / or, the liquid storage unit further includes a one-way valve disposed in the first pipeline.

11. The liquid cooling system as described in claim 1, characterized in that, The evaporation assembly includes a plurality of evaporators for contact with the heat source, the plurality of evaporators being arranged in parallel, the outlet of the pump being connected to the inlet of the plurality of evaporators through the circulation pipeline, and the outlet of the plurality of evaporators being connected to the inlet of the condenser through the circulation pipeline; And / or, the performance parameters of the liquid cooling medium include temperature, pressure, and cavitation fraction; And / or, the control unit adopts a two-layer control architecture, the control unit includes a bottom-layer controller and an upper-layer optimizer, the bottom-layer controller controls the pump working fluid according to the performance parameters detected by the detection component, and the upper-layer optimizer dynamically calculates the target working fluid component concentration of the liquid cooling medium according to the temperature of the heat source and the performance of the liquid cooling medium, and transmits it to the bottom-layer controller.

12. A control method for a liquid cooling system as described in any one of claims 1 to 11, characterized in that, The control method includes: The temperature, pressure, and empty shot fraction of the current liquid cooling medium are acquired in real time by the detection component, and the real-time working fluid component concentration C_r of the liquid cooling medium is calculated based on the temperature, pressure, and empty shot fraction. The temperature of the heat source is acquired in real time by the detection component, and the target working fluid component concentration C_t of the liquid cooling medium is calculated based on the temperature of the heat source and the thermodynamic property data of the liquid cooling medium. Based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, the flow control valve is controlled to adjust the flow rate of different working fluids, thereby adjusting the real-time component concentration of the liquid medium in the circulation pipeline.

13. The control method for the liquid cooling system as described in claim 12, characterized in that, The step of acquiring the temperature of the heat source collected in real time by the detection component, and calculating the target working fluid component concentration C_t of the liquid cooling medium based on the temperature of the heat source and the thermodynamic property data of the liquid cooling medium includes: Acquire the temperature of the heat source in real time from the detection component; The surface temperature distribution curve T_h(x,t) of the heat source is generated based on the temperature of the heat source. Based on the surface temperature distribution curve T_h(x,t) of the heat source, and combined with the preset system energy efficiency optimization target, the ideal target working fluid phase change temperature glide curve T_gt(p,x,t) is calculated; where p is the system pressure, x is the spatial coordinate along the flow direction of the evaporator, and t is time; Based on the temperature glide curve T_gt(p,x,t), combined with the current system pressure p and the preset thermodynamic properties of the liquid cooling medium, the target working fluid component concentration C_t of the liquid cooling medium required to reach the temperature glide curve T_gt(p,x,t) is calculated in reverse.

14. The control method for the liquid cooling system as described in claim 12, characterized in that, The step of controlling the flow control valve to adjust the flow rate of different working fluids based on the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium, in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline, includes: Determine whether the deviation ΔC between the target working fluid component concentration C_t and the real-time working fluid component concentration C_r of the liquid cooling medium exceeds a preset threshold. If so, the flow control valve is used to adjust the flow rate of different working fluids in order to adjust the real-time component concentration of the liquid medium in the circulation pipeline; If not, cycle according to the current working fluid composition concentration of the liquid cooling medium.

15. An electronic device, characterized in that, The electronic device includes a liquid cooling system as claimed in any one of claims 1 to 11.

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