Flow channel design method, light source heat dissipation liquid cooling plate and semiconductor light source

Abstract

Embodiments of the present application provide a flow channel design method, a light source heat dissipation liquid cooling plate and a semiconductor light source, and relate to the technical field of semiconductor light sources. The flow channel design method comprises: determining a total target pressure drop of a liquid cooling plate system, including a first target pressure drop generated by a liquid cooling plate body and a second target pressure drop corresponding to a heat generating module cooled by the liquid cooling plate body; determining a flow channel type according to the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path, determining the proportion of the frictional pressure drop and the local pressure drop, and determining the design target values of the two according to the total target pressure drop and the proportion; under a preset upper limit flow condition, the frictional pressure drop and the local pressure drop are calculated respectively to determine whether the design target values are met; a corresponding relationship between the flow channel corner geometric parameters and the pressure drop values is established, and the minimum allowable angle and the minimum allowable fillet radius are determined based on the local pressure drop design target value. The present application can realize low flow resistance flow channel design with controllable pressure drop, reduce the load of the water cooling machine, ensure the heat dissipation flow, and improve the heat dissipation efficiency.

Description

Technical Field

[0001] This invention relates to the field of semiconductor light source technology, and more specifically, to a flow channel design method, a light source heat dissipation liquid cooling plate, and a semiconductor light source. Background Technology

[0002] Under high-power operation, semiconductor light sources generate enormous heat power density from core components such as the primary and secondary heat-generating devices, requiring efficient heat dissipation through liquid cooling plates. The flow channel design of the liquid cooling plate directly affects heat dissipation performance and system energy consumption, with voltage drop being one of the key indicators for evaluating the quality of the flow channel design.

[0003] However, the liquid cooling plate flow channel design lacks systematic planning for pressure drop. In the early stages of design, the total pressure drop was not decomposed into each component, nor was the contribution ratio of pressure drop along the flow path and local pressure drop distinguished. As a result, it is impossible to accurately locate the specific location and cause of excessive pressure drop during the design process, leading to excessively high local pressure drop, which increases the load on the water chiller, reduces the flow rate that the water chiller can achieve, is not conducive to heat dissipation, and results in low heat dissipation efficiency. Summary of the Invention

[0004] The present invention aims to provide a flow channel design method, a liquid cooling plate for heat dissipation of the light source, and a semiconductor light source, which can precisely control the flow channel pressure drop, thereby reducing the load on the water chiller, ensuring heat dissipation flow, and improving heat dissipation efficiency.

[0005] The embodiments of the present invention can be implemented as follows: In a first aspect, the present invention provides a flow channel design method applied to a liquid cooling system, the liquid cooling system including a liquid cooling plate and a heating module, comprising the following steps: Determine the total target pressure drop of the liquid cooling plate system, including a first target pressure drop generated by the liquid cooling plate body and a second target pressure drop corresponding to the heat-generating module cooled by the liquid cooling plate body, wherein the liquid cooling system includes the liquid cooling plate body; Based on the ratio of the equivalent hydraulic diameter of the flow channel to the total flow length of the liquid cooling plate system, the flow channel type is determined, and the ratio of friction pressure drop and local pressure drop is determined based on the flow channel type. The design target values ​​of friction pressure drop and local pressure drop are determined based on the total target pressure drop and the ratio. Under the preset flow rate limit condition, the friction drop and local pressure drop of the flow channel are calculated respectively, and it is determined that the friction drop and local pressure drop meet the corresponding design target values ​​respectively; Establish the correspondence between the geometric parameters of the flow channel corner and the pressure drop value. Based on the design target value of the local pressure drop, determine the minimum allowable angle and the minimum allowable fillet radius of the flow channel corner.

[0006] In an optional implementation, when the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path is greater than or equal to a preset threshold, the flow channel type is determined to be a long pipe, the pressure drop ratio along the flow path is determined to be 90%, and the local pressure drop ratio is determined to be 10%. When the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path is less than the preset threshold, the flow channel type is determined to be a short pipe, and the pressure drop ratio along the flow path and the local pressure drop ratio are determined to be 50% respectively.

[0007] In an optional implementation, the correspondence between the geometric parameters of the flow channel angle and the pressure drop value is established, including: Based on the same turning angle, obtain the pressure drop values ​​corresponding to flow channels with different fillet radii, and determine the correspondence between fillet radius and pressure drop; Based on the same fillet radius, obtain the pressure drop values ​​corresponding to different turning angles, and determine the correspondence between the turning angle and the pressure drop.

[0008] In a second aspect, the present invention provides a light source heat dissipation liquid cooling plate, designed based on the flow channel design method described in any of the foregoing embodiments, comprising a plate body, wherein the plate body is provided with a flow channel system for cooling multiple heat-generating devices; The flow channel system includes: Main channel, used for introducing coolant; Multiple sub-channels are connected to the main channel, and the sub-channels are used to cool the heat-generating device.

[0009] In an optional embodiment, the heating device includes at least two first heating devices and one second heating device, and the sub-channel includes a first sub-channel for cooling the first heating devices and a second sub-channel for cooling the second heating devices. A first layer, a second layer, and a third layer of different heights are provided along the thickness direction of the plate. Two first sub-flow channels are respectively provided on the first layer and the third layer. A second sub-flow channel is provided on the second layer, which is located between the first layer and the third layer.

[0010] In an optional embodiment, the second sub-channel includes two main channels and a plurality of branch channels connected between the two main channels, and at least one of the main channels is in communication with the main channel. Along the flow direction of the coolant in the main channel, the cross-sectional area of ​​the main channel gradually decreases, and the cross-sectional area of ​​the branch channel gradually decreases.

[0011] In an optional embodiment, the ratio of the maximum to the minimum cross-sectional area of ​​the main channel is 1.5:1 to 3:1; the ratio of the maximum to the minimum cross-sectional area of ​​the branch channel is 1.5:1 to 3:1.

[0012] In an optional embodiment, a flow-guiding protrusion is provided on the inner wall of the main channel away from the branch channel, and the flow-guiding protrusion is inclined toward the flow direction of the coolant.

[0013] In an optional embodiment, the plurality of branch channels are spaced apart, and the distance between two adjacent branch channels gradually increases along the flow direction of the coolant in the main channel.

[0014] Thirdly, the present invention provides a semiconductor light source, including a light source heat dissipation liquid cooling plate as described in any of the foregoing embodiments.

[0015] The beneficial effects of the liquid cooling system flow channel design method, the light source heat dissipation liquid cooling plate, and the semiconductor light source provided in this invention include: The flow channel design method for the liquid cooling system provided in this invention determines the total target pressure drop of the liquid cooling plate system and rationally allocates the total target pressure drop into a first target pressure drop of the liquid cooling plate body and a second target pressure drop corresponding to the heating module. This avoids the problem of excessively high local pressure drops caused by unreasonable pressure drop allocation. By determining the flow channel type based on the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path, and accordingly determining the proportion of friction loss and local pressure drop and setting design target values, the contribution ratio of friction loss and local loss can be accurately distinguished, clarifying the key direction for pressure drop optimization. By designing the flow channel under the preset flow rate upper limit condition, the method further improves the flow channel design. Verifying the pressure drop along the flow path and the local pressure drop ensures that each pressure drop component meets the design objectives, avoiding design iterations caused by general judgments after traditional overall simulation. By establishing a quantitative correspondence between the geometric parameters of different flow channel corners and the pressure drop values, the minimum allowable angle and minimum allowable fillet radius of the flow channel corners can be determined. This effectively reduces the local pressure drop while ensuring the flexibility of the heat dissipation flow channel layout, reduces the load on the water chiller, ensures that the water chiller can achieve a high flow rate, improves the heat dissipation efficiency of the first and second heat-generating devices, and facilitates the structural design freedom when multiple pump modules are used in series. Attached Figure Description

[0016] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0017] Figure 1 This is a schematic diagram of the structure of the heat dissipation liquid cooling plate for the light source provided in this embodiment.

[0018] Icons: 100 - Light source heat dissipation liquid cooling plate; 10 - Main flow channel; 11 - First sub-flow channel; 12 - Second sub-flow channel; 121 - Main flow channel; 122 - Guide protrusion; 123 - Branch flow channel; 13 - Flow channel corner. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, 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. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0020] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention.

[0021] It should be noted that similar labels and letters in the following figures indicate similar items. Therefore, once an item is defined in one figure, it does not need to be further defined and explained in subsequent figures.

[0022] In the description of this invention, it should be noted that if terms such as "upper," "lower," "inner," or "outer" are used to indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, or the orientation or positional relationship in which the product of this invention is usually placed, they are only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this invention.

[0023] Furthermore, the terms "first" and "second" are used only to distinguish descriptions and should not be interpreted as indicating or implying relative importance.

[0024] It should be noted that, where there is no conflict, the features in the embodiments of the present invention can be combined with each other.

[0025] Example 1 This invention provides a flow channel design method for a liquid cooling system, used to design the flow channel system of a high-power light source heat dissipation liquid cooling plate, so as to reduce the flow channel pressure drop and improve the heat dissipation efficiency.

[0026] The flow channel design method specifically includes the following steps: Target pressure drop decomposition steps: Determine the total target pressure drop of the liquid cooling plate system, including the first target pressure drop generated by the liquid cooling plate body and the second target pressure drop corresponding to at least one heat-generating module cooled by the liquid cooling plate body.

[0027] It is understandable that pressure drop is the pressure lost by the coolant flowing within the liquid cooling plate system.

[0028] The total target pressure drop is determined by combining the available head of the water chiller and the pressure drop loss of the water supply pipeline. Specifically, the rated head of the water chiller is first obtained, and the total pressure drop of the water supply and return pipelines at the operating flow rate is deducted. The remaining pressure drop is the total target pressure drop allowed by the liquid cooling plate system. Then, the total target pressure drop is decomposed into a first target pressure drop borne by the liquid cooling plate itself and a second target pressure drop borne by each heat dissipation module. For example, when the liquid cooling plate is connected to three heat dissipation devices, the total target pressure drop d must satisfy d ≥ a1 + 3 × a2, where a1 is the first target pressure drop of the liquid cooling plate itself and a2 is the second target pressure drop of a single heat dissipation device module.

[0029] Specifically, the second target pressure drop is the pressure drop required by the heating module at the rated flow rate, which can be obtained through simulation calculation or actual testing based on the flow channel structure of the heating module. For example, when the liquid cooling plate body is connected to three pump source modules, the second target pressure drop a2 of each pump source module can be determined in advance as 0.07MPa through simulation or testing.

[0030] The first target pressure drop is the remaining value after deducting all second target pressure drops from the total target pressure drop. For example, if the total target pressure drop d is 0.26 MPa, then the first target pressure drop a1 of the liquid cooling plate body is ≤ d. 3 × a² = 0.26 3 × 0.07 = 0.05 MPa.

[0031] By decomposing the target pressure drop, the upper limit of the pressure drop of each component can be clearly defined in the early stage of design, avoiding the problem of excessive local pressure drop caused by unreasonable pressure drop distribution, and providing clear quantitative constraints for subsequent flow channel design.

[0032] Pressure drop estimation steps: Based on the ratio of the equivalent hydraulic diameter of the flow channel to the total flow length of the liquid-cooled plate system, determine the flow channel type, and calculate the proportion of pressure drop along the flow path and local pressure drop based on the ratio to obtain the design target values ​​of pressure drop along the flow path and local pressure drop.

[0033] It is understandable that when the coolant flows within the straight-flow channel section of the liquid-cooled plate in this embodiment, frictional resistance exists between the fluid and the channel wall, and between different fluid layers, due to the viscosity of the coolant itself. This continuously consumes pressure energy, causing the pressure to gradually decrease along the flow direction. This pressure loss caused by friction along the flow path is called frictional pressure drop. When the coolant flows through local areas such as the channel corners or abrupt changes in cross-section of the liquid-cooled plate in this embodiment, the flow velocity or flow direction changes drastically. Collisions, vortices, or backflows occur between fluid particles, resulting in concentrated pressure energy loss at these local locations. This pressure loss caused by local structural features is called local pressure drop.

[0034] Specifically, when the ratio of the equivalent hydraulic diameter of the channel to the total length of the flow path is greater than or equal to a preset threshold, the channel type is determined to be a long pipe, the friction drop ratio is set at 90%, and the local pressure drop ratio is set at 10%. When the ratio of the equivalent hydraulic diameter of the channel to the total length of the flow path is less than the preset threshold, the channel type is determined to be a short pipe, and the friction drop ratio and the local pressure drop ratio are each set at 50%. For complex pipe network systems, the friction drop ratio can be estimated to be 70% to 80%, and the local pressure drop ratio can be estimated to be 20% to 30%. The equivalent hydraulic diameter can be calculated based on the cross-sectional shape of the channel. For a rectangular cross-section channel, the equivalent hydraulic diameter de = 4A / P, where A is the cross-sectional area of ​​the channel and P is the wetted perimeter. In this embodiment, the preset threshold is exemplarily set to 1000.

[0035] The design target values ​​are determined as follows: the first target pressure drop a1 of the liquid-cooled plate body is used as the total pressure drop for allocation. The total pressure drop is multiplied by the corresponding proportion to obtain the design target values ​​for friction drop and local pressure drop. For example, if it is determined to be a short-pipe system with a proportion of 50% each, then the design target value for friction drop ΔPf = a1 × 50%, and the design target value for local pressure drop ΔPlocal = a1 × 50%. Specifically, in this embodiment, a1 = 0.05MPa, then ΔPf = 0.025MPa, and ΔPlocal = 0.025MPa.

[0036] By distinguishing the contribution ratios of pressure drop along the pressure line and local pressure drop, the key areas for pressure drop optimization can be accurately identified, avoiding the problem of unclear optimization direction caused by general judgments in traditional design.

[0037] Step-by-step simulation verification steps: Under the preset flow rate limit condition, calculate the friction drop and local pressure drop of the flow channel respectively, and use the design target values ​​of friction drop ΔPf and local pressure drop ΔPlocal determined in the previous step as verification benchmarks to verify whether the calculated friction drop and local pressure drop meet the corresponding design target values ​​respectively. If not, adjust the flow channel parameters until they meet the requirements.

[0038] In this embodiment, computational fluid dynamics simulation software can be used. First, the friction drop is calculated, the pressure drop per unit length of the flow channel is extracted, and multiplied by the total length of the flow channel to obtain the total friction drop. This is then verified to ensure that the total friction drop meets the design target value. Next, the local pressure drop is calculated, the number of local corner features from the inlet to the outlet of the flow channel is counted, and the sum of the local pressure drops at each corner is calculated to verify that the local pressure drop meets the design target value.

[0039] By performing step-by-step simulation verification, it can be confirmed whether the pressure drop along the friction and the local pressure drop meet the standards. If a certain component exceeds the standard, the corresponding structural parameters can be adjusted accordingly, avoiding the design iterations caused by the general judgment after traditional overall simulation and improving design efficiency.

[0040] Local feature determination steps: Establish the correspondence between the geometric parameters of the flow channel corner and the pressure drop value; based on the design target value of the local pressure drop, determine the minimum allowable angle and minimum allowable fillet radius of the flow channel corner; and, based on the design target value of the friction pressure drop, determine the flow channel cross-sectional parameters and / or length that satisfy the design target value of the friction pressure drop.

[0041] Specifically, firstly, flow channel angle 13 models with different geometric parameters are established. The pressure drop values ​​corresponding to different fillet radii at preset turning angles are calculated, generating a curve showing the relationship between fillet radius and pressure drop. Secondly, the pressure drop values ​​corresponding to different turning angles with a fixed fillet radius are calculated, generating a curve showing the relationship between turning angle and pressure drop. For example, for a 90-degree turning angle, the pressure drop values ​​are calculated for fillet radii of 0mm, 10mm, 20mm, and 40mm, obtaining the relationship between fillet radius and pressure drop. For a 10mm fillet, the pressure drop values ​​are calculated for turning angles of 45 degrees, 90 degrees, and 135 degrees, obtaining the relationship between turning angle and pressure drop.

[0042] Then, based on the local pressure drop design target value and the total number of corner features in the flow channel, the maximum allowable pressure drop value for each corner is determined. For example, if the local pressure drop design target value is 0.025 MPa (i.e., 25000 Pa), and there are 10 corner features in the flow channel from the inlet to the outlet, then the maximum allowable pressure drop value for each corner is 25000 ÷ 10 = 2500 Pa.

[0043] Finally, based on the aforementioned correlation curves and the maximum allowable pressure drop at each corner, the minimum allowable angle and minimum allowable fillet radius of the flow channel corner 13 are determined by reverse calculation. For example, at a 90-degree corner, when the pressure drop limit is 2500 Pa, according to the correlation curve between fillet radius and pressure drop, the fillet radius must be no less than 10 mm, and the pressure drop improvement is not significant after the fillet radius exceeds 40 mm; at a 10 mm fillet, when the pressure drop limit is 2500 Pa, according to the correlation curve between turning angle and pressure drop, the turning angle must be no less than 90 degrees. If the original design contains a 45-degree acute corner, its pressure drop is approximately 10000 Pa, far exceeding the 2500 Pa limit. It can be split into a combination structure of a 90-degree corner and a 135-degree corner. After splitting, the local pressure drop can be reduced to about one-sixth of the original value, meeting the design requirements.

[0044] By establishing a quantitative relationship between the geometric parameters of the turning angle and the pressure drop, the turning angle parameters can be determined, effectively reducing local pressure drop while ensuring the flexibility of the flow channel layout.

[0045] The specific process for determining the flow channel cross-sectional parameters and / or length based on the design target value of the friction pressure drop is as follows: The friction pressure drop ΔPf' satisfies ΔPf' = f × (L / de) × (ρv² / 2), where f is the friction resistance coefficient, L is the total flow length, de is the equivalent hydraulic diameter, ρ is the coolant density, v is the coolant velocity, and v = Q / A, where Q is the flow rate and A is the flow channel cross-sectional area. Here, de = 4A / P, and P is the wetted perimeter, i.e., the circumference of the flow channel wall in contact with the fluid. Under the preset upper limit of flow rate, given the design target value of the friction pressure drop ΔPf, the flow channel cross-sectional area A (or equivalent hydraulic diameter de) and the total flow length L are adjusted to ensure that the calculated ΔPf' ≤ ΔPf. In practice, a set of cross-sectional dimensions and lengths can be preset first, and the corresponding friction pressure drop ΔPf' can be calculated. If it is greater than the design target value ΔPf, the cross-sectional dimensions (A, de) are increased or the length (L) is shortened, and the calculation is repeated until the target value is met.

[0046] In the reverse solution of the aforementioned flow channel geometry parameters, the cross-sectional area (equivalent hydraulic diameter) and length of the flow channel satisfying ΔPf'≤ΔPf can be determined based on the design target value ΔPf of the pressure drop along the flow path. Numerical inversion algorithms such as least squares, gradient iterative optimization, differential evolution, or Bayesian optimization can be used. Specifically, the least squares method iteratively adjusts the flow channel parameters by minimizing the sum of squares of the errors between the calculated pressure drop ΔPf' and the design target value ΔPf; gradient iterative optimization utilizes the gradient information of the objective function with respect to the parameters to gradually approach the optimal parameters along the negative gradient direction; differential evolution searches for the global optimum in the parameter space through mutation, crossover, and selection operations of the population; and Bayesian optimization, based on a surrogate model and acquisition function, efficiently finds parameter combinations that satisfy the constraints within a limited number of parameter evaluations. The above numerical inversion algorithms all use the cross-sectional area of ​​the flow channel (or equivalent hydraulic diameter) and the flow length as optimization variables, and the deviation between ΔPf' and ΔPf as the objective function. They obtain the flow channel cross-sectional parameters and / or length that meet the design target value ΔPf of pressure drop along the flow path through iterative calculation.

[0047] In summary, the flow channel design method for the liquid cooling plate provided in this invention, through four steps—target pressure drop decomposition, pressure drop composition estimation, step-by-step simulation verification, and local feature determination—can systematically plan the total pressure drop of the liquid cooling plate, rationally allocate it to each component and each pressure drop type, and establish a quantitative relationship between the geometric parameters of the rotation angle and the pressure drop based on simulation. This allows for the precise determination of the minimum allowable angle and fillet radius of the flow channel rotation angle 13, achieving a low-resistance flow channel design with controllable pressure drop. This method reduces the load on the water chiller, ensures that the water chiller can achieve a high flow rate, improves the heat dissipation efficiency of heat-generating devices, and facilitates the structural design freedom when multiple pump modules are used in series.

[0048] Example 2 Please refer to Figure 1 This invention provides a liquid cooling plate 100 for heat dissipation of a light source, designed by the flow channel design method in Embodiment 1 above, and applied to high-power semiconductor light sources for liquid cooling of heat-generating devices.

[0049] The heat dissipation liquid cooling plate 100 of the light source includes a plate body, on which a flow channel system for cooling multiple heat-generating devices is provided.

[0050] The flow channel system includes a main flow channel 10 and multiple sub-flow channels. The main flow channel 10 is used to introduce coolant; its inlet is connected to the water supply pipe of the water chiller, and its outlet is connected to the return pipe. Multiple sub-flow channels are connected to the main flow channel 10 and are used to cool heat-generating components. After entering through the main flow channel 10, the coolant is distributed to each sub-flow channel, cooling the heat-generating components in different areas, and finally discharged. Specifically, multiple sub-flow channels are connected in series on the main flow channel 10, and the coolant flows sequentially through the multiple sub-flow channels along the path of the main flow channel 10.

[0051] In this embodiment, the heating device includes at least two first heating devices and one second heating device, and the sub-channel includes a first sub-channel 11 for cooling the first heating devices and a second sub-channel 12 for cooling the second heating device.

[0052] Along the thickness direction of the plate, there are three layers of different heights: a first layer, a second layer, and a third layer. Two first sub-flow channels 11 are respectively located on the higher first layer and the lower third layer, and a second sub-flow channel 12 is located on the second layer, which is situated between the first and third layers.

[0053] By setting the two first sub-channels 11 corresponding to the first heating device at different height levels on both sides, and setting the second sub-channel 12 corresponding to the second heating device at the middle level, a flow channel layout with high, medium and low heights is formed. This can make full use of the installation space of the semiconductor light source, realize independent heat dissipation of different heat sources, and avoid thermal crosstalk between heat sources.

[0054] The first sub-channel 11 on the first layer is used to cool the first heating element located on one side of the plate, the first sub-channel 11 on the third layer is used to cool the first heating element located on the other side of the plate, and the second sub-channel 12 on the second layer is used to cool the second heating element located between the two first heating elements. The second heating element has a higher heat flux density during operation. Placing its corresponding channel on the middle layer, with the channels for the first heating elements on both sides at different heights, helps to increase the heat exchange area of ​​the channel below the second heating element and improves the heat dissipation efficiency of the second heating element.

[0055] By adopting the above-mentioned flow channel design method, the flow channel corner 13 of the light source heat dissipation liquid cooling plate 100 has a definite minimum allowable angle and minimum allowable fillet radius, thereby effectively controlling the flow channel pressure drop and reducing the load of the water chiller while meeting the heat dissipation layout requirements.

[0056] Furthermore, the second sub-channel 12 includes two main channels 121 and a plurality of branch channels 123 connecting the two main channels 121. At least one of the main channels 121 is connected to the main channel 10. The two main channels 121 are located on both sides below the second heating device, and the coolant is diverted from the main channel 10 into the two main channels 121 and then distributed to each branch channel 123. The branch channels 123 are distributed at intervals along the winding direction of the second heating device to uniformly dissipate heat from different areas of the second heating device.

[0057] Along the flow direction of the coolant in the main channel 121, the cross-sectional area of ​​the main channel 121 gradually decreases, and the cross-sectional area of ​​the branch channel 123 also gradually decreases. Specifically, the ratio of the maximum to minimum cross-sectional area of ​​the main channel 121 can be from 1.5:1 to 3:1, and in this embodiment, it is selected as 2:1. The ratio of the maximum to minimum cross-sectional area of ​​the branch channel 123 can also be from 1.5:1 to 3:1, and in this embodiment, it is selected as 2.25:1. By gradually reducing the cross-sectional areas of the main channel 121 and the branch channel 123 along the flow direction, the flow resistance of the downstream channel can be increased, forcing more coolant to flow to the upstream branch channel 123. This results in a more uniform flow distribution in each branch channel 123, avoiding the problem of excessive flow in the branch channel 123 near the inlet and insufficient flow in the branch channel 123 far from the inlet, thus achieving uniform heat dissipation.

[0058] It should be noted that in other embodiments, the ratio of the cross-sectional area change of the main channel 121 and the branch channel 123 can be adjusted according to the actual heat dissipation requirements and simulation calculation results, as long as the flow rate of each branch channel 123 can be evenly distributed.

[0059] Furthermore, a flow-guiding protrusion is formed on the inner wall of the main flow channel 121 on the side away from the branch flow channel 123, and the flow-guiding protrusion is inclined towards the direction of coolant flow. The proportion of the flow-guiding protrusion to the width of the main flow channel 121 can be 1 / 4 to 1 / 2. The function of the flow-guiding protrusion is to artificially increase directional flow, change the flow direction of the coolant, and guide more coolant to the branch flow channel 123 area with higher heat flux density, without excessively increasing flow resistance. For example, when a heat-generating component with high heat flux density is distributed above a branch flow channel 123, while the heat flux density above an adjacent branch flow channel 123 is significantly lower, a flow-guiding protrusion can be set at the corresponding position to guide the fluid to the branch flow channel 123 with higher heat flux density, achieving on-demand distribution.

[0060] Furthermore, multiple branch channels 123 are spaced apart, with the distance between adjacent branch channels 123 gradually increasing along the flow direction of the coolant in the main channel 121. By adjusting the distance between the branch channels 123, the flow distribution of each branch channel 123 can be further adjusted. Combined with the gradual change in the cross-sectional area of ​​the main channel 121 and the branch channels 123, the flow difference between each branch channel 123 can be controlled within a small range.

[0061] Furthermore, the main channel 10 is provided with at least one flow channel corner 13, the minimum fillet radius of the flow channel corner 13 being 10 mm, and the turning angle being 90 degrees or 135 degrees. In an optional embodiment, a 45-degree acute angle corner in the flow channel system is split into a combination of a 90-degree corner and a 135-degree corner. By splitting the acute angle corner into a combination of two obtuse or right angle corners, the local pressure drop can be significantly reduced, for example, reducing the local pressure drop to approximately one-sixth of its original value.

[0062] It should be noted that the above-mentioned angle parameters are preferred values ​​determined under specific design target conditions based on the flow channel design method of Embodiment 1. In other embodiments, when the design target parameters such as pressure drop and flow rate are different, the specific values ​​of the minimum allowable angle and the minimum allowable fillet radius can be re-determined according to the method described above.

[0063] The working principle of the light source heat dissipation liquid cooling plate 100 provided in this embodiment of the invention is as follows: Driven by the water chiller, the coolant enters from the inlet of the main channel 10 and is divided into the first sub-channel 11 and the second sub-channel 12. The coolant in the first sub-channel 11 flows through the first heating element, carrying away the heat generated by the first heating element. The coolant in the second sub-channel 12 is distributed to each branch channel 123 via the main channel 121, flows through the second heating element, and carries away the heat generated by the second heating element. Finally, the coolant from each channel merges and is discharged from the outlet, returning to the water chiller for cooling and recycling. Due to the optimized design of the channel bend 13, the local pressure drop is effectively controlled. Because the main channel 121 and the branch channels 123 adopt a gradually changing cross-sectional area design and are equipped with guide protrusions, the flow distribution of each branch channel 123 is uniform, achieving uniform heat dissipation.

[0064] In summary, the liquid cooling plate 100 for heat dissipation of the light source provided in this embodiment of the invention, through the parallel design of the main channel 10 and multiple sub-channels, the channel layout at three different height levels, the gradual change in cross-sectional area of ​​the main channel 121 and the branch channels 123, and the setting of the guide protrusions, can achieve uniform flow distribution in each branch channel 123. This significantly reduces channel pressure drop while ensuring efficient heat dissipation, reduces the load on the water chiller, ensures the water chiller can achieve a high flow rate, improves heat dissipation efficiency, and facilitates structural design freedom when multiple pump modules are used in series. Furthermore, by placing the channel below the second heating device at the middle level and distributing the channels of the first heating devices on both sides at different heights, the heat exchange area of ​​the second heating device's heat dissipation region is increased, further improving heat dissipation efficiency.

[0065] Example 3 This invention provides a semiconductor light source, including the liquid cooling plate 100 for heat dissipation described in Embodiment 2 above. The semiconductor light source also includes a first heating device, a second heating device, optical components, a driving power supply, and a chassis. The first and second heating devices are mounted on the liquid cooling plate 100 and are cooled by the liquid cooling plate. The driving power supply supplies power to the first heating device module, and the optical components are used to shape and couple the pump light.

[0066] Thanks to the use of the aforementioned liquid cooling plate 100 for heat dissipation of the light source, this semiconductor light source has high heat dissipation efficiency, low voltage drop, low system energy consumption, and good operational stability, making it suitable for high-power laser output applications.

[0067] The above description is merely a specific embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in the present invention should be included within the scope of protection of the present invention.

Claims

1. A flow channel design method, characterized in that, Applied to a liquid cooling system, the liquid cooling system including a liquid cooling plate system and a heating module, the method includes the following steps: Determine the total target pressure drop of the liquid cooling plate system, including a first target pressure drop generated by the liquid cooling plate body and a second target pressure drop corresponding to the heat-generating module cooled by the liquid cooling plate body, wherein the liquid cooling system includes the liquid cooling plate body; Based on the ratio of the equivalent hydraulic diameter of the flow channel to the total flow length of the liquid cooling plate system, the flow channel type is determined, and the ratio of friction pressure drop and local pressure drop is determined based on the flow channel type. The design target values ​​of friction pressure drop and local pressure drop are determined based on the total target pressure drop and the ratio. Under the preset flow rate limit condition, the friction drop and local pressure drop of the flow channel are calculated respectively, and it is determined that the friction drop and local pressure drop meet the corresponding design target values ​​respectively; Establish the correspondence between the geometric parameters of the flow channel corner and the pressure drop value. Based on the design target value of the local pressure drop, determine the minimum allowable angle and the minimum allowable fillet radius of the flow channel corner.

2. The flow channel design method according to claim 1, characterized in that, When the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path is greater than or equal to a preset threshold, the flow channel type is determined to be a long pipe, the pressure drop ratio along the flow path is determined to be 90%, and the local pressure drop ratio is determined to be 10%. When the ratio of the equivalent hydraulic diameter of the flow channel to the total length of the flow path is less than the preset threshold, the flow channel type is determined to be a short pipe, and the pressure drop ratio along the flow path and the local pressure drop ratio are determined to be 50% respectively.

3. The flow channel design method according to claim 1, characterized in that, Establish the correspondence between the geometric parameters of the flow channel angle and the pressure drop value, including: Based on the same turning angle, obtain the pressure drop values ​​corresponding to flow channels with different fillet radii, and determine the correspondence between fillet radius and pressure drop; Based on the same fillet radius, obtain the pressure drop values ​​corresponding to different turning angles, and determine the correspondence between the turning angle and the pressure drop.

4. A liquid cooling plate for heat dissipation of a light source, characterized in that, Designed based on the flow channel design method according to any one of claims 1-3, the plate includes a plate body, wherein the plate body is provided with a flow channel system for cooling multiple heat-generating devices; The flow channel system includes: Main channel, used for introducing coolant; Multiple sub-channels are connected to the main channel, and the sub-channels are used to cool the heat-generating device.

5. The liquid cooling plate for heat dissipation of the light source according to claim 4, characterized in that, The heating device includes at least two first heating devices and one second heating device, and the sub-channel includes a first sub-channel for cooling the first heating devices and a second sub-channel for cooling the second heating device; A first layer, a second layer, and a third layer of different heights are provided along the thickness direction of the plate. Two first sub-flow channels are respectively provided on the first layer and the third layer. A second sub-flow channel is provided on the second layer, which is located between the first layer and the third layer.

6. The liquid cooling plate for heat dissipation of the light source according to claim 5, characterized in that, The second sub-channel includes two main channels and a plurality of branch channels connecting the two main channels, and at least one of the main channels is connected to the main channel; Along the flow direction of the coolant in the main channel, the cross-sectional area of ​​the main channel gradually decreases, and the cross-sectional area of ​​the branch channel gradually decreases.

7. The liquid cooling plate for heat dissipation of the light source according to claim 6, characterized in that, The ratio of the maximum to the minimum cross-sectional area of ​​the main channel is 1.5:1 to 3:1; the ratio of the maximum to the minimum cross-sectional area of ​​the branch channel is 1.5:1 to 3:

1.

8. The liquid cooling plate for heat dissipation of the light source according to claim 6, characterized in that, A flow-guiding protrusion is provided on the inner wall of the main channel on the side away from the branch channel, and the flow-guiding protrusion is inclined toward the flow direction of the coolant.

9. The liquid cooling plate for heat dissipation of the light source according to claim 6, characterized in that, The multiple branch channels are spaced apart, and the distance between two adjacent branch channels gradually increases along the flow direction of the coolant in the main channel.

10. A semiconductor light source, characterized in that, Including the light source heat dissipation liquid cooling plate as described in any one of claims 5-9.

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