Laminar cooling uniformity optimization method and apparatus

Abstract

The application discloses a laminar cooling uniformity optimization method and device, and belongs to the technical field of metallurgical control. The method comprises the following steps: determining a non-uniform distribution mode of primary damping holes and secondary damping holes of a lower header based on process parameters and cooling requirements of a laminar cooling system; constructing a fluid dynamics mathematical model based on the non-uniform distribution mode and the process parameters, so as to show fluid flow characteristics in the lower header with a triple-chamber structure; constructing a comprehensive evaluation function based on the fluid dynamics mathematical model, so as to evaluate cooling performance in the width direction of a strip; and obtaining optimal distribution parameters of the primary damping holes and the secondary damping holes when the comprehensive evaluation function is minimized, so as to configure hole diameter sizes and axial positions. By introducing a quantitative design method based on fluid dynamics theory, pressure loss of cooling water along a path is compensated, precise regulation and control of cooling water flow are realized, cooling uniformity in the width direction of the strip is improved, and consistency of product microstructure and mechanical properties is ensured.

Description

Technical Field

[0001] This application relates to the field of metallurgical control technology, and in particular to a method and apparatus for optimizing laminar cooling uniformity. Background Technology

[0002] The post-rolling cooling system for hot-rolled strip steel is a core component of the production process, its core function being to precisely control the coiling temperature of the strip steel and optimize its mechanical properties. The intensity and uniformity of the cooling manifold have a decisive impact on the quality and performance of the final product. Among these technologies, laminar flow cooling technology has attracted widespread attention in the industry due to its wide applicability and ease of equipment maintenance. The main heat exchange mechanism of laminar flow cooling is film boiling heat exchange. Cooling water flows vertically across the surface of the steel plate under gravity, forming a continuous water flow, which theoretically can achieve uniform and efficient heat exchange. However, in the actual application of strip steel cooling, due to insufficient cooling water pressure, the outflow continuity of nozzles in some traditional manifolds is low. This causes the heat exchange process between the cooling water and the strip steel surface to change from a stable film boiling state to an unstable state, thus hindering the heat transfer process and resulting in low cooling intensity. At the same time, insufficient cooling water pressure and discontinuous outflow cause uneven cooling in the width direction of the strip steel, further affecting the stability of the product's microstructure and properties. Summary of the Invention

[0003] This application provides a method and apparatus for optimizing the uniformity of laminar cooling, so as to at least solve the problem of uneven cooling in the width direction of strip steel during laminar cooling in related technologies, which leads to unstable strip steel performance.

[0004] In a first aspect, this application provides a method for optimizing laminar cooling uniformity, the method comprising:

[0005] Based on the process parameters and cooling requirements of the laminar flow cooling system, the non-uniform distribution pattern of the primary and secondary damping orifices in the lower manifold is determined. The primary and secondary damping orifices are used to jointly regulate the cooling water flow rate.

[0006] Based on the non-uniform distribution pattern and process parameters, a fluid dynamics mathematical model is constructed to demonstrate the fluid flow characteristics in the lower manifold with a triple-chamber structure.

[0007] Based on the fluid dynamics mathematical model, a comprehensive evaluation function for the lower manifold is constructed. This comprehensive evaluation function is used to evaluate the cooling performance in the width direction of the strip.

[0008] When the comprehensive evaluation function is minimized, the optimal distribution parameters of the primary damping hole and the secondary damping hole are obtained. The optimal distribution parameters are used to configure the hole size and axial position of the primary damping hole and the secondary damping hole.

[0009] The above technical solution determines the non-uniform distribution pattern of the primary and secondary damping orifices, constructs a fluid dynamics model and comprehensive evaluation function for the triple-chamber structure, and solves for the optimal distribution parameters with the goal of minimizing the function, thereby realizing the digital characterization and precise control of the complex flow field in the lower manifold. This solution effectively overcomes the defect of traditional uniform design that cannot compensate for the uneven flow distribution caused by pressure loss along the pipe, significantly improves the cooling uniformity in the strip width direction, ensures the stability of the product's microstructure and mechanical properties, and realizes the transformation of cooling manifold design from passive experience trial and error to active intelligent optimization.

[0010] Secondly, this application provides a laminar cooling uniformity optimization device, the device comprising:

[0011] The water inlet pipe is connected at one end to the cooling water source;

[0012] The water inlet chamber is connected to the other end of the water inlet pipe. The side wall of the water inlet chamber is provided with a number of non-uniformly distributed primary damping holes. The distribution parameters of the primary damping holes are obtained by performing any of the flow cooling uniformity optimization methods described above.

[0013] A buffer chamber is connected to the water inlet chamber. The upper wall of the buffer chamber is provided with a plurality of non-uniformly distributed secondary damping holes. The distribution parameters of the secondary damping holes are obtained by performing any of the flow cooling uniformity optimization methods described above.

[0014] The equalizing chamber is connected to the buffer chamber;

[0015] The nozzle panel is located at the bottom of the equalizing chamber.

[0016] The above technical solution achieves refined control of cooling water flow and active compensation for pressure loss along the pipe by setting up a two-stage damping structure consisting of an inlet pipe, an inlet chamber, a buffer chamber, and a pressure equalization chamber, and by using the non-uniform distribution parameters of the first-stage and second-stage damping orifices determined by the aforementioned optimization method. This device effectively solves the problems of uneven flow distribution and pressure fluctuation caused by pressure loss along the pipe in traditional manifolds, significantly improves the cooling uniformity and pressure stability in the width direction of the strip, thereby ensuring the stability of the product's microstructure and mechanical properties, and achieving efficient and stable operation of the cooling device. Attached Figure Description

[0017] The accompanying drawings, which are incorporated in and form a part of this specification, illustrate embodiments consistent with this disclosure and, together with the description, serve to explain the principles of this disclosure.

[0018] To more clearly illustrate the technical solutions in the embodiments of this disclosure or the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, for those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 1 ;

[0020] Figure 2 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 2 ;

[0021] Figure 3 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 3 ;

[0022] Figure 4 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 4 ;

[0023] Figure 5 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 5 ;

[0024] Figure 6 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 6 ;

[0025] Figure 7 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 7 ;

[0026] Figure 8 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 8 ;

[0027] Figure 9 A flowchart illustrating a laminar cooling uniformity optimization method provided in this application embodiment. Figure 9 ;

[0028] Figure 10 A schematic cross-sectional view of the internal chamber of the cooling manifold and the primary buffer structure provided in the embodiments of this application;

[0029] Figure 11 This is a schematic diagram of the longitudinal section of the internal two-stage buffer structure of the cooling manifold provided in the embodiments of this application;

[0030] Figure 12 The non-uniform arrangement of damping holes provided in the embodiments of this application is shown in the following schematic diagram: the number of damping holes is dense in the middle and sparse at both ends.

[0031] Figure 13 The non-uniform arrangement of damping holes provided in the embodiments of this application is shown in the following schematic diagram: the number distribution of damping holes is sparse in the middle and dense at both ends.

[0032] Figure 14 The non-uniform arrangement of damping holes provided in the embodiments of this application is shown in the following schematic diagram: the number of damping holes is dense on the inlet side and sparse on the sealing side.

[0033] Figure 15 The non-uniform arrangement of damping holes provided in the embodiments of this application is shown in the schematic diagram of the number distribution of damping holes: sparse on the inlet side and dense on the sealing side.

[0034] 1. Inner pipe, 2. Outer pipe, 3. Bracket, 4. Nozzle panel, 5. Secondary damping plate, 6. Secondary damping hole, 7. Primary damping hole, 8. Inlet pipe. Detailed Implementation

[0035] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the protection scope of this application.

[0036] It should be noted that, in the description of this application, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. The terms "first," "second," etc., in this application are used to distinguish similar objects and are not used to describe a specific order or sequence.

[0037] In related technologies, laminar flow cooling systems are key equipment for controlling the microstructure and mechanical properties of hot-rolled strip steel on production lines. The core component, the cooling manifold, especially the lower manifold, is responsible for spraying high-pressure cooling water onto the surface of the high-temperature strip steel to achieve rapid cooling. Ideally, to ensure uniform cooling of the strip steel across its width, the flow rate of cooling water from each nozzle in the manifold should be consistent. However, in practical applications, the lower manifold typically employs a single-chamber structure, with cooling water flowing in from the inlet end, flowing axially along the manifold, and exiting from each nozzle. This structure presents significant hydrodynamic defects: as the cooling water flows within the manifold, its static pressure energy continuously decreases along the flow direction due to frictional resistance and flow diversion, resulting in a pressure gradient distribution with high pressure at the inlet and low pressure at the outlet. With uniform nozzle openings, this pressure gradient directly leads to a large flow rate at the inlet nozzle and a small flow rate at nozzles farther from the inlet, creating a "flow tilt" phenomenon along the width of the strip steel. Uneven flow rate directly leads to inconsistent cooling intensity in the width direction of the strip, causing uneven sheet material properties, poor sheet shape, and even quality problems such as wavy bending caused by residual stress.

[0038] To alleviate this problem, existing technologies mainly employ two methods: one is to increase the manifold diameter to reduce flow velocity and thus decrease frictional resistance, but this significantly increases equipment costs and space requirements; the other is to rely on experience in the design phase for compensatory design, such as adjusting nozzle orifice diameter or spacing, but this method lacks theoretical basis, often requires multiple trials, and is difficult to adapt to different operating conditions, failing to fundamentally solve the problem of uneven flow distribution. Furthermore, for advanced lower manifolds with a triple-chamber structure of "inlet chamber - buffer chamber - equalizing chamber," the internal flow field is even more complex. The synergistic effect of the two-stage damping orifices (primary and secondary damping orifices) has not yet been described by a mathematical model, making it difficult for traditional empirical design methods to achieve synergistic optimization of the triple-chamber structure. In summary, existing technologies suffer from uneven cooling water flow distribution, poor cooling uniformity, and a lack of optimized design methods in lower manifolds.

[0039] To address the aforementioned technical problems, this embodiment provides a method for optimizing laminar cooling uniformity, particularly suitable for the optimized design of lower manifolds with a triple-chamber structure. By establishing a fluid dynamics model and constructing a comprehensive evaluation function for numerical optimization, the optimal non-uniform distribution parameters of the primary and secondary damping orifices are obtained, thereby achieving the distribution of cooling water flow rate along the strip width.

[0040] The application scenarios of the technical solutions provided in the embodiments of this application are described below.

[0041] The laminar flow cooling uniformity optimization method and apparatus provided in this application are mainly applied to the laminar flow cooling system of hot-rolled strip steel production line, especially for the optimization design and control of the laminar flow cooling system of the lower manifold on the output roller table.

[0042] Scene 1: Laminar flow cooling zone of hot-rolled strip steel production line

[0043] In the hot-rolled strip steel production process, the final rolling temperature is typically above 800℃. The strip steel needs to pass through a laminar flow cooling zone to rapidly reduce its temperature to the coiling temperature (usually between 400℃ and 700℃). The laminar flow cooling uniformity optimization device for the lower manifold provided in this application is located below the output roller conveyor and works in conjunction with the upper manifold. Because the lower manifold needs to overcome the influence of gravity, and the cooling water needs to be accurately sprayed onto the lower surface of the strip steel, the uniformity of the water flow is even more critical. Applying the optimization method based on a fluid dynamics model and non-uniform damping orifice distribution provided in this application, the parameters of the primary and secondary damping orifices of the lower manifold can be precisely designed to ensure the formation of a uniform cooling water film along the width direction of the strip steel. This plays a crucial role in eliminating cooling blind spots on the lower surface of the strip steel and improving overall cooling efficiency.

[0044] Scenario 2: Highly Uniform Cooling Production of Wide Strip Steel

[0045] When producing wide strip steel, such as strip steel with a width exceeding 1500mm, traditional uniformly perforated manifolds are prone to uneven cooling along the width direction due to pressure loss along the friction path, leading to strip shape defects such as edge waviness and center waviness. The technical solution of this application is particularly suitable for the production of such wide strip steel. By constructing a fluid dynamics mathematical model, comprehensively considering cooling uniformity and pressure stability, the calculated non-uniformly distributed primary and secondary damping orifices can effectively compensate for the pressure drop along the friction path, ensuring that the velocity and flow rate of the water jetted from the nozzle remain highly consistent along the width direction of the strip steel. Applying this solution can significantly improve the strip shape quality of wide strip steel and reduce the defect rate caused by uneven cooling.

[0046] Scenario 3: Precise phase transformation control of high-strength steel and high-grade pipeline steel

[0047] For high-strength low-alloy steel (HSLA), duplex steel (DP), or high-grade pipeline steel (X80, X100, etc.), their mechanical properties are highly dependent on the phase transformation process during cooling. This requires that the cooling rate be strictly controlled within a specific range, and that the cooling history of each part of the strip be consistent. The laminar flow cooling uniformity optimization device for the lower manifold provided in this application, through a triple-chamber structure of an inlet chamber, a buffer chamber, and a pressure equalization chamber, combined with a non-uniform damping orifice design, better stabilizes the pressure and flow rate at the nozzle outlet, reducing water flow fluctuations. The device applying the laminar flow cooling method can effectively control the cooling path of the strip, ensuring a uniform transformation of the microstructure, thereby guaranteeing a high pass rate for the product's yield strength, tensile strength, and toughness indicators.

[0048] Scenario 4: Technical Upgrading of Outdated Laminar Flow Cooling Systems

[0049] To address the issues of insufficient cooling capacity or poor cooling uniformity in existing laminar flow cooling systems of hot rolling production lines, this application provides a low-cost, high-efficiency retrofit solution. It eliminates the need for large-scale dismantling and reconstruction of the entire laminar flow cooling system; instead, it utilizes the method described in this application to recalculate and process the damping orifice distribution parameters of the lower manifold based on existing process parameters and equipment constraints, and replaces key lower manifold components. This significantly improves product quality control capabilities and extends equipment lifespan in aging production lines.

[0050] After introducing the application scenarios of the embodiments of this application, the technical solutions provided by the embodiments of this application will be described below. (See also...) Figure 1 Taking the laminar cooling uniformity optimization device, such as a PLC or industrial computer processor, as an example, the following steps are included.

[0051] Step S101: Based on the process parameters and cooling requirements of the laminar flow cooling system, determine the non-uniform distribution pattern of the primary and secondary damping orifices in the lower manifold.

[0052] The primary and secondary damping orifices are used to jointly regulate the cooling water flow rate. Specifically, the specifications of the strip to be cooled, such as steel grade, thickness, width, target coiling temperature, and cooling rate, are read, and combined with the structural constraints of the lower manifold, such as total length and chamber size, the distribution pattern of the primary and secondary damping orifices is initially set. This orifice pattern is not uniformly distributed, but rather preset as a trend distribution pattern with small or low orifice diameter at the inlet end and large or high orifice diameter at the end, based on the flow characteristics of high inlet pressure and low end pressure. For example, the orifice pattern can be set such that, along the width direction of the strip, from the inlet end to the end, the orifice diameter of the primary and secondary damping orifices gradually increases, or the orifice spacing gradually decreases, or a combination of both, to balance the water flow rate of each nozzle. For example, based on the process parameters and cooling requirements of the laminar flow cooling system, the process parameters and cooling requirements of the laminar flow cooling system can also be adjusted according to the actual production situation. Specifically, based on the requirement for uniform cooling of the steel plate surface, a multi-row small-diameter water column outflow arrangement is adopted to achieve multiple water columns flowing out to the steel plate surface; based on the arrangement requirement of multiple rows of small-diameter water columns, the physical structure of the cooling chamber inside the manifold is determined, and the size and distribution of the damping orifice are designed to achieve precise control of the outflow rate of cooling water along the length of the manifold.

[0053] Step S102: Construct a fluid dynamics mathematical model based on the non-uniform distribution mode and process parameters.

[0054] The fluid dynamics mathematical model is used to demonstrate the fluid flow characteristics within a lower manifold with a triple-chamber structure. Specifically, the processor constructs a fluid dynamics mathematical model for the triple-chamber structure of "inlet chamber - buffer chamber - equalizing chamber" based on the laws of conservation of mass, momentum, and energy in fluid mechanics. This fluid dynamics mathematical model includes the pressure distribution equation within the inlet chamber, the throttling equation for the first-stage damping orifice, the pressure equalization equation within the buffer chamber, the overflow equation for the second-stage damping orifice, and the pressure stability equation within the equalizing chamber. The processor uses the orifice diameter parameters and axial position parameters determined in step S101 as input variables, combined with boundary conditions such as water supply pressure and flow rate, and substitutes them into the fluid dynamics mathematical model for solution. It can calculate the pressure field and velocity field distribution in each region of the lower manifold under different distribution modes, as well as the flow velocity and flow rate values ​​at each nozzle outlet, thereby simulating the fluid flow characteristics within the triple-chamber structure.

[0055] Step S103: Construct a comprehensive evaluation function for the lower manifold based on the fluid dynamics mathematical model.

[0056] The comprehensive evaluation function is used to assess the cooling performance along the width of the strip. Specifically, this step first uses the fluid dynamics mathematical model constructed in step S102 to perform simulation calculations and determine the actual flow distribution data of the cooling water in the lower manifold along the width of the strip. Based on this actual flow distribution data, the actual cooling water flow density at each position along the width of the strip is calculated and compared with the target cooling water flow density to determine the deviation value of the flow density. Subsequently, combined with preset weighting coefficients along the width of the strip, such as assigning higher weights to the edges or key areas, the cooling uniformity evaluation index is calculated. Finally, based on the flow distribution data and the cooling uniformity evaluation index, a comprehensive evaluation function is constructed. Specifically, a multi-dimensional comprehensive evaluation function is constructed, which includes a pressure gradient penalty term, a pressure setting deviation term, and a cooling uniformity optimization term. By assigning weighting coefficients to different terms and summing them, a comprehensive evaluation function is constructed. The function value of the comprehensive evaluation function reflects the quality of cooling uniformity under the current primary damping orifice and secondary damping orifice distribution modes. The smaller the value, the better the cooling uniformity and the more stable and safe the system operation.

[0057] Step S104: When the comprehensive evaluation function is minimized, the optimal distribution parameters of the first-stage damping orifice and the second-stage damping orifice are obtained.

[0058] The optimal distribution parameters are used to configure the orifice size and axial installation position of the primary and secondary damping orifices. Specifically, an optimization algorithm, such as a genetic algorithm, particle swarm optimization, or sequential quadratic programming, is invoked to iteratively optimize within a preset orifice size range and axial position constraints, with the goal of minimizing the comprehensive evaluation function. In each iteration, the algorithm generates a new set of distribution parameters for the primary and secondary damping orifices, which are then substituted into the fluid dynamics mathematical model of step S102 for simulation to obtain flow rate and pressure distribution data. This data is then substituted into the comprehensive evaluation function constructed in step S103 to calculate the corresponding evaluation value. After multiple iterations, when the evaluation value converges to the minimum value, the corresponding distribution parameters are the optimal distribution parameters. These optimal distribution parameters specifically define the precise orifice size and axial installation position of each primary and secondary damping orifice. They are output and stored to guide the subsequent manufacturing or configuration of the lower manifold, thereby achieving precise control of the cooling water flow rate.

[0059] This embodiment constructs a triple-chamber fluid dynamics model including an inlet chamber, a buffer chamber, and a pressure equalization chamber. It establishes a comprehensive evaluation function with cooling uniformity and pressure stability as indicators, and uses an optimization algorithm to solve the function minimization solution. This achieves the technical effect of obtaining the aperture size and axial position of the primary damping orifice and the secondary damping orifice, and achieves the beneficial effects of effectively compensating for pressure loss along the friction and ensuring uniform cooling in the width direction of the strip.

[0060] It should be noted that the above steps S101-S104 are a simplified description of the embodiments provided in this application.

[0061] The following will provide a more detailed explanation, using examples, of how the process parameters and cooling requirements of the laminar flow cooling system provided in this application determine the non-uniform distribution pattern of the primary and secondary damping orifices in the lower manifold. (See [link to relevant documentation]). Figure 2 This includes the following steps.

[0062] Step S201: Based on the process parameters of the laminar flow cooling system, determine the dimensional characteristics and structural constraints of the lower manifold.

[0063] Specifically, the process parameters of the laminar flow cooling system encompass the physical specifications and operating conditions of the lower manifold and internal chambers, including the total length of the lower manifold, the diameter of each chamber, material properties, and the manufacturing capabilities of existing equipment. Based on these parameters, the dimensional characteristics of the lower manifold are determined, such as the inner diameter of the inlet chamber, the height of the buffer chamber, and the volume of the equalizing chamber. Simultaneously, structural constraints are defined, such as the minimum spacing of damping orifices allowed to ensure pipe wall strength, the maximum and minimum orifice diameter thresholds of damping orifices limited by the manufacturing process (e.g., a minimum orifice diameter of not less than 4mm to prevent clogging), and the upper limit of the inlet flow velocity, providing physical boundary conditions for subsequent design.

[0064] Step S202: Based on cooling requirements, determine the target flow distribution characteristics of cooling water in the width direction of the strip.

[0065] Specifically, cooling requirements stem from the heat treatment process requirements of the strip steel, including the strip steel's material, specifications, initial temperature, target coiling temperature, and specific indicators for the cooling rate. Based on these requirements, the ideal flow distribution curve, i.e., the target flow distribution characteristic, is calculated through thermodynamic model inversion to achieve uniform temperature cooling along the width of the strip steel. This typically manifests as a uniform distribution characteristic requiring consistent cooling water flow density along the width of the strip steel, or a specific convex or edge-reinforced distribution characteristic designed for the rapid heat dissipation at the edges of the strip steel.

[0066] Step S203: Based on the size characteristics and structural constraints of the lower manifold and the target flow distribution characteristics, determine the non-uniform distribution pattern of the primary damping orifice and the secondary damping orifice.

[0067] The primary damping orifice is located on the side wall of the inlet chamber inside the lower manifold, and the secondary damping orifice is located on the upper wall of the buffer chamber inside the lower manifold. The non-uniform distribution pattern includes at least one or a combination of the following: dense in the middle and sparse at both ends; sparse in the middle and dense at both ends; dense on the inlet side and sparse on the sealing side; or sparse on the inlet side and dense on the sealing side.

[0068] Specifically, the physical boundary conditions determined in step S201 are coupled with the ideal flow distribution target determined in step S202. Considering the pressure loss along the flow path of the fluid inside the lower manifold, a uniform orifice would lead to a decrease in the flow rate at the end. Therefore, the non-uniform distribution pattern of the damping orifices along the length of the manifold is determined by calculation. For example, damping orifices with different diameters or spacings are set at different axial positions. The non-uniform distribution of the damping orifice geometry is used to compensate for the frictional changes in fluid pressure, so that the actual outflow capacity of the damping orifice can accurately match the target flow distribution characteristics.

[0069] This embodiment analyzes process parameters to determine physical dimensional constraints and processing limitations, sets a target flow rate curve based on cooling requirements, and matches a corresponding non-uniform orifice distribution pattern accordingly. By combining this with the ideal flow rate distribution target required for strip cooling, a mapping relationship between the two is constructed. This achieves the technical effect of effectively unifying manufacturing feasibility and cooling process objectives. It also achieves the beneficial effect of accurately compensating for pressure loss along the pipe while ensuring the strength of the manifold structure and anti-clogging performance, thereby obtaining the optimal orifice layout scheme to meet complex cooling requirements.

[0070] In some embodiments, the non-uniform distribution pattern of the primary damping orifice and the secondary damping orifice is determined based on the size characteristics and structural constraints of the lower manifold and the target flow distribution characteristics. (See [reference needed]) Figure 3 Specifically, it includes:

[0071] Step S301: Based on the size characteristics of the lower manifold, determine the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalization chamber within the lower manifold.

[0072] Specifically, the detailed dimensional characteristics of the lower manifold are first obtained, including parameters such as the length of each chamber, its internal diameter, and the roughness of the pipe wall. Based on fluid dynamics principles, when cooling water flows axially within the inlet chamber, frictional resistance occurs along the pipe wall, causing the static pressure to gradually decrease along the flow direction. Through simulation calculations, the pressure attenuation curve of the inlet chamber from the inlet end to the sealing end is obtained. Subsequently, considering the location of the primary damping orifice, the pressure distribution after the cooling water enters the buffer chamber, and the pressure field distribution after entering the equalizing chamber via the secondary damping orifice, are further calculated. Finally, global pressure distribution data covering all three chambers along the strip width is generated, clarifying the pressure differences at different axial positions and providing fundamental data for subsequent orifice design.

[0073] Step S302: Based on the pressure distribution and the target flow distribution characteristics, determine the opening area or aperture of the primary damping orifice and the secondary damping orifice at different locations.

[0074] This ensures that the actual outflow capacity of the primary damping orifice and the secondary damping orifice matches the target flow distribution characteristics.

[0075] Specifically, after obtaining the pressure values ​​at each location, compensation calculations are performed based on the target flow distribution characteristics determined by the cooling requirements. The logic lies in using the local resistance characteristics of the damping orifices to offset the pressure differences along the flow path. For example, in the high-pressure area near the inlet, to prevent excessive outflow, calculations determine that a smaller orifice area or diameter is needed in this area to increase local resistance and suppress outflow; while in the low-pressure area far from the inlet, to ensure sufficient cooling water volume, a larger orifice area or diameter is needed to reduce local resistance and improve outflow capacity. Through this differentiated configuration, the optimal orifice diameter value for each primary and secondary damping orifice can be accurately calculated, ensuring that even with uneven pressure distribution, the combined outflow capacity at each location still strictly matches the target flow uniformity requirements.

[0076] This embodiment achieves the technical effect of compensating for pressure loss along the friction path by calculating the pressure distribution along the triple chamber structure and reverse matching the opening area of ​​the damping orifice at each position according to the pressure difference. This ensures that the actual outflow capacity of each nozzle is highly consistent with the target flow rate, thereby eliminating the beneficial effect of cooling deviation in the width direction of the strip.

[0077] In some embodiments, the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalizing chamber of the lower manifold is determined based on the dimensional characteristics of the lower manifold. See [reference needed]. Figure 4 Specifically, it includes:

[0078] Step S401: Based on the size characteristics of the lower manifold, determine the friction resistance coefficient along the water inlet chamber of the lower manifold.

[0079] Specifically, based on the dimensional characteristics of the lower manifold, the inner diameter of the inlet chamber, the pipe wall roughness, and the flow velocity parameters of the cooling water are obtained. According to fluid mechanics principles, the Reynolds number of the cooling water flowing within the chamber is calculated to determine whether the fluid is in a laminar or turbulent state. Based on this flow regime determination and the pipe wall roughness, the frictional resistance coefficient within the inlet chamber is determined by consulting the Moody diagram or using the Colbrook formula. This frictional resistance coefficient quantifies the degree of frictional resistance generated by the pipe wall on the fluid flow and is a fundamental parameter for calculating the pressure drop along the flow path.

[0080] Step S402: Determine the frictional pressure loss along the inlet chamber based on the frictional resistance coefficient.

[0081] Specifically, after obtaining the frictional resistance coefficient along the flow path, and combining the density of the cooling water, average flow velocity, and axial length of the inlet chamber, the cumulative pressure loss caused by friction during the axial flow of cooling water from the inlet to each position is calculated using Darcy's formula. Since the cooling water needs to overcome the frictional force of the pipe wall during flow, the static pressure continuously decreases along the flow direction. This physical phenomenon is quantified as a frictional pressure loss curve along the flow path, revealing the law that the pressure in the inlet chamber decreases with distance.

[0082] Step S403: Based on the frictional pressure loss, the local pressure loss of the primary damping orifice, and the local pressure loss of the secondary damping orifice, determine the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalizing chamber.

[0083] First, based on the frictional pressure loss within the inlet chamber, the static pressure distribution at different axial positions within the inlet chamber is calculated. Second, considering the local pressure loss caused by the abrupt change in cross-section when the fluid flows through the primary damping orifice, the pressure distribution within the buffer chamber is deduced from the pressure within the inlet chamber. Third, combining the local pressure loss when the fluid flows through the secondary damping orifice, the pressure distribution within the equalizing chamber is further calculated. By comprehensively considering the frictional pressure loss along the flow path and the local pressure loss from the two damping orifices, the overall pressure distribution of the cooling water within the inlet chamber, buffer chamber, and equalizing chamber is finally determined.

[0084] This embodiment uses a technical approach of calculating the frictional resistance coefficient along the inlet chamber to derive the frictional pressure loss, and superimposing the local pressure loss of two-stage damping orifices to construct the global pressure distribution of the three chambers. This achieves the technical effect of analyzing the pressure gradient of the complex flow field inside the manifold under laminar cooling, and provides accurate physical parameter basis for the subsequent optimization design of the damping orifice diameter, thereby improving the beneficial effect of manifold flow distribution control.

[0085] In some embodiments, a fluid dynamics mathematical model is constructed based on the non-uniform distribution pattern and the process parameters, see [link to relevant documentation]. Figure 5 ,include:

[0086] Step S501: Based on the non-uniform distribution mode, determine the size distribution characteristics of the primary damping orifice and the secondary damping orifice along the length of the manifold.

[0087] Specifically, based on a preset non-uniform distribution pattern, the opening diameter or opening area data of each primary damping orifice and secondary damping orifice are extracted sequentially along the axial length of the lower manifold. By processing these discrete data, a continuously varying dimensional distribution characteristic along the length of the manifold is generated, clarifying the increasing, decreasing, or fluctuating patterns of the orifice diameter at different locations, thus providing specific geometric boundary conditions for subsequent calculations.

[0088] Step S502: Based on process parameters, determine the inlet water pressure, the cross-sectional area of ​​the equalizing chamber, and the fluid physical properties.

[0089] The process parameters of the current production task are read to determine the total inlet water pressure of the cooling system. Combined with the design drawings of the lower manifold, the specific cross-sectional area of ​​the equalizing chamber is obtained. Simultaneously, based on the real-time temperature and historical water quality data of the cooling water, the physical properties of the fluid, such as density and viscosity, are determined. These physical quantities are then integrated into the boundary condition set required for the simulation calculation.

[0090] Step S503: Based on the size distribution characteristics, inlet water pressure, cross-sectional area of ​​the equalizing chamber, and fluid physical properties, construct a fluid dynamics mathematical model.

[0091] The fluid dynamics mathematical model includes a first-stage damping orifice flow distribution function, a second-stage damping orifice overflow function, a pressure dynamic model of the equalizing chamber, and a nozzle jet velocity function. Specifically, the fluid dynamics mathematical model is established by combining the dimensional distribution characteristics with the inlet water pressure, the cross-sectional area of ​​the equalizing chamber, and the fluid physical properties. This fluid dynamics mathematical model specifically includes: a first-stage damping orifice flow distribution function, used to describe the flow change of cooling water from the inlet chamber into the buffer chamber through the first-stage damping orifice; a second-stage damping orifice overflow function, used to calculate the flow rate of water in the buffer chamber entering the equalizing chamber through the second-stage damping orifice; a pressure dynamic model of the equalizing chamber, used to simulate the accumulation and pressure stabilization process of fluid in the equalizing chamber; and a nozzle jet velocity function, used to correlate the chamber pressure with the nozzle outlet velocity. By simultaneously solving the above functions, the overall flow of cooling water within the triple-chamber structure can be simulated.

[0092] This embodiment utilizes the technique of extracting the dimensional distribution characteristics of the damping orifice along the length of the manifold, and combining the pressure, geometric dimensions, and fluid properties in the process parameters to construct an integrated fluid dynamics model that includes the flow rate of the primary orifice, the overflow of the secondary orifice, the chamber pressure, and the nozzle jet velocity. This achieves the technical effect of mathematically describing the flow process of cooling water in the triple chamber structure of the lower manifold, and provides a high-fidelity simulation calculation basis for subsequent flow uniformity assessment and parameter optimization.

[0093] In some embodiments, a fluid dynamics mathematical model is constructed based on the size distribution characteristics, inlet water pressure, cross-sectional area of ​​the equalizing chamber, and fluid physical properties. (See [reference needed]). Figure 6 ,include:

[0094] Step S601: Establish the flow distribution function of the first-stage damping orifice by utilizing the inlet water pressure, the size distribution characteristics of the first-stage damping orifice, and the fluid physical properties.

[0095] The flow distribution function of the first-stage damping orifice describes the instantaneous flow rate of cooling water flowing from the inlet chamber to the buffer chamber in the lower manifold. Specifically, the flow distribution function of the first-stage damping orifice is established based on the principle of fluid throttling. This function uses the pressure distribution in the inlet chamber as the input power source, and combines the orifice size of the first-stage damping orifice at different axial positions with the density and viscosity properties of the fluid to calculate the instantaneous flow rate of cooling water through each first-stage damping orifice. This function quantifies the dynamic process of water injection from the inlet chamber to the buffer chamber, accurately reflecting the flow rate variation along the flow path when flowing from the high-pressure chamber to the low-pressure chamber.

[0096] Step S602: Establish the overflow function of the secondary damping orifice by utilizing the size distribution characteristics and fluid physical properties of the secondary damping orifice.

[0097] The overflow function of the secondary damping orifice describes the flow rate of cooling water overflowing from the buffer chamber to the pressure equalization chamber in the lower manifold. This function is established based on the fluid overflow principle. Driven by the pressure distribution within the buffer chamber, and considering the orifice size characteristics and fluid properties, the function calculates the flow rate of cooling water entering the pressure equalization chamber from the buffer chamber via the secondary damping orifice. This function describes the fluid transport capacity of the intermediate buffer stage, revealing how the secondary damping orifice performs secondary distribution of the fluid from the inlet chamber, further regulating the flow rate distribution along the pipe.

[0098] Step S603: Establish a dynamic pressure model of the equalization chamber by utilizing the cross-sectional area of ​​the equalization chamber, the fluid physical properties, and the flow rate relationship between the inflow and outflow of the equalization chamber.

[0099] The pressure dynamic model of the equalizing chamber is used to describe the pressure distribution within the equalizing chamber in the lower manifold. This model is established based on the laws of mass and energy conservation. It calculates the dynamic balance between the total flow rate into the equalizing chamber through the secondary damping orifice and the total flow rate out of the equalizing chamber through the nozzles. By combining the cross-sectional area of ​​the equalizing chamber with the fluid compressibility, the real-time pressure distribution within the equalizing chamber is determined. This model is used to evaluate whether the equalizing chamber can effectively suppress pressure fluctuations and ensure the stability of the nozzle injection pressure.

[0100] Step S604: Based on the pressure and fluid physical properties described by the pressure dynamic model of the pressure equalization chamber, establish the nozzle jet velocity function.

[0101] Specifically, a nozzle jet velocity function is established based on Bernoulli's principle. This function converts the pressure inside the equalizing chamber calculated by the dynamic model into the jet velocity at the nozzle outlet. By introducing fluid density properties, this function establishes the conversion relationship between pressure energy and kinetic energy, linking the internal flow state of the manifold with the external cooling effect, and serves as the final output parameter for evaluating cooling capacity.

[0102] Step S605: Construct a fluid dynamics mathematical model based on the flow distribution function of the first-stage damping orifice, the overflow function of the second-stage damping orifice, the pressure dynamic model of the pressure equalization chamber, and the nozzle jet velocity function.

[0103] Specifically, the flow distribution function of the first-stage damping orifice, the overflow function of the second-stage damping orifice, the pressure dynamic model of the pressure equalization chamber, and the nozzle jet velocity function are coupled and solved. By solving the simultaneous equations, a complete fluid dynamics mathematical model is constructed to realize the simulation of the entire flow field from the inlet to the nozzle outlet, and to reproduce the pressure decay and flow redistribution process of cooling water in the triple chamber structure.

[0104] This embodiment achieves the technical effect of stepwise analysis and overall simulation of the complex flow field of the triple chamber of the lower manifold by establishing independent functions describing the characteristics of water inlet throttling, buffer overflow, pressure equalization and stabilization and jet injection, and coupling them to construct a complete fluid dynamics model. It also reveals the collaborative control mechanism of the two-stage damping orifice, thus providing a beneficial effect of providing accurate theoretical model support for the optimization of cooling uniformity.

[0105] To verify the technical effects of the present invention, the specific embodiments of the present invention will be described in detail below in conjunction with a fluid dynamics mathematical model.

[0106] The laminar flow cooling manifold described in this invention is based on a three-stage chamber and a two-stage damping structure. Its fluid dynamics optimization design model defines the system performance through the following functional relationship:

[0107] 1. First-stage damping orifice flow distribution function: describes the flow of cooling water from the inlet chamber into the buffer chamber through non-uniformly distributed damping orifices. Location X Instantaneous flow rate at (along the length of the manifold) for:

[0108]

[0109] In the formula, The flow coefficient of the first-stage damping orifice; For the first-stage damping orifice at position X The diameter at that point; The input pressure of the inlet chamber; For the buffer chamber in position X Pressure at the location; This represents the density of the cooling water.

[0110] 2. Secondary damping orifice overflow function: Describes the flow rate of cooling water from the buffer chamber, after it fills the buffer chamber, through the non-uniform damping orifice to the pressure equalization chamber. for:

[0111]

[0112] In the formula, The flow coefficient of the secondary damping orifice; For the secondary damping orifice at position X The flow area at the point; For the buffer chamber in position X The water level height at the location (relative to the damping orifice); g This is the acceleration due to gravity.

[0113] 3. Dynamic model of pressure in a uniform pressure chamber: describes the pressure inside the uniform pressure chamber. The establishment and distribution of pressure. After the cooling water fills the pressure equalization chamber, it is sprayed out through the nozzle panel. The pressure in the pressure equalization chamber is the result of the combined effect of the overflow from the secondary damping orifice and the outflow from the nozzle. Its pressure distribution... for:

[0114]

[0115] In the formula, β The bulk modulus of water; A3 The cross-sectional area of ​​the pressure equalization chamber is... V3 This represents the characteristic volume of the uniform pressure chamber.

[0116] 4. Nozzle jet velocity function: describes the final velocity of the water jet from the nozzle panel. For position X The corresponding nozzle outlet flow rate. Nozzle outlet velocity. Determined by the pressure and gravitational potential energy of the uniform pressure chamber:

[0117]

[0118] In the formula, This refers to the nozzle flow coefficient. This is the inherent height of the nozzle; For optional nozzle panel height fine-tuning.

[0119] 5. Cooling Uniformity Evaluation Function: An index that quantifies the cooling non-uniformity in the width direction of the strip. U .

[0120]

[0121] in, L This refers to the effective cooling length of the manifold; For position X Cooling water mass flow rate at the location; A n This refers to the cross-sectional area of ​​a single nozzle outlet. q n This represents the average mass flow rate in the width direction.

[0122] 6. Comprehensive optimization objective function: Couple the above relationships and minimize them to optimize the non-uniform arrangement parameters of the damping holes.

[0123]

[0124] In the formula, the first term is the pressure gradient penalty term, which aims to minimize the pressure change along the length of the pressure equalization chamber; the second term is the pressure setting deviation term; and the third term is the cooling uniformity term. These are the corresponding weighting coefficients; RThis is a regularization term used to constrain design variables, such as the variance of the damping orifice diameter or area. It adjusts the non-uniform distribution parameters of the primary and secondary damping orifices. d d1 (X) and A d2 (X) Minimize objective function ψ This allows us to obtain a manifold design scheme with optimal cooling uniformity under specific operating conditions.

[0125] In some embodiments, see Figure 7 Based on the basic fluid dynamics mathematical model, a comprehensive evaluation function for the lower manifold is constructed, including:

[0126] Step S701: Based on the fluid dynamics mathematical model, determine the flow distribution data of cooling water along the width direction of the strip.

[0127] Specifically, the established fluid dynamics mathematical model is run, and the current boundary conditions and damping orifice parameters are input for numerical solution. The output is the cooling water flow rate value corresponding to each nozzle along the strip width direction. These discrete cooling water flow rate values ​​are integrated into a flow distribution dataset, showing the variation of the flow rate of each nozzle along the strip, providing a data foundation for evaluating the cooling effect.

[0128] Step S702: Based on the flow distribution data, determine the evaluation index of cooling uniformity in the width direction of the strip.

[0129] The evaluation index is used to quantify the cooling non-uniformity in the strip width direction. Specifically, statistical analysis is performed on the flow distribution data to extract characteristic values ​​representing the degree of flow dispersion. The cooling uniformity evaluation index is determined by calculating the deviation between the flow rate of each nozzle and the target flow rate, or by statistically analyzing the fluctuation range of the flow distribution. This cooling uniformity evaluation index transforms the complex flow distribution curve into a set of quantifiable values, which are used to objectively evaluate the cooling uniformity level under the current damping orifice configuration.

[0130] Step S703: Based on the flow distribution data and cooling uniformity evaluation index, construct a comprehensive evaluation function for the lower manifold.

[0131] The comprehensive evaluation function includes a pressure gradient penalty term, a pressure setting deviation term, and a cooling uniformity optimization term. Specifically, a multi-dimensional comprehensive evaluation function for the lower manifold is constructed. This function not only includes optimization terms characterizing cooling uniformity but also introduces a pressure gradient penalty term to prevent excessive pressure gradients within the chamber from causing structural stress risks, and a pressure setting deviation term to limit the degree to which the operating pressure deviates from the design conditions. By assigning weight coefficients to different terms and summing them, a comprehensive evaluation function is constructed; the smaller the value, the better the cooling uniformity and the more stable and safer the system operation.

[0132] This embodiment achieves the technical effect of quantifying the complex cooling effect and system safety into a single optimization objective by extracting flow distribution data from the fluid dynamics model, calculating the uniformity index, and constructing a comprehensive evaluation function in combination with the pressure safety term. This achieves the beneficial effect of comprehensively evaluating cooling performance and guiding the optimization algorithm to search in the direction of synergistic improvement of uniformity and stability.

[0133] In some embodiments, see Figure 8 Based on flow distribution data, the evaluation index for cooling uniformity in the strip width direction is determined, including:

[0134] Step S801: Determine the actual cooling water flow density based on the flow distribution data.

[0135] Specifically, based on the flow distribution data, the volumetric flow rate of each nozzle is converted into the water flow rate per unit area, i.e., the actual cooling water flow density. This step takes into account the nozzle coverage area, converting the flow rate data into a water flow density parameter that directly corresponds to the cooling intensity, thus more realistically reflecting the distribution of cooling capacity received by the strip surface.

[0136] Step S802: Determine the deviation value of the water flow density based on the actual cooling water flow density.

[0137] The water flow density deviation value is the difference between the actual cooling water flow density and the target cooling water flow density. Specifically, the target cooling water flow density is set according to the production process requirements, and the difference between the actual cooling water flow density and the target value at each nozzle position is calculated to obtain the water flow density deviation value. This water flow density deviation value reflects the areas where local cooling is too strong or too weak, and serves as the basis for evaluating the degree of cooling unevenness.

[0138] Step S803: Determine the cooling uniformity evaluation index in the strip width direction based on the deviation value and the preset weighting coefficient in the strip width direction.

[0139] The evaluation index for cooling uniformity includes at least one of the maximum deviation value or root mean square error. Specifically, the deviation values ​​across the entire width are weighted statistically using preset weighting coefficients. These weighting coefficients can be adjusted according to the control precision requirements of different regions of the strip, for example, higher weighting for the central region and lower weighting for the edge regions. The maximum deviation value or root mean square error of all deviation values ​​is calculated and used as the evaluation index for cooling uniformity. The maximum deviation value reflects extreme points of cooling unevenness, while the root mean square error reflects the overall level of uniformity.

[0140] This embodiment achieves a refined and differentiated evaluation of cooling effect by converting flow rate data into water flow density and calculating its deviation from the target value, and then using a weighted solution to obtain the uniformity evaluation index. This results in the ability to sensitively identify local cooling defects and accurately reflect the overall uniformity status.

[0141] In some embodiments, when the comprehensive evaluation function is minimized, the optimal distribution parameters of the primary damping orifice and the secondary damping orifice are obtained. See [reference needed]. Figure 9 ,include:

[0142] Step S901: Based on the comprehensive evaluation function, determine the objective variables and constraints of the optimization problem.

[0143] The target variables include the diameter distribution parameters of the primary damping orifice and the area distribution parameters of the secondary damping orifice. Specifically, the optimization problem is standardized, and the variables to be solved are clearly defined as the axial distribution parameters of the diameter of the primary damping orifice and the axial distribution parameters of the area of ​​the secondary damping orifice. Simultaneously, strict constraints are set based on machining limits, anti-clogging requirements, and strength requirements, such as upper and lower limits of the orifice diameter and the minimum distance between adjacent orifices, to ensure the manufacturability of the optimization results in practical engineering.

[0144] Step S902: Determine the value of the target variable based on the target variable and constraints.

[0145] The objective variable is defined as the optimal combination of parameters that minimizes the comprehensive evaluation function while satisfying the constraints. Specifically, a numerical optimization algorithm is invoked to continuously adjust the values ​​of the objective variable within the feasible region defined by the constraints. After each adjustment, the cooling effect is recalculated using the fluid dynamics mathematical model, and the result is substituted into the comprehensive evaluation function to calculate the evaluation value. After multiple iterative searches, when a set of parameters is found that minimizes the value of the comprehensive evaluation function without violating any constraints, this set of parameters is locked as the objective variable value.

[0146] Step S903: Based on the target variable values ​​and the non-uniform distribution pattern, obtain the optimal distribution parameters of the primary damping orifice and the secondary damping orifice.

[0147] Specifically, the obtained optimal target variable values ​​are mapped back to specific physical distribution patterns. For example, the diameter distribution parameters are transformed into specific aperture numerical sequences, and the area distribution parameters are transformed into specific opening shapes and dimensions. Finally, the optimal distribution parameters for the primary and secondary damping orifices are output. These optimal distribution parameters specify the specific aperture size and axial installation position of each damping orifice, which guides the subsequent manufacturing or configuration of the manifold.

[0148] This embodiment achieves the technical effect of obtaining a better cooling effect configuration scheme under the premise of meeting engineering manufacturing constraints by clearly defining the variables and constraints of the optimization problem and searching for the optimal parameter combination with the goal of minimizing the function. It also achieves the beneficial effects of significantly reducing the cost of manual design trial and error and solving the problem of uneven cooling in the width direction of strip steel.

[0149] To more intuitively illustrate the non-uniform distribution mode and its specific parameter calculation method provided in the embodiments of this application, specific embodiments of the damping orifice distribution parameters are given below in conjunction with several typical working conditions. (See also...) Figures 10-15 .

[0150] Example 1: Sparse distribution on the inlet side and dense distribution on the sealing side (corresponding to uniform cooling condition with water inlet on one side)

[0151] This distribution configuration is suitable for single-sided inlet manifolds, used to correct for uneven flow distribution caused by pressure drop along the flow direction. It is suitable for standard uniform cooling of wide strip steel (e.g., 2250 mm wide).

[0152] Design strategy: Utilize the synergistic effect of the dense distribution in the middle and sparse distribution at both ends of the two-stage strip to centrally correct the inherent cooling difference between the middle and the edge of the strip.

[0153] Primary damping orifice: A distribution pattern of denser orifices in the middle and sparser orifices at both ends is adopted. The base orifice diameter is designed to be 10mm, and the orifice diameter variation along the length of the manifold follows the following formula:

[0154]

[0155] in, m 1 represents the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 1 is 0.2. The maximum aperture at the center position (1125mm) is 12mm, and the aperture at the edge positions of 0mm and 2250mm is 10mm.

[0156] Secondary damping orifice: Also designed with a denser middle section and sparser ends, the reference orifice diameter is 6mm, and the orifice diameter variation follows the following formula:

[0157]

[0158] in, m 2 is the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 2 is 0.25. The maximum aperture at the center position (1125mm) is 7.5mm, and the aperture at the edge positions of 0mm and 2250mm is 6mm.

[0159] It can be controlledm 1. m 2. The specific values ​​of the reference diameter and cross-sectional area are used to achieve the same "increase the middle and stabilize the two ends" flow distribution mode at both levels, which can synergistically suppress the risk of ultra-coldness in the middle of the strip and jointly improve the overall cooling uniformity.

[0160] Example 2: Dense distribution in the middle and sparse distribution at both ends (corresponding to enhanced cooling in the middle)

[0161] This distribution pattern is suitable for applications requiring enhanced cooling intensity in the middle of the strip or where the edges of the strip dissipate heat quickly and require reduced cooling water. It is also suitable for situations where there is a specific need to compensate for the non-uniformity of the strip cooling temperature profile, such as for thick strips where edge insulation is particularly important.

[0162] Design strategy: The complementary regulation type is either dense in the middle and sparse at both ends, or sparse in the middle and dense at both ends. The primary orifice increases the flow in the middle to supplement the main cooling zone, selecting a dense middle and sparse at both ends. The secondary orifice restricts the flow at the edges to protect specific areas, selecting a sparse middle and dense at both ends, thus forming a complementary system.

[0163] Primary damping orifice:

[0164] Adopting a dense distribution pattern in the middle and sparse distribution at both ends, the reference diameter of the damping orifice is designed to be 6mm, and the orifice diameter variation along the length of the manifold follows the following formula:

[0165]

[0166] in, m 1 represents the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 1 is 0.5. The maximum aperture at the center position (1125mm) is 9mm, and the aperture at the edge positions of 0mm and 2250mm is 6mm.

[0167] Secondary damping orifice:

[0168] The design adopts a sparse-in-the-middle and dense-at-both-ends pattern. The base diameter of the damping orifice is 10mm, and the orifice diameter variation follows the formula below:

[0169]

[0170] in, m 2 is the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 2 is -0.1. The minimum aperture at the center position (1125mm) is 5.4mm, and the aperture at the edge positions of 0mm and 2250mm is 6mm.

[0171] The first stage provides strong cooling capacity at the center, while the second stage provides strong flow guarantee at the edges. The combined effect of the two stages can create a more complex cooling curve in the width direction, providing more flexible means for specific steel grades or defect control (such as edge overcooling).

[0172] Example 3: Sparse distribution in the middle and dense distribution at both ends (corresponding to edge-enhanced cooling conditions)

[0173] This distribution pattern is suitable for the production of special steel grades where the edge temperature drop is delayed or requires strong edge cooling. The single-sided flow compensation type features both a sealed inlet side and a sparse inlet side distribution, systematically increasing the orifice size / area along the flow direction to counteract pressure loss along the flow path and achieve spatial uniformity of the final flow rate.

[0174] Primary damping orifice:

[0175] A dense distribution pattern is adopted on the inlet side and a sparse distribution pattern on the sealing side. The reference diameter of the damping orifice is designed to be 8mm, and the orifice diameter variation along the length of the manifold follows the following formula:

[0176]

[0177] in, m 1 represents the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 1 is 0.25, the diameter of the hole at the center position (1125mm) is 9mm, the diameter of the hole at the 0mm position on the water inlet side is 10mm, and the diameter of the hole at the 2250mm position on the water sealing side is 8mm.

[0178] Secondary damping orifice:

[0179] The design features a dense distribution pattern on the inlet side and a sparse distribution pattern on the sealing side. The base diameter of the damping orifice is 8mm, and the orifice diameter variation follows the formula below:

[0180]

[0181] in, m 2 is the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 2 is 0.25, the diameter of the hole at the center position (1125mm) is 9mm, the diameter of the hole at the 0mm position on the water inlet side is 10mm, and the diameter of the hole at the 2250mm position on the water sealing side is 8mm.

[0182] A larger orifice is used on the inlet side to limit excess flow under high pressure, while the orifice diameter gradually decreases towards the sealing side to compensate for insufficient flow caused by low pressure. Through two stages of adjustment in the same direction, the aim is to ultimately flatten the pressure distribution in the pressure equalization chamber, thereby ensuring uniform flow rate across the nozzle width.

[0183] Example 4: Distribution of primary inlet water seal with water-retaining and secondary intermediate seal with sparse ends (corresponding to special temperature drop curve conditions)

[0184] This distribution pattern is suitable for applications with extremely high inlet pressure or where correction of specific flow field deviations is required. It is a combined, non-uniform regulating type, with a primary inlet seal that is water-repellent and a secondary design that is denser in the middle and sparser at both ends. It is suitable for comprehensive adjustments or complex processes targeting a specific "bi-peak" cooling curve. The primary orifice is mainly used to compensate for pressure drop in the flow direction, while the secondary orifice is used to correct symmetrical cooling defects in the width direction.

[0185] Primary damping orifice:

[0186] A dense distribution pattern is adopted on the inlet side and a sparse distribution pattern on the sealing side. The reference diameter of the damping orifice is designed to be 10mm, and the orifice diameter variation along the length of the manifold follows the following formula:

[0187]

[0188] in, m 1 represents the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 1 is 0.25, the diameter of the hole at the center position (1125mm) is 11.25mm, the diameter of the hole at the 0mm position on the water inlet side is 12.5mm, and the diameter of the hole at the 2250mm position on the water sealing side is 10mm.

[0189] Secondary damping orifice:

[0190] The design employs a sparse inlet side and a dense seal side configuration. The baseline diameter of the damping orifice is 6mm, and the orifice diameter variation follows the formula below:

[0191]

[0192] in, m 2 is the distribution coefficient, with a value ranging from -0.5 to 0.5. Taking a width of 2250mm as an example... m 2 is 0.25, at the center position (1125mm), the orifice diameter is 5.25mm, at the water inlet side 0mm position, the orifice diameter is 4.5mm, and at the water seal side 2250mm position, the orifice diameter is 6mm.

[0193] This combination is equivalent to independently controlling the flow rate in two dimensions of the manifold: along the flow direction and in the width-symmetrical direction. This helps solve multiple non-uniform cooling problems, such as high inlet pressure and insufficient cooling in the middle section.

[0194] The laminar cooling uniformity optimization device provided in this application will be described in detail below with reference to the accompanying drawings and specific embodiments. Figure 10 and Figure 11This is a schematic diagram of a laminar flow cooling uniformity optimization device provided in an embodiment of this application. This device realizes the practical application of the above-mentioned optimization method through physical structure. The specific structure and function are as follows:

[0195] The inlet pipe 8 is connected at one end to the cooling water source. As the main channel for cooling water to enter the entire laminar flow cooling device, the structural design of the inlet pipe 8 must ensure the stability of fluid transport. One end of the inlet pipe 8 is tightly connected to the main water supply pipeline of the laminar flow cooling system to introduce high-pressure cooling water; the other end is connected to the inlet chamber to transport the cooling water to the distribution core area.

[0196] The inlet chamber, connected to the other end of the inlet pipe 8, is a chamber formed by the internal space of the inner pipe 1. The side wall of the inner pipe 1 has several non-uniformly distributed primary damping holes 7. The distribution parameters of these primary damping holes are obtained using the laminar flow cooling uniformity optimization method described above. The inlet chamber is the component that achieves the first-stage flow distribution in this device. Unlike traditional uniformly perforated lower manifolds, the distribution parameters of these primary damping holes 7, including the hole diameter and axial position, are not set empirically but calculated using the laminar flow cooling uniformity optimization method described in the previous embodiment. The non-uniform distribution pattern determined by this laminar flow cooling uniformity optimization method can actively compensate for the frictional pressure loss generated by the cooling water flowing in the inlet chamber, suppress the flow rate in the high-pressure area on the inlet side, and compensate for the flow rate in the low-pressure area on the sealing side, ensuring that the flow rate of cooling water flowing out from different positions in the inlet chamber tends to be consistent, thus laying the foundation for subsequent uniform cooling.

[0197] The buffer chamber is connected to the inlet chamber, such as... Figure 10 As shown, the space between the inner tube 1 and the outer tube 2 forms an interval chamber, and the outer wall of the inner tube 1 and the inner wall of the outer tube 2 are connected by a secondary damping plate 5. The outer tube 2 is fixed in a suitable position by a bracket 3. The secondary damping plate 5 has several non-uniformly distributed secondary damping holes 6, which divide the interval chamber into two chambers. The chamber away from the nozzle is a buffer chamber, and the upper wall of the buffer chamber has several non-uniformly distributed secondary damping holes 6. The distribution parameters of the secondary damping holes 6 are obtained using the laminar flow cooling uniformity optimization method described above. The buffer chamber, as an intermediate transition link, receives cooling water from the primary damping holes 7, playing a role in initial pressure stabilization and flow diversion. The secondary damping holes on the upper wall of the buffer chamber also perform secondary fine control of the fluid based on the non-uniform distribution parameters calculated by the optimization algorithm. By coordinating the adjustment of the opening areas of the primary damping holes and the secondary damping holes 6, the flow deviation caused by the previous stage error or the internal flow field disturbance of the chamber is further corrected, achieving secondary precise distribution of cooling water flow.

[0198] The equalizing chamber is connected to the buffer chamber. Cooling water overflows into the equalizing chamber through the secondary damping orifice. This chamber acts as a buffer and rectification unit, utilizing its large volume to receive fluid from the buffer chamber and conduct momentum exchange and mixing within the chamber. This eliminates local high-speed jets and pressure fluctuations, maintaining a highly stable pressure field within the chamber along the width of the strip, thus providing a stable water supply pressure environment for the nozzle.

[0199] Nozzle panel 4 is located outside the pressure equalization chamber, away from the buffer chamber. Several nozzles are mounted on nozzle panel 4, serving as the final element to perform the cooling action. The nozzles communicate with the interior of the pressure equalization chamber, spraying the pressure-stabilized cooling water in a specific flow pattern, such as laminar flow, onto the surface of the strip traveling below. The non-uniform design of the upstream two-stage damping orifice ensures the uniformity of pressure distribution within the pressure equalization chamber, thereby guaranteeing the consistency of the outflow rate from each nozzle, thus achieving highly uniform cooling along the width direction of the strip.

[0200] Specifically, cooling water is input into the inlet chamber at an initial set pressure via the inlet pipe 8. Within the inlet chamber, the static pressure gradually decreases due to frictional resistance as the cooling water flows axially. Because the primary damping orifices 7 on the sidewall of the inlet chamber employ non-uniform distribution parameters determined by the aforementioned optimization method—for example, smaller or sparser orifices near the inlet and larger or denser orifices further away—the local resistance in the high-pressure region increases, while the local resistance in the low-pressure region decreases. This provides reverse compensation for the flow rate in the first stage of distribution, making the flow distribution into the buffer chamber more uniform. Subsequently, the cooling water enters the buffer chamber via the primary damping orifices 7. The buffer chamber acts as a pressure stabilizer and transition chamber. The secondary damping orifices on its upper wall also perform secondary fine-tuning of the fluid based on non-uniform distribution parameters, further correcting flow deviations caused by errors in the preceding stage or disturbances in the internal flow field. After two stages of damping adjustment, the cooling water overflows into the equalizing chamber. The equalizing chamber, utilizing its large volume and specific cross-sectional area, effectively eliminates turbulent pulsations and pressure fluctuations, forming a highly stable pressure field. Ultimately, driven by stable pressure, the cooling water is ejected from the nozzles on the nozzle panel at a consistent flow rate and volume, achieving highly uniform cooling of the strip across its width. This device, through a combination of physical structure and optimized parameters, actively compensates for pressure loss along the pipe and solves the problem of flow inclination in traditional manifolds.

[0201] This embodiment employs a non-uniformly distributed primary and secondary damping orifices, designed based on the aforementioned optimization method, to create the inlet chamber and buffer chamber. Combined with the rectification and pressure stabilization effect of the pressure equalization chamber, and utilizing the technical means of synergistic compensation of fluid pressure loss along the flow path by the two-stage damping orifices, it achieves the technical effect of highly consistent cooling water flow rate and stable flow field at each nozzle. This results in significantly improving the cooling uniformity in the strip width direction, enhancing cooling accuracy and product quality, while ensuring the long-term stable operation of the device.

[0202] It should be noted that the laminar cooling uniformity optimization device provided in the above embodiments is only illustrated by the division of the above functional modules when realizing the cooling uniformity control function. In practical applications, the above functions can be assigned to different functional modules as needed, that is, the internal structure of the computer device can be divided into different functional modules to complete all or part of the functions described above. In addition, the laminar cooling uniformity optimization device and the laminar cooling uniformity optimization method embodiments provided in the above embodiments belong to the same concept, and the specific implementation process can be found in the method embodiments, which will not be repeated here.

[0203] Through the above description of the embodiments, those skilled in the art will understand that, for the sake of convenience and brevity, only the division of the above functional modules is used as an example. In actual applications, the above functions can be assigned to different functional modules as needed, that is, the internal structure of the device can be divided into different functional modules to complete all or part of the functions described above.

[0204] In the embodiments provided in this application, it should be understood that the disclosed apparatus and methods can be implemented in other ways. For example, the apparatus embodiments described above are merely illustrative; for instance, the division of modules or units is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple units or components may be combined or integrated into another apparatus, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be through some interfaces; the indirect coupling or communication connection between apparatuses or units may be electrical, mechanical, or other forms.

[0205] The above description is only a specific implementation of this application, but the protection scope of this application is not limited thereto. Any changes or substitutions that can be easily conceived by those skilled in the art within the scope of the technology disclosed in this application should be included within the protection scope of this application.

Claims

1. A method for optimizing laminar flow cooling uniformity, characterized in that, The method includes: Based on the process parameters and cooling requirements of the laminar flow cooling system, the non-uniform distribution pattern of the primary and secondary damping orifices in the lower manifold is determined. The primary and secondary damping orifices are used to jointly regulate the cooling water flow rate. Based on the non-uniform distribution mode and the process parameters, a fluid dynamics mathematical model is constructed. The fluid dynamics mathematical model is used to demonstrate the fluid flow characteristics in the lower manifold with a triple chamber structure. Based on the aforementioned fluid dynamics mathematical model, a comprehensive evaluation function for the lower manifold is constructed, which is used to evaluate the cooling performance in the width direction of the strip. When the comprehensive evaluation function is minimized, the optimal distribution parameters of the primary damping hole and the secondary damping hole are obtained. The optimal distribution parameters are used to configure the hole size and axial position of the primary damping hole and the secondary damping hole.

2. The method according to claim 1, characterized in that, Based on the process parameters and cooling requirements of the laminar flow cooling system, the non-uniform distribution pattern of the primary and secondary damping orifices in the lower manifold is determined, including: Based on the process parameters of the laminar flow cooling system, the dimensional characteristics and structural constraints of the lower manifold are determined. Based on the cooling requirements, the target flow distribution characteristics of the cooling water in the strip width direction are determined; Based on the size characteristics and structural constraints of the lower manifold and the target flow distribution characteristics, a non-uniform distribution pattern of the primary damping orifice and the secondary damping orifice is determined. The primary damping orifice is opened on the side wall of the inlet chamber in the lower manifold, and the secondary damping orifice is opened on the upper wall of the buffer chamber in the lower manifold. The non-uniform distribution pattern includes at least one or a combination of the following: dense in the middle and sparse at both ends; sparse in the middle and dense at both ends; dense on the inlet side and sparse on the sealing side; or sparse on the inlet side and dense on the sealing side.

3. The method according to claim 2, characterized in that, The determination of the non-uniform distribution pattern of the primary damping orifice and the secondary damping orifice based on the size characteristics and structural constraints of the lower manifold and the target flow distribution characteristics includes: Based on the dimensional characteristics of the lower manifold, the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalizing chamber within the lower manifold is determined. Based on the pressure distribution and the target flow distribution characteristics, the opening area or aperture of the primary damping orifice and the secondary damping orifice at different locations is determined, so that the actual outflow capacity of the primary damping orifice and the secondary damping orifice matches the target flow distribution characteristics.

4. The method according to claim 3, characterized in that, The determination of the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalizing chamber of the lower manifold based on its dimensional characteristics includes: Based on the dimensional characteristics of the lower manifold, the frictional resistance coefficient along the water inlet chamber of the lower manifold is determined; Based on the frictional resistance coefficient along the flow path, the frictional pressure loss along the flow path of the inlet chamber is determined. Based on the frictional pressure loss, the local pressure loss of the primary damping orifice, and the local pressure loss of the secondary damping orifice, the pressure distribution along the flow path of the inlet chamber, buffer chamber, and equalizing chamber is determined.

5. The method according to claim 1, characterized in that, The construction of a fluid dynamics mathematical model based on the non-uniform distribution pattern and the process parameters includes: Based on the non-uniform distribution pattern, the size distribution characteristics of the primary damping orifice and the secondary damping orifice along the length of the manifold are determined; Based on the process parameters, the inlet water pressure, the cross-sectional area of ​​the equalizing chamber in the lower manifold, and the fluid physical properties are determined. Based on the size distribution characteristics, the inlet water pressure, the cross-sectional area of ​​the pressure equalization chamber, and the fluid physical properties, a fluid dynamics mathematical model is constructed. The fluid dynamics mathematical model includes the flow distribution function of the first-stage damping orifice, the overflow function of the second-stage damping orifice, the pressure dynamic model of the pressure equalization chamber, and the nozzle jet velocity function.

6. The method according to claim 5, characterized in that, The fluid dynamics mathematical model is constructed based on the size distribution characteristics, the inlet water pressure, the cross-sectional area of ​​the pressure equalization chamber, and the fluid physical properties, including: Using the inlet water pressure, the size distribution characteristics of the first-stage damping orifice, and the fluid physical properties, a flow distribution function for the first-stage damping orifice is established. This flow distribution function describes the instantaneous flow rate of cooling water in the lower manifold from the inlet chamber into the buffer chamber. Using the size distribution characteristics and fluid physical properties of the secondary damping orifice, an overflow function for the secondary damping orifice is established. The overflow function for the secondary damping orifice is used to describe the flow rate of cooling water overflowing from the buffer chamber to the pressure equalization chamber in the lower manifold. Using the cross-sectional area of ​​the equalizing chamber, the physical properties of the fluid, and the flow rate relationship between the inflow and outflow from the equalizing chamber, a pressure dynamic model of the equalizing chamber is established. This pressure dynamic model is used to describe the pressure distribution within the equalizing chamber in the lower manifold. Based on the pressure described by the pressure dynamic model of the equalizing chamber and the physical properties of the fluid, a nozzle jet velocity function is established. A fluid dynamics mathematical model is constructed based on the flow distribution function of the first-stage damping orifice, the overflow function of the second-stage damping orifice, the pressure dynamic model of the equalizing chamber, and the jet velocity function of the nozzle.

7. The method according to claim 1, characterized in that, The comprehensive evaluation function for the lower manifold, based on the aforementioned fluid dynamics mathematical model, includes: Based on the aforementioned fluid dynamics mathematical model, the flow distribution data of cooling water along the width direction of the strip are determined; Based on the flow distribution data, a cooling uniformity evaluation index is determined in the strip width direction. The evaluation index is used to quantify the cooling non-uniformity in the strip width direction. Based on the flow distribution data and cooling uniformity evaluation index, a comprehensive evaluation function for the lower manifold is constructed. The comprehensive evaluation function includes a pressure gradient penalty term, a pressure setting deviation term, and a cooling uniformity optimization term.

8. The method according to claim 7, characterized in that, The step of determining the cooling uniformity evaluation index in the strip width direction based on the flow distribution data includes: Based on the flow distribution data, the actual cooling water flow density is determined; Based on the actual cooling water flow density, a deviation value for the water flow density is determined, wherein the deviation value is the difference between the actual cooling water flow density and the target cooling water flow density; Based on the deviation value and the preset weighting coefficient in the strip width direction, a cooling uniformity evaluation index in the strip width direction is determined. The cooling uniformity evaluation index includes at least one of the maximum deviation value or the root mean square error.

9. The method according to claim 1, characterized in that, When the comprehensive evaluation function is minimized, the optimal distribution parameters of the primary damping orifice and the secondary damping orifice are obtained, including: Based on the comprehensive evaluation function, the objective variables and constraints of the optimization problem are determined. The objective variables include the first-level damping orifice diameter distribution parameters and the second-level damping orifice area distribution parameters. Based on the target variable and constraints, the value of the target variable is determined. The target variable is the optimal combination of parameters that minimizes the comprehensive evaluation function and satisfies the constraints. Based on the target variable values ​​and the non-uniform distribution pattern, the optimal distribution parameters of the primary damping orifice and the secondary damping orifice are obtained.

10. A laminar flow cooling uniformity optimization device, characterized in that, include: The water inlet pipe is connected at one end to the cooling water source; The water inlet chamber is connected to the other end of the water inlet pipe. The side wall of the water inlet chamber is provided with a plurality of non-uniformly distributed primary damping holes. The distribution parameters of the primary damping holes are obtained by the method described in any one of claims 1-9. A buffer chamber is connected to the water inlet chamber. The side wall of the buffer chamber is provided with a plurality of non-uniformly distributed secondary damping holes. The distribution parameters of the secondary damping holes are obtained by the method described in any one of claims 1-9. The equalizing chamber is connected to the buffer chamber; The nozzle panel is located on the outside of the equalizing chamber, away from the buffer chamber.

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