Flow guide type liquid cooling plate, detection method, equipment and storage medium

Abstract

The invention discloses a flow guide type liquid cooling plate, a detection method, equipment and a storage medium, and relates to the technical field of radiators. The liquid cooling plate comprises a liquid cooling plate shell, a segmented staggered flow channel structure arranged in the shell, and a flow guide assembly arranged at an end socket. Structural optimization is carried out on the basis of a traditional parallel flow channel radiator, an optimized structure and a flow guide plate optimized structure are designed by improving the flow channel configuration and additionally arranging the end socket flow guide plate, and it is verified through numerical simulation and sample piece experiments that the optimized structure is remarkably improved in the aspects of flow and heat transfer performance.

Description

Technical Field

[0001] This invention relates to the field of radiator technology, and in particular to a flow-guided liquid cooling plate, a testing method, an apparatus, and a storage medium. Background Technology

[0002] The automotive industry is currently actively promoting a transformation towards low-carbon, high-performance, and lightweight technologies, with the new energy vehicle industry being a key area for optimizing and upgrading the energy structure. As a core component of electric vehicles, the technological development of power batteries is of decisive significance. However, the performance, lifespan, and safety of lithium-ion batteries are highly sensitive to temperature. Temperature fluctuations in batteries are generally unavoidable, primarily due to environmental conditions and the heat generated during electrochemical reactions during charging and discharging. The operating temperature range for lithium-ion batteries should ideally be controlled between 15 and 35 °C, and the battery system must meet the requirement that the temperature difference between individual cells is no more than 5 °C to mitigate potential negative impacts on lithium-ion batteries in practical applications. With the continuous improvement of automotive performance indicators and driving range requirements, solving the battery cooling problem during rapid charging and discharging has become a key technological challenge in overcoming industry development bottlenecks.

[0003] To address this technological bottleneck, extensive research has been conducted, resulting in various thermal management optimization strategies. While existing solutions offer advantages in improving heat dissipation performance, inherent technical limitations remain. Cold plate heat exchangers, with their superior heat transfer coefficient, compact structure, and excellent temperature uniformity, have become a key research focus in the field of heat and mass transfer. Among these, the passive heat dissipation mode, which optimizes the liquid-cooled plate structure to achieve efficient heat conduction to the battery pack surface, has been proven to be a solution with significant engineering application value. Initially, rectangular parallel flow channel designs were primarily used, but with the continuous increase in battery power density, traditional structures can no longer meet increasingly stringent heat dissipation requirements, prompting the exploration of new optimization schemes. Summary of the Invention

[0004] The purpose of this invention is to provide a flow-guided liquid cooling plate, a detection method, an apparatus, and a storage medium, in order to solve or improve at least one of the above-mentioned technical problems.

[0005] To achieve the above objectives, the present invention provides the following solution: A flow-guided liquid cooling plate includes: a liquid cooling plate shell, a segmented staggered flow channel structure disposed inside the shell, and a flow guiding component disposed at the end cap; The segmented staggered flow channel structure includes an inlet section, a middle section, and an outlet section in sequence along the coolant flow direction; wherein, the middle section is provided with N ribs and N+1 flow channels, and the inlet section and the outlet section are each provided with M ribs and M+1 flow channels, where N < M, and N and M are both positive integers; The ribs in the intermediate section are staggered and non-aligned with the ribs in the inlet and outlet sections in the direction of flow channel extension, forming a gradual width transition zone between adjacent flow channels; the flow channel width W1 of the intermediate section is greater than the flow channel width W2 of the inlet and outlet sections, and the flow channel width changes smoothly and continuously along the flow direction within the transition zone; the cross-section of the ribs is rectangular, with the long side arranged along the flow direction, the rib height is consistent, and the rib spacing is gradient distributed along the flow direction, resulting in a local expansion of the flow channel cross-sectional area within the intermediate section; The flow guiding assembly includes multiple guide plates arranged along the width direction of the head. The curvature of the frontal surface and the installation angle of each guide plate are optimized by hydrodynamics. The guide plate located in the central region of the head has its maximum width position corresponding to the inlet centerline, which is used to guide the mainstream to diffuse evenly. The guide plates located on both sides are arranged at an acute angle to the flow direction to suppress the sidewall effect and eliminate flow dead zones. The height of each guide plate decreases from the center to both sides, which matches the inlet cross-sectional width distribution of the segmented flow channel structure, so as to realize the active distribution of coolant flow according to the flow channel requirements.

[0006] Optionally, the segmented staggered flow channel structure adopts a three-section design: the middle section is provided with 10 ribs and 11 flow channels, and the remaining two sections are each provided with 11 ribs and 12 flow channels; the ribs of the middle section are staggered with the ribs of the remaining two sections.

[0007] Optionally, the flow channel width of the middle section is 6 mm, and the flow channel width of the remaining two sections is 5 mm.

[0008] Optionally, the ribs are arranged in parallel and have a size of 25mm × 3mm.

[0009] Optionally, the flow guiding assembly includes 7 flow guiding plates, each of which is arranged symmetrically in two sections with the inlet center line as the axis of symmetry; wherein the middle flow guiding plate is peach-shaped and the other flow guiding plates are elliptical.

[0010] The present invention also provides a method for detecting a flow-guided liquid-cooled plate, comprising: A three-dimensional parametric model of the flow-guided liquid cooling plate was established in SpaceClaim and imported into Fluent Meshing for unstructured mesh generation. Local mesh refinement was performed on the ribs, flow channel boundaries, and guide plate areas. Based on computational fluid dynamics numerical simulation, a Realizable k-ε turbulence model was adopted, with the inlet set as a velocity inlet and the outlet as a pressure outlet. Flow and heat transfer simulations under multiple working conditions were carried out to obtain the flow field distribution, temperature field characteristics, pressure drop, heat transfer coefficient and Nusselt number. Based on the optimized structural parameters from the simulation, an aluminum base plate and cover plate were milled, an acrylic plate was laser-cut into a flow guide plate, and high-strength AB structural adhesive was used for sealing and assembly to prepare a flow-guided liquid cooling plate prototype. An integrated experimental platform was built, including a low-temperature constant temperature water bath, a gear flow meter, a digital differential pressure gauge, a peristaltic pump, a temperature data acquisition instrument, and a DC power supply. The inlet flow rate was adjusted by valves, and the flow and heat transfer performance of the sample was tested under set working conditions. Collect experimental data, including inlet and outlet temperatures, surface multi-point temperatures, pressure drop and flow rate, and calculate thermal resistance, average convective heat transfer coefficient and Nusselt number; The experimental data were compared and verified with the CFD simulation results. The overall heat dissipation performance and temperature uniformity of the liquid cooling plate were evaluated based on the comprehensive performance evaluation factor. The test report and structural optimization suggestions were output.

[0011] The present invention also provides an electronic device, including a memory and a processor, wherein the memory is used to store a computer program, and the processor runs the computer program to cause the electronic device to perform the flow-guided liquid-cooled plate detection method according to the above.

[0012] The present invention also provides a computer-readable storage medium storing a computer program that, when executed by a processor, implements the flow-guided liquid cooling plate detection method as described above.

[0013] According to specific embodiments provided by the present invention, the present invention discloses the following technical effects: This invention discloses a flow-guided liquid cooling plate, a detection method, an apparatus, and a storage medium. The liquid cooling plate includes a liquid cooling plate shell, a segmented staggered flow channel structure disposed inside the shell, and a flow guiding component disposed at the end cap. This invention optimizes the structure of a traditional parallel flow channel radiator by improving the flow channel configuration and adding a flow guiding plate to the end cap. Optimized structures and flow guiding plate optimized structures are designed respectively. Numerical simulations and sample experiments verify that the optimized structures significantly improve flow and heat transfer performance. Attached Figure Description

[0014] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments 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 these drawings without creative effort.

[0015] Figure 1 This is a schematic diagram of the flow channel structure of Type 1 in this embodiment; Figure 2This is a schematic diagram of the flow channel structure of Type 2 in this embodiment; Figure 3 This is a schematic diagram of the flow channel structure of Type 3 in this embodiment; Figure 4 This is a mesh partitioning diagram for Type 1 to Type 3 in this embodiment; Figure 5 This is a diagram of the experimental system in this embodiment. Detailed Implementation

[0016] 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 some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0017] The purpose of this invention is to provide a flow-guided liquid cooling plate, a detection method, an apparatus, and a storage medium, in order to solve or improve at least one of the above-mentioned technical problems.

[0018] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0019] In a first aspect, the present invention provides a flow-guided liquid cooling plate, including a liquid cooling plate shell, a segmented staggered flow channel structure disposed inside the shell, and a flow guiding component disposed at the end cap.

[0020] The segmented staggered flow channel structure includes an inlet section, a middle section, and an outlet section in sequence along the coolant flow direction; wherein, the middle section is provided with N ribs and N+1 flow channels, and the inlet section and the outlet section are each provided with M ribs and M+1 flow channels, where N < M, and N and M are both positive integers.

[0021] The ribs in the intermediate section are staggered and non-aligned with the ribs in the inlet and outlet sections in the direction of flow channel extension, forming a gradual width transition zone between adjacent flow channels. The flow channel width W1 in the intermediate section is greater than the flow channel width W2 in the inlet and outlet sections, and the flow channel width changes smoothly and continuously along the flow direction within the transition zone. The ribs have rectangular cross-sections with their long sides arranged along the flow direction, consistent rib heights, and gradient distribution of rib spacing along the flow direction, resulting in a local expansion of the flow channel cross-sectional area within the intermediate section.

[0022] The flow guiding assembly includes multiple guide plates arranged along the width direction of the head. The curvature of the frontal surface and the installation angle of each guide plate are optimized by hydrodynamics. The guide plate located in the central region of the head has its maximum width position corresponding to the inlet centerline, which is used to guide the mainstream to diffuse evenly. The guide plates located on both sides are arranged at an acute angle to the flow direction to suppress the sidewall effect and eliminate flow dead zones. The height of each guide plate decreases from the center to both sides, which matches the inlet cross-sectional width distribution of the segmented flow channel structure, so as to realize the active distribution of coolant flow according to the flow channel requirements.

[0023] As a specific implementation method, this embodiment optimizes the structure of a traditional parallel-channel radiator (Type 1). By improving the channel configuration and adding baffles to the end caps, optimized structures (Type 2) and baffle-optimized structures (Type 3) were designed. Numerical simulations were performed using Fluent 2022R1, and the flow field distribution, temperature field characteristics, pressure drop, heat transfer coefficient, and Nusselt number of the three models were compared and analyzed. The results show that the optimized structure significantly improves flow and heat transfer performance. Finally, the consistency between the simulation results and measured data was verified through sample preparation and experimental platform construction.

[0024] To compare and analyze the performance differences between the optimized model and the traditional parallel channel model in terms of heat transfer and flow characteristics, this embodiment designs a traditional parallel channel model and defines it as Type 1. Figure 1 The diagram shown is a schematic of the Type 1 structure generated using SpaceClaim software. The Type 1 structure consists of three parts: a heat source, a base plate, and a cover plate. The heat source dimensions are 150mm × 92mm × 10mm; the base plate dimensions are 164mm × 97mm × 5mm, with a flow channel depth of 3mm and a wall thickness of 2mm. Figure 1 As shown, the flow channel system comprises 12 parallel equal-width flow channels (5mm wide, 100mm long) and 11 ribs (3mm wide), with inlet and outlet dimensions of 2.5mm × 3mm and a length of 25mm. The cover plate matches the bottom plate in size and has a thickness of 2mm.

[0025] To improve the flow uniformity and heat transfer performance of the radiator, this embodiment optimizes the flow channel structure, transforming the parallel flow channel into a segmented staggered flow channel, and constructs an optimized flow channel structure model (Type 2). For example... Figure 2 As shown, Type 2 maintains the same external dimensions as Type 1, with only modifications to the internal flow channel structure. This structure employs a three-section design: the middle section contains 11 flow channels and 10 ribs, while the other two sections each have 12 flow channels and 11 ribs. Except for the two sides of the middle section, where the flow channel width is 6mm, the width of the remaining flow channels is 5mm. All ribs are arranged in parallel and have a uniform size of 25mm × 3mm.

[0026] To further improve the uniformity of coolant flow in the radiator, based on the optimized flow channel structure, seven guide vanes of different shapes and sizes were added to the end cap to create an optimized flow channel structure with guide vanes, called Type 3. Figure 3 This is a schematic diagram of the flow channel structure for Type 3. The flow channel structure of this model is exactly the same as that of Type 2, except that seven guide vanes are added at the end cap. The guide vanes are symmetrical about the inlet centerline, with both ends being mutually symmetrical. The middle guide vane is peach-shaped, while the others are elliptical.

[0027] As a second aspect, the present invention also provides a method for detecting a flow-guided liquid-cooled plate, comprising: A three-dimensional parametric model of the flow-guided liquid cooling plate was established in SpaceClaim and imported into Fluent Meshing for unstructured mesh generation. Local mesh refinement was performed on the ribs, flow channel boundaries, and guide plate areas.

[0028] Based on computational fluid dynamics numerical simulation, a Realizable k-ε turbulence model was adopted, with the inlet set as a velocity inlet and the outlet as a pressure outlet. Flow and heat transfer simulations under multiple operating conditions were carried out to obtain the flow field distribution, temperature field characteristics, pressure drop, heat transfer coefficient, and Nusselt number.

[0029] Based on the optimized structural parameters obtained from simulation, an aluminum base plate and cover plate were milled, an acrylic plate was laser-cut into a flow guide plate, and high-strength AB structural adhesive was used for sealing and assembly to prepare a flow-guided liquid cooling plate prototype.

[0030] An integrated experimental platform was built, including a low-temperature constant temperature water bath, a gear flow meter, a digital differential pressure gauge, a peristaltic pump, a temperature data acquisition instrument, and a DC power supply. The inlet flow rate was adjusted by valves, and the flow and heat transfer performance of the sample was tested under set operating conditions.

[0031] Collect experimental data, including inlet and outlet temperatures, surface multi-point temperatures, pressure drop and flow rate, and calculate thermal resistance, average convective heat transfer coefficient and Nusselt number.

[0032] The experimental data were compared and verified with the CFD simulation results. The overall heat dissipation performance and temperature uniformity of the liquid cooling plate were evaluated based on the comprehensive performance evaluation factor. The test report and structural optimization suggestions were output.

[0033] As a specific implementation method, this embodiment presents a numerical model of the flow-guided liquid cooling plate constructed above. The specific process includes: 1. Grid division The model was first created in SpaceClaim and then imported into Fluent Meshing for mesh generation. The models designed in this embodiment all use unstructured meshes. The ribs, flow channel boundaries, and guide vanes were locally refined. The skewness of the generated surface meshes is less than 0.7, and the orthogonality quality of the volume meshes is greater than 0.15, indicating good mesh quality. Figure 4 It is a grid partitioning diagram from Type 1 to Type 3.

[0034] 2. Basic Assumptions and Governing Equations This step describes the fluid model using the incompressible Navier-Stokes fluid equations. Therefore, the following assumptions are made about the mathematical model: (1) The fluid is a steady-state, incompressible, single-phase fluid.

[0035] (2) The energy balance equation does not consider the viscous dissipation inside the fluid.

[0036] (3) The effects of surface tension and volume forces on the model are not considered.

[0037] (4) The heat dissipation methods are only heat conduction and heat convection, and the influence of radiation on the radiator is ignored.

[0038] (5) The properties of solid materials are constant, while the thermal properties of fluid materials change with temperature.

[0039] 3. Initial conditions and boundary conditions All numerical simulations involved in this embodiment were performed using Fluent 2022 R1. Water was used as the coolant throughout the process, aluminum was used as the solid material for the radiator, and copper was used as the solid material for the heating plate. The Coupled method was used to couple velocity and pressure calculations. The diffusion and convection terms in both the energy and momentum equations were discretized using a second-order upwind spatial scheme. The Realizable k-epsilon model was selected for the numerical simulation. During the Fluent solution process, the standard residuals of the velocity and continuity equations in the xyz directions were set to 10⁻⁵, the standard residual of the energy equation was 10⁻⁶, and the standard residuals of k and epsilon were set to 10⁻³ by system default. Since Type 1, Type 2, and Type 3 have the same inlet size, the Reynolds number (Re) is also the same under different flow rates. Table 1 shows the corresponding Reynolds number for different flow rates. The inlet flow velocity range involved in this embodiment is 0.2 m / s to 1.5 m / s. When the flow velocity is less than 0.8 m / s, the fluid flow is laminar. When the flow velocity is between 0.8 m / s and 1.5 m / s, the fluid flow is transitional.

[0040] Table 1. Radiator inlet velocity and Reynolds number

[0041] The radiator inlet is a velocity inlet, therefore the boundary conditions can be expressed as: In the above formula The fluid inlet velocity is... This refers to the fluid inlet temperature.

[0042] Since the radiator outlet is a pressure outlet, its boundary conditions are as follows: The boundary conditions at the interface between a solid and a liquid are: A uniform and stable heat source is added to the bottom surface of the radiator, and the other surfaces are considered as insulating surfaces: In the formula Indicates heat flux, This indicates the heating power of the heat source.

[0043] Volumetric flow rate Q Represented as: Where L represents the inlet width and H represents the inlet height.

[0044] 4. Relevant parameters The Reynolds number (Re) is an important dimensionless number in fluid mechanics, used to characterize the relative strength of inertial and viscous forces in fluid flow, thereby determining the flow state. When the Re number is less than 2000, it is laminar flow; when the Re number is between 2000 and 4000, it is moderate flow; and when the Re number is greater than 4000, it is turbulent flow.

[0045] in, υ For inlet velocity; ρ For fluid density; D h The hydraulic diameter; μ This refers to the fluid dynamic viscosity.

[0046] The convective heat transfer coefficient is a physical quantity that describes the convective heat transfer capacity between a fluid and a solid surface. It represents the heat transferred between the fluid and the solid per unit area per unit time due to the temperature difference. According to Newton's law of cooling, its expression is: in, Q w Indicates the total input power. A eff Indicates the effective heat exchange area. The average temperature of the fluid at the interface with the wall. The average temperature of the fluid is expressed by the following formula: in, The temperature of the inlet fluid. This refers to the outlet fluid temperature.

[0047] The Nu number is an important dimensionless number in heat transfer, used to characterize the ratio of convective heat transfer intensity to conductive heat transfer intensity between a fluid and a solid surface. Its formula is as follows: in, The average convective heat transfer coefficient, The hydraulic diameter, This refers to the thermal conductivity of the coolant.

[0048] Thermal resistance is a physical quantity that measures the ability of a material or interface to impede heat transfer. It is an important indicator for evaluating the heat exchange performance of a radiator, and its formula is as follows: in, T surf,max This indicates the highest temperature on the surface of the radiator. q Represents heat flux density, A This indicates the area of ​​the heat source.

[0049] The Comprehensive Performance Evaluation Factor (PEC) is used in the radiator design process to balance the contradictions between parameters such as the overall heat transfer coefficient and pressure drop, forming a single quantitative evaluation index to assess the overall heat dissipation performance of the radiator. Its calculation formula is as follows: in, and These represent the Nu number and friction coefficient of the reference model, respectively. The expression is: in, L The characteristic length of the flow channel. The average flow velocity of the fluid.

[0050] 5. Mesh independence verification In this embodiment, all three models feature parallel flow channels with rectangular shapes. Mesh independence is verified using Type 1 as an example. To test mesh independence, a cross-section is set at the end of the flow channel, and the temperature standard deviation and relative error of this plane are analyzed and calculated under different mesh numbers. The four mesh numbers for Type 1 are 713112, 1497475, 1743857, and 2312776. Table 2 lists the temperature standard deviation and relative error corresponding to different mesh numbers for this model. As shown in Table 2, when the mesh number is greater than the selected standard, the maximum relative error of the temperature relative standard deviation is only 0.56%, and the maximum relative error of the cross-sectional average temperature is only 0.066%, proving that the mesh number has little impact on the numerical simulation results.

[0051] Table 2 Mesh independence verification

[0052] 6. Model Validation The experiment demonstrates the variation of the maximum surface temperature difference and average temperature with flow velocity under the conditions of an inlet temperature of 20℃ and a heating power of 90W. The experimental and simulation results show the same trend, with the surface average temperature curves (except for Type 1) basically overlapping. The deviation in the experimental values ​​for Type 1 stems from its poor temperature uniformity, and the fact that the experiment only used the average value of 9 measuring points, leading to increased error. Similarly, the difference in the maximum temperature difference under high and low flow velocities is also due to the limited number of measuring points, which failed to fully capture extreme temperatures. These results indicate that the simulation results are reliable in the analysis of flow and temperature uniformity.

[0053] A prototype experiment was conducted on the constructed flow-guided liquid cooling plate. The specific process included: 1. Experimental Principles and Equipment like Figure 5As shown in the figure, this is the experimental system diagram for this experiment. The entire experimental setup mainly consists of a low-temperature constant-temperature water bath (DHC-05-A), a gear flow meter (JCW-04), valves, an optimized structure radiator, a digital differential pressure gauge (DXL-DMG512B), a peristaltic pump, a temperature data acquisition instrument (RIGOL-M300), and a DC power supply (UTP1310). The low-temperature constant-temperature water bath (DHC-05-A) provides a constant temperature coolant to the experimental system, ensuring that the temperature of the coolant flowing into the experimental setup is maintained at the set 15 ℃, 20 ℃, and 25 ℃. A peristaltic pump is placed inside the water bath to provide pumping power for the coolant, causing it to flow into the optimized structure radiator and finally back into the water bath. The cooling function of the water bath returns the coolant to the set temperature, completing the experimental cycle. The valves in the setup control the inlet flow rate, which is then measured by the gear flow meter and converted into a flow velocity that can be controlled within the range of 0.2 m / s to 1.5 m / s. The optimized structure radiator is connected to digital differential pressure gauges (DXL-DMG512B) at both ends to measure the pressure loss of the coolant flowing through the radiator.

[0054] Nine measuring points were set on the optimized radiator surface, with their relative positions within the radiator. Holes were drilled at the inlet and outlet hoses, and two T-type thermocouples were inserted, centered, and then secured with high-strength AB structural adhesive to ensure pipe sealing. These thermocouples are used to measure the actual inlet and outlet temperatures. Each measuring point had a T-type thermocouple, the other end of which was connected to a temperature data acquisition instrument (RIGOL-M300) to obtain the temperature at each point, thus characterizing the radiator's temperature distribution. A copper heating plate was installed on the lower surface of the radiator, with three holes on its wide side through which three heating rods were placed. A layer of silicone grease was evenly applied to the outer surface of the heating rods to reduce contact thermal resistance with the heating plate. A layer of silicone grease was also evenly applied between the radiator and the heating plate to improve heat conduction and reduce heat loss. The three heating rods were connected in parallel, the other end of which was connected to a DC power supply (UTP1310). Controlling the current or voltage controlled the heat source power.

[0055] The optimized heat sink was designed using SpaceClaim, and then milled to obtain the final product. The material used for milling was aluminum. Type 1 and Type 2 mainly consist of a base plate and a cover plate, while Type 3, in addition to the above structures, consists of a flow guide plate made of acrylic sheet. Before the experiment, the above structures were firmly glued together with film, and high-strength AB structural adhesive was used for edge sealing to ensure the airtightness of the structure.

[0056] 2. Deterministic Analysis In the experiment, the operating parameters such as pressure drop, measuring point temperature, inlet flow rate, and heating power, as well as the accuracy of the processing technology, and the geometric parameters of the model are all uncertain factors.

[0057] Table 3 Uncertainty Analysis

[0058] Table 3 shows the directly obtained uncertainties, while the parameters used in the analysis, such as thermal resistance, convective heat transfer coefficient, and Nu number, can be calculated using the following formulas: Taking Type 3 as an example, with a heating power of 90W, a fluid inlet temperature of 20℃, and a flow velocity of 0.6m / s, the uncertainties of thermal resistance, convective heat transfer coefficient, and Nu number are 9.43%, 9.40%, and 4.89%, respectively.

[0059] Finally, the following experimental results can be obtained through the above simulation and experiment: Due to problems such as uneven fluid distribution, poor temperature uniformity, and low heat transfer performance in automotive radiators, this embodiment designs two optimized models based on the traditional parallel flow channel radiator (Type 1): a segmented staggered flow channel radiator model (Type 2) and a staggered segmented radiator model with guide vanes (Type 3). Using ANSYS Fluent 2022R1 software and an experimental platform, numerical simulations and experimental comparisons were conducted to analyze the temperature uniformity, fluid uniformity, and heat transfer performance of the three radiator models, seeking the optimal structural radiator model. The following main conclusions were obtained: (1) After the heat source heating power and fluid inlet temperature are changed, the pressure drop, thermal resistance, Nu number and PEC parameters do not change and have almost no effect on the heat exchange performance of the radiator.

[0060] (2) The temperature uniformity of the radiator increases with the increase of the fluid inlet velocity, and the higher the velocity, the more obvious the optimization effect of Type 3 and Type 2 compared to Type 1. The temperature uniformity is maximized when the velocity is 1.5 m / s. The average surface temperature of Type 3 is 1.309 ℃ lower than that of Type 1 and 0.819 ℃ lower than that of Type 2. The maximum surface temperature difference of Type 3 is 2.656 ℃, which is 1.734 ℃ lower than that of Type 1 and 0.964 ℃ lower than that of Type 1. Therefore, Type 3 has the best temperature uniformity.

[0061] (3) The heat transfer performance of the radiator increases with the increase of the fluid inlet velocity. The optimization effect is most obvious when the flow velocity is 1.5 m / s. The thermal resistance of Type 3 is 38.78% and 26.83% lower than that of Type 1 and Type 2, respectively, while the thermal resistance of Type 2 is 16.32% lower than that of Type 1. The heat transfer coefficient of Type 3 is 142.15% and 90.91% higher than that of Type 1 and Type 2, respectively, and the Nu number is 141.93% and 90.9% higher, respectively. The heat transfer coefficient and Nu number of Type 2 are both 26.72% higher than those of Type 1. Therefore, Type 3 has the best heat transfer effect.

[0062] (4) For Type 3, PEC3-1 and PEC3-2 are greater than 1 for both Type 1 and Type 2 under all flow rate conditions. For Type 2, PEC2-1 is greater than 1 only under flow rates greater than or equal to 0.8 m / s. This indicates that the optimization effect of Type 3 has a significant improvement on fluid uniformity, temperature uniformity, and heat transfer performance, while the optimization of Type 2 only shows improvement under limited conditions. Therefore, Type 3 is more applicable to practical engineering applications.

[0063] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. The same or similar parts between the various embodiments can be referred to each other.

[0064] This embodiment uses specific examples to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only for the purpose of helping to understand the core ideas of the present invention; at the same time, for those skilled in the art, there will be changes in specific implementation methods and application scope based on the ideas of the present invention. In summary, the content of this specification should not be construed as a limitation of the present invention.

Claims

1. A flow-guided liquid cooling plate, characterized by, The application relates to a liquid cooling plate, which comprises a liquid cooling plate shell, a segmented staggered flow channel structure arranged in the shell, and a flow guide assembly arranged at a head. The segmented staggered flow channel structure comprises an inlet section, an intermediate section and an outlet section in sequence along a cooling liquid flow direction; the intermediate section is provided with N rib columns and N+1 flow channels, and the inlet section and the outlet section are each provided with M rib columns and M+1 flow channels, wherein N The rib columns of the intermediate section are staggered and non-aligned with the rib columns of the inlet section and the outlet section in the flow channel extension direction, so that a width gradually changing transition zone is formed between adjacent flow channels; the flow channel width W1 of the intermediate section is greater than the flow channel width W2 of the inlet section and the outlet section, and the flow channel width changes smoothly and continuously in the transition zone along the flow direction; the cross section of the rib column is rectangular, the long side is arranged along the flow direction, the rib column height is consistent, and the rib column spacing is gradient-distributed along the flow direction, so that the flow channel cross section is locally enlarged in the intermediate section; The flow guide assembly comprises a plurality of flow guide plates arranged along the width direction of the head, the curvature and installation inclination of each flow guide plate are optimized through fluid dynamics, wherein the maximum width position of the flow guide plate located in the center area of the head corresponds to the inlet center line, and is used for guiding the uniform diffusion of the main flow; the long axis of the flow guide plate located on both sides is arranged at an acute angle with the flow direction, and is used for inhibiting the edge wall effect and eliminating the flow dead zone; the height of each flow guide plate decreases from the center to both sides, and matches the inlet cross section width distribution of the segmented flow channel structure, so that the cooling liquid flow is actively distributed according to the flow channel demand. The segmented staggered flow channel structure adopts a three-section design: the intermediate section is provided with 10 rib columns and 11 flow channels, and the remaining two sections are each provided with 11 rib columns and 12 flow channels; the rib columns of the intermediate section are staggered with the rib columns of the remaining two sections.

2. The flow-guided liquid cooling plate of claim 1, wherein, The flow channel width of the intermediate section is 6mm, and the flow channel width of the remaining two sections is 5mm.

3. The flow-guided liquid cooling plate of claim 2, wherein, The rib columns are all arranged in parallel, and the size is 25mm*3mm.

4. The flow-guided liquid cooling plate of claim 2, wherein, The flow guide assembly comprises seven flow guide plates, each of which is symmetrical to the inlet center line, and the two sections are arranged symmetrically; wherein the intermediate flow guide plate is in the shape of a peach, and the remaining flow guide plates are in the shape of an ellipse.

5. The flow-guided liquid cooling board according to claim 1, characterized by, The application also discloses a preparation method of the liquid cooling plate. 6.A flow-guided liquid cooling plate detection method, characterized in that, A three-dimensional parameterized model of the flow guide type liquid cooling plate is established in SpaceClaim, and is imported into Fluent Meshing for non-structured grid division, and local grid encryption is carried out on the rib columns, flow channel boundaries and flow guide plate regions; Based on the computational fluid dynamics numerical simulation method, a Realizable k-epsilon turbulent flow model is adopted, the inlet is set as a velocity inlet, and the outlet is set as a pressure outlet, flow and heat transfer simulation under multiple working conditions is carried out, and flow field distribution, temperature field characteristics, pressure drop, heat exchange coefficient and Nusselt number are obtained; According to the structure parameters optimized through simulation, an aluminum bottom plate and a cover plate are processed through milling, an acrylic plate is laser cut to form a flow guide plate, and high-strength AB structural glue is used for sealing and assembly, so that a flow guide type liquid cooling plate sample is prepared. ​ An integrated experimental platform is built, including a low-temperature constant-temperature water tank, a spur gear flowmeter, a digital differential pressure gauge, a peristaltic pump, a temperature data acquisition instrument and a direct current power supply. The inlet flow is adjusted by a valve, and the flow and heat transfer performance of the sample are tested under the set working condition. Experimental data, including inlet and outlet temperatures, surface multi-point temperatures, pressure drop and flow rate, are collected, and thermal resistance, average convective heat transfer coefficient and Nusselt number are calculated. The experimental data are compared with the CFD simulation results for verification, and the overall heat dissipation performance and temperature uniformity of the liquid cooling plate are evaluated based on the comprehensive performance evaluation factor. A detection report and structure optimization suggestions are output.

7. An electronic device, comprising: The electronic device includes a memory and a processor. The memory is used to store a computer program, and the processor runs the computer program to make the electronic device execute the flow-guided liquid cooling plate detection method according to any one of claims 1-5.

8. A computer-readable storage medium, characterized in that, The computer program is stored in the memory and is executed by the processor to realize the flow-guided liquid cooling plate detection method according to any one of claims 1-5.

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