A heat exchanger dual-fluid temperature simulation calculation method, device, vehicle and medium

Abstract

The present invention relates to the field of automotive thermal management simulation technology, and discloses a heat exchanger dual-fluid temperature simulation calculation method, device, vehicle, and medium. The method includes: simplifying the heat exchanger into a porous medium region, the porous medium region being a geometric structure adapted to the physical size of the heat exchanger; meshing the region where the heat exchanger is located to obtain a first mesh region containing the porous medium region and a second mesh region not containing the porous medium region; performing flow field simulation on the first mesh region and the second mesh region, and coupling solving the fluid temperature field of the first mesh region to obtain the dual-fluid temperature of the heat exchanger. After simplifying the heat exchanger into a porous medium region adapted to its physical size, the present invention divides each mesh region and performs flow field simulation and coupling solution, which can realize simulation calculation of the fluid temperature on both sides of the heat exchanger, not only shortening the calculation cycle, but also making the simulation results more accurately reflect the actual working state of the heat exchanger, greatly improving the simulation calculation accuracy.

Description

Technical Field

[0001] The present invention relates to the technical field of automobile thermal management simulation, and in particular to a heat exchanger dual-fluid temperature simulation calculation method, device, vehicle and medium. Background Art

[0002] The automotive thermal management simulation calculation field is used to perform three-dimensional simulation analysis of the flow field and temperature field of the entire vehicle to ensure the rationality of the airflow distribution and temperature field distribution in different areas of the vehicle. Among them, the temperature and flow field in the engine compartment are the most important.

[0003] Currently, heat exchangers, as critical components in automobiles, are typically located at the front end of the engine compartment, serving as the inflow channel for the fluid within the engine compartment. The velocity, pressure, and temperature of the fluid passing through the heat exchanger significantly influence the flow and temperature field calculations within the vehicle's engine compartment, with a strong front-end-to-back correlation between the two. Heat exchangers in automotive thermal management systems primarily utilize liquid and gas as two fluid media for heat exchange, often requiring simultaneous calculation of the temperatures of the fluids on both sides of the heat exchanger under specific operating conditions. Simulations involving dual-fluid regions, where two temperatures must be solved simultaneously, require the use of a special coupled set of equations to simultaneously solve for the temperatures of the cold and hot fluids on the grid. Due to the complex, irregular piping structure and numerous fins of the heat exchanger, the front-to-back flow paths are very narrow. Using the commonly used single-fluid modeling approach, the heat exchanger is simplified into a porous medium region, solving for the temperature distribution on the air side, but not the liquid side.

[0004] Therefore, given the importance of heat exchanger simulation calculations in automotive thermal management simulations and the difficulty of the current single-fluid modeling method in simultaneously calculating the liquid-side fluid temperature, there is an urgent need for a dual-fluid three-dimensional simulation solution that can simultaneously calculate the fluid temperature on both sides of the automotive heat exchanger, so as to accurately calculate the temperature distribution of the fluids on both sides of the heat exchanger after heat exchange, thereby improving the calculation accuracy of automotive thermal management simulations. Summary of the Invention

[0005] In view of this, the present invention provides a method, device, vehicle and medium for simulating and calculating the dual-fluid temperature of a heat exchanger to solve the problem that the existing technology is difficult to realize the simulation calculation of the fluid temperature on both sides of the heat exchanger, resulting in low simulation calculation accuracy and difficulty in meeting high-precision simulation requirements.

[0006] In a first aspect, the present invention provides a method for simulating and calculating the temperature of a heat exchanger using two fluids, the method comprising:

[0007] Simplify the heat exchanger into a porous medium region, where the porous medium region is a geometric structure adapted to the physical size of the heat exchanger;

[0008] The heat exchanger region is meshed to obtain a first mesh region containing a porous medium region and a second mesh region not containing a porous medium region. The first mesh region includes a cold-side mesh region and a hot-side mesh region. The cold-side mesh region and the hot-side mesh region are two sets of independent mesh regions that overlap in spatial position. The fluid types in the cold-side mesh region and the hot-side mesh region are different.

[0009] The flow field simulation is performed on the first grid area and the second grid area, and the fluid temperature field of the first grid area is coupled and solved to obtain the dual fluid temperatures of the heat exchanger, which include the cold side fluid temperature and the hot side fluid temperature.

[0010] The present invention replaces complex entities with geometric structures, specifically simplifying the heat exchanger into a porous medium area that is adapted to its physical size, which can effectively reduce the number of subsequent grids and thus significantly shorten the simulation cycle; and the area where the heat exchanger is located is gridded, flow field simulated and coupled solved separately, which can accurately capture the dynamic changes of the hot side fluid of the heat exchanger from high temperature to low temperature and the cold side fluid from low temperature to high temperature, and then realize the temperature simulation calculation of the dual fluid of the heat exchanger, which not only ensures the simulation reliability, but also improves the simulation calculation accuracy of the temperature field, greatly meeting the high-precision simulation requirements of the dual fluid temperature of the heat exchanger.

[0011] In an optional embodiment, performing flow field simulation on the first grid area and the second grid area includes:

[0012] Merging the first grid area into the second grid area to obtain a grid area to be simulated, and establishing a data exchange channel for data exchange between the cold-side grid area and the second grid area;

[0013] The grid area to be simulated is simulated based on preset simulation parameters, and the fluid momentum equation is solved to obtain the velocity field and pressure field. The preset simulation parameters at least include fluid physical property parameters such as fluid density, viscosity and specific heat capacity, as well as initial boundary conditions of velocity and pressure.

[0014] The present invention adopts the design of "spatial overlap and mutual independence" of the cold-side grid area and the hot-side grid area, which not only ensures that the flow and heat transfer processes of the two different fluids can be accurately simulated separately, but also, due to the "spatial overlap" feature, truly restores the heat exchange scene of the fluids on both sides of the heat exchanger at the same physical position, thereby making the heat transfer process of the two fluids closer to the actual physical laws, and significantly improving the accuracy of the coupled simulation; at the same time, a data exchange channel is established between the cold-side grid area and the second grid area, which solves the problem of "discontinuous flow parameters between independent grids" and reduces the risk of calculation divergence caused by parameter discontinuity; finally, the simulation design is performed based on the real flow parameters, so that the flow field results are closer to the actual test data, further enhancing the reliability of the flow field results, and laying a high-quality flow data foundation for the subsequent temperature field coupling solution.

[0015] In an optional embodiment, coupling and solving the fluid temperature field in the first grid area to obtain the dual-fluid temperatures of the heat exchanger includes:

[0016] determining a cold fluid velocity distribution in a cold side grid area based on the velocity field and the pressure field, wherein the cold fluid velocity distribution includes a cold fluid velocity in each grid cell;

[0017] Calculating a target heat transfer coefficient based on a preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution. The preset heat transfer performance table is a mapping relationship table obtained through experimental measurement that includes different cold-side fluid mass flow rates and corresponding heat transfer powers;

[0018] Taking the cold-side fluid temperature in the cold-side grid area and the hot-side fluid temperature in the hot-side grid area as unknown quantities, the temperature control equations for each grid unit are constructed respectively. Each temperature control equation is solved based on the target heat transfer coefficient to obtain the cold-side fluid temperature and hot-side fluid temperature of the corresponding grid unit;

[0019] Based on the cold-side fluid temperature and the hot-side fluid temperature of all grid cells in the first grid area, the dual-fluid temperatures of the heat exchanger are obtained.

[0020] The present invention takes into account the differences in cold fluid velocities in different grid units, calculates the local heat transfer coefficient through grid-level velocity distribution, so that the heat transfer power of each grid matches the actual flow rate, and uses each grid unit to separately construct a temperature control equation, which can accurately capture the temperature gradients of the cold and hot side fluids at the microscale, thereby making the dual-fluid temperature distribution closer to the actual heat transfer details inside the heat exchanger; and obtains a preset heat transfer performance table through experimental measurement to directly reflect the actual heat transfer law, so that the target heat transfer coefficient subsequently calculated based on this is more in line with the actual working conditions, further enhancing the reliability of the dual-fluid temperature simulation calculation results; at the same time, the "cold side fluid temperature and hot side fluid temperature are unknown quantities" are solved separately, and the coupling relationship between the two is established through the target heat transfer coefficient, which can avoid the simplified distortion of the fluid characteristics on the other side by the traditional "single fluid model", so that the time or spatial changes of the temperature field are more in line with the actual heat exchange logic, while ensuring the accuracy and reliability of the temperature field calculation, it can provide a high-precision and high-reliability solution for the dual-fluid temperature simulation of the heat exchanger.

[0021] In an optional embodiment, calculating the target heat transfer coefficient according to a preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution includes:

[0022] Determine the cold side fluid inlet temperature and the hot side fluid inlet temperature respectively, and calculate the inlet temperature difference between the cold side fluid inlet temperature and the hot side fluid inlet temperature;

[0023] Determine the global heat transfer coefficient based on the ratio of heat transfer power to inlet temperature difference in the preset heat transfer performance table;

[0024] determining a unit heat transfer coefficient based on a ratio of the global heat transfer coefficient to the total number of grid cells in the first grid area;

[0025] Solve each temperature control equation based on the unit heat transfer coefficient to obtain the cold side fluid temperature and hot side fluid temperature of the grid unit;

[0026] Calculate the current average temperature difference based on the cold side fluid temperature and the hot side fluid temperature of all grid cells, and calculate the current heat exchange power based on the current average temperature difference;

[0027] A heat exchange error is calculated based on the current heat exchange power and the heat exchange power in the preset heat exchange performance table, and a target heat exchange coefficient is determined based on a magnitude relationship between the heat exchange error and a first preset power threshold.

[0028] The present invention splits the global coefficient into each grid unit, so that the heat transfer coefficient of each unit forms an association basis with the flow characteristics of its own position, providing a "grid-level adjustment carrier" for subsequent iterative optimization combined with local flow velocity, and finally achieving a better match between the heat transfer coefficient of each grid unit and the actual flow state, which helps to improve the calculation accuracy of the subsequent temperature field; and through the real-time state of the temperature field, the dynamic adjustment of the heat transfer coefficient is inferred, that is, a process of "solving the current average temperature difference based on the temperature of all grid units, calculating the current heat transfer power, comparing the test power to obtain the error and correct the target heat transfer coefficient" is designed, so as to adapt to the changes in heat transfer characteristics under complex flow, further make the heat transfer coefficient of each unit more matched with the actual flow, and at the same time enhance the adaptability of the changes in heat transfer characteristics under different working conditions; the above scheme ensures the physical authenticity of the target heat transfer coefficient and improves its adaptability to complex working conditions, providing core support for the accurate solution of the dual-fluid temperature field, and ultimately making the heat exchanger temperature simulation results more reliable and closer to engineering practice.

[0029] In an optional embodiment, determining the target heat transfer coefficient based on the magnitude relationship between the heat transfer error and the first preset power threshold includes:

[0030] If the heat transfer error is less than the first preset power threshold, the unit heat transfer coefficient is determined as the target heat transfer coefficient;

[0031] If the heat exchange error is not less than the first preset power threshold, the process returns to the step of solving each temperature control equation based on the unit heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the heat exchange error is less than the first preset power threshold.

[0032] The present invention designs an iterative feedback mechanism to achieve precise calibration of the heat transfer coefficient. Specifically, the heat transfer error is compared with the first preset power threshold to dynamically iteratively determine the target heat transfer coefficient, so that the unit heat transfer coefficient automatically approaches the true value in each cycle, making the target heat transfer coefficient more closely matched with the actual heat transfer capacity of each grid, greatly reducing the calculation error of the local heat transfer coefficient, and further ensuring the credibility of the simulation results.

[0033] In an optional embodiment, the temperature control equation includes a first fluid energy equation for each grid cell in the cold-side grid area and a second fluid energy equation for each grid cell in the hot-side grid area; with the cold-side fluid temperature in the cold-side grid area and the hot-side fluid temperature in the hot-side grid area as unknown quantities, the temperature control equation for each grid cell is constructed separately, including:

[0034] The cold side fluid temperature of the current grid cell in the cold side grid area is taken as an unknown quantity, and the cold flow upstream grid temperature is taken as a known quantity. The first fluid energy equation of the current grid cell is constructed by combining the obtained cold side fluid mass flow rate, cold side fluid specific heat capacity, and unit heat transfer coefficient. The cold flow upstream grid temperature is the fluid temperature of the upstream grid cell in the cold flow direction of the current grid cell.

[0035] The hot side fluid temperature of the current grid cell in the hot side grid area is taken as the unknown quantity, the heat flow upstream grid temperature is taken as the known quantity, and the hot side fluid mass flow rate, hot side fluid specific heat capacity and unit heat transfer coefficient are combined to construct the second fluid energy equation of the current grid cell; among which, the heat flow upstream grid temperature is the fluid temperature of the upstream grid cell in the heat flow direction of the current grid cell.

[0036] The present invention constructs equations with the upstream grid temperature of the cold flow or hot flow as a known quantity to accurately capture the continuous flow of the fluid, so that the distribution of the temperature field strictly follows the energy transfer logic of the fluid flow direction, and the simulation results are closer to the actual temperature evolution process in the heat exchanger; and each grid unit is designed to construct an energy equation separately, further decomposing the heat transfer process to the micro grid scale, which can independently reflect the local heat transfer intensity of the grid and realize fine modeling at the grid level; at the same time, taking into account the differences in the characteristics of the two fluids, the energy equations of the first and second fluids are constructed separately, further ensuring the physical adaptability of the energy equations; in addition, the strong coupling of the two fluids is realized through the unit heat transfer coefficient, which truly restores the microscopic mechanism of "heat transfer from the hot side to the cold side through the solid wall surface", avoids the temperature field drift caused by energy imbalance, and further improves the reliability of the simulation results.

[0037] In an optional embodiment, after coupling and solving the fluid temperature field in the first grid area to obtain the dual-fluid temperatures of the heat exchanger, the dual-fluid temperature simulation calculation method for the heat exchanger further includes:

[0038] Multiply the difference between the hot-side fluid temperature and the cold-side fluid temperature of each grid cell in the first grid area by the target heat transfer coefficient to obtain the corresponding single-grid heat transfer power;

[0039] Sum the heat transfer powers of all single grids to obtain the actual heat transfer power of the heat exchanger;

[0040] Calculate the actual heat transfer error between the actual heat transfer power and the corresponding heat transfer power in the preset heat transfer performance table;

[0041] When the actual heat exchange error is not less than the second preset power threshold, the process returns to the step of solving each temperature control equation based on the target heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the actual heat exchange error is less than the second preset power threshold.

[0042] The present invention takes into account the core design goal of the heat exchanger meeting the overall heat exchange power requirements in actual applications. By summing the heat exchange powers of all single grids to obtain the actual heat exchange power design, the focus is shifted from local temperature to overall performance. The actual heat exchange error is then compared with a second preset power threshold for iterative correction, ensuring that the overall heat exchange capacity of the heat exchanger strictly meets engineering requirements, further improving the calculation accuracy of the dual-fluid temperature simulation.

[0043] In an optional embodiment, the area where the heat exchanger is located is meshed to obtain a first mesh area containing a porous medium area and a second mesh area not containing a porous medium area, including:

[0044] Divide the area where the heat exchanger is located into a volume grid to obtain a volume grid area containing multiple grid cells;

[0045] Based on the current spatial position of the heat exchanger, a first grid area corresponding to the porous medium area is divided from the body grid area;

[0046] The first mesh area is subtracted from the volume mesh area to obtain the second mesh area.

[0047] The present invention first constructs a volume grid containing all areas, and then divides the logic of the first and second grid areas from it, ensuring that the grids of the two areas can maintain continuity at the boundary; and based on the current spatial position of the heat exchanger, the first grid area is divided from the volume grid area, so that the porous medium area and the actual physical position of the heat exchanger are strictly corresponding, thereby ensuring that the path of the fluid flowing through the porous medium area in the subsequent flow field simulation is consistent with the path of the actual fluid flowing through the heat exchanger, providing a high-quality grid foundation for the flow field solution and temperature field coupling of the dual-fluid simulation of the heat exchanger, and helping to improve the stability of the flow field and temperature field solutions.

[0048] In an optional embodiment, after simplifying the heat exchanger into a porous medium region, the heat exchanger two-fluid temperature simulation calculation method further includes:

[0049] Inertial and viscous drag coefficients are added to porous media regions to simulate the resistance of fluid flow through the porous media region.

[0050] By adding inertial resistance coefficient and viscous resistance coefficient to the porous medium area to simulate fluid resistance, the present invention can accurately reproduce the real flow resistance characteristics of the heat exchanger, further improve the accuracy of flow field simulation, and lay a solid foundation for subsequent temperature field coupling solution.

[0051] In a second aspect, the present invention provides a heat exchanger dual-fluid temperature simulation calculation device, the device comprising:

[0052] A simplification module is used to simplify the heat exchanger into a porous medium region, where the porous medium region is a geometric structure adapted to the physical size of the heat exchanger;

[0053] a partitioning module for performing grid division on the area where the heat exchanger is located, obtaining a first grid area including a porous medium area and a second grid area not including a porous medium area, wherein the first grid area includes a cold side grid area and a hot side grid area, wherein the cold side grid area and the hot side grid area are two sets of grid areas that overlap in spatial position and are independent of each other, and the types of fluids in the cold side grid area and the hot side grid area are different;

[0054] The calculation module is used to simulate the flow field of the first grid area and the second grid area, and couple the fluid temperature field of the first grid area to obtain the dual fluid temperature of the heat exchanger, which includes the cold side fluid temperature and the hot side fluid temperature.

[0055] The dual-fluid temperature simulation and calculation device for a heat exchanger of the present invention can effectively reduce the number of subsequent grids and further significantly shorten the simulation cycle by simplifying the heat exchanger into a porous medium area adapted to its physical size; and by gridding the area where the heat exchanger is located, and coupling the flow field simulation and temperature field of the grid area, a stable velocity field and pressure field can be obtained, which not only lays the foundation for the subsequent calculation of the fluid temperature field, but also makes the simulation results more accurately reflect the actual working state of the fluid on both sides of the heat exchanger, greatly improving the accuracy and reliability of the dual-fluid temperature field calculation of the heat exchanger, and at the same time provides an efficient and reliable technical means for the performance evaluation and optimization of the dual-fluid heat exchanger, meeting the high-precision simulation requirements of the dual-fluid temperature of the heat exchanger.

[0056] In a third aspect, the present invention provides a vehicle, comprising a controller, the controller comprising: a memory and a processor, the memory and the processor being communicatively connected to each other, the memory storing computer instructions, and the processor executing the computer instructions to execute a heat exchanger dual-fluid temperature simulation calculation method according to the first aspect or any corresponding embodiment thereof.

[0057] In a fourth aspect, the present invention provides a computer-readable storage medium having computer instructions stored thereon, the computer instructions being used to enable a computer to execute a heat exchanger dual-fluid temperature simulation calculation method according to the first aspect or any corresponding embodiment thereof.

[0058] The heat exchanger dual-fluid temperature simulation calculation method and device of the present invention replace complex entities with geometric structures, specifically simplifying the heat exchanger into a porous medium area adapted to its physical size, which can effectively reduce the number of subsequent grids and thus significantly shorten the simulation cycle; and the area where the heat exchanger is located is gridded, flow field simulated and coupled to solve separately, to obtain stable velocity and pressure fields, which not only lays the foundation for the subsequent calculation of the fluid temperature field, but also makes the simulation results more accurately reflect the actual working state of the fluids on both sides of the heat exchanger, greatly improving the accuracy and reliability of the heat exchanger dual-fluid temperature field calculation, and at the same time providing an efficient and reliable technical means for the performance evaluation and optimization of the dual-fluid heat exchanger, meeting the high-precision simulation requirements of the heat exchanger dual-fluid temperature. BRIEF DESCRIPTION OF THE DRAWINGS

[0059] In order to more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the following briefly introduces the drawings required for use in the specific embodiments or the description of the prior art. Obviously, the drawings described below are some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0060] Figure 1 1 is a flow chart of a method for simulating and calculating the temperature of a heat exchanger using two fluids according to an embodiment of the present invention;

[0061] Figure 2 is a flow chart of another heat exchanger dual-fluid temperature simulation calculation method according to an embodiment of the present invention;

[0062] Figure 3 This is a flow chart of the two-fluid temperature field calculation;

[0063] Figure 4 This is a schematic diagram of the grid of the heat exchanger dual-fluid area and the main calculation area;

[0064] Figure 5 It is a flow chart of the two-fluid temperature field solver algorithm;

[0065] Figure 6 is a schematic diagram of the temperature of the local grid unit;

[0066] Figure 7 2 is a structural block diagram of a heat exchanger dual-fluid temperature simulation calculation device according to an embodiment of the present invention;

[0067] Figure 8 4 is a schematic structural diagram of a vehicle controller according to an embodiment of the present invention. DETAILED DESCRIPTION

[0068] To make the purpose, technical solutions, and advantages of the embodiments of the present invention more clear, the technical solutions in the embodiments of the present invention will be clearly and completely described below in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of this embodiment, not all of them. Based on the embodiments in this embodiment, all other embodiments obtained by those skilled in the art without making creative efforts shall fall within the scope of protection of this embodiment.

[0069] An embodiment of the present invention provides an embodiment of a method for simulating and calculating the temperature of a heat exchanger using two fluids. It should be noted that the steps shown in the flowchart of the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions, and although a logical order is shown in the flowchart, in some cases, the steps shown or described can be executed in an order different from that shown here.

[0070] In this embodiment, a heat exchanger dual-fluid temperature simulation calculation method is provided. Figure 1 FIG. 1 is a flow chart of a method for simulating and calculating the temperature of a heat exchanger using two fluids according to an embodiment of the present invention. Figure 1 As shown, the process includes the following steps:

[0071] Step S101 : simplifying the heat exchanger into a porous medium region, where the porous medium region has a geometric structure that matches the physical size of the heat exchanger.

[0072] In practical applications, directly modeling complex heat exchanger structures (such as fins, pipes, and flow channels) requires billions of meshes due to the fine geometric details (for example, fin spacing of 0.5 to 2 mm), resulting in high computational resource consumption and long simulation cycles. In this example, by simplifying the heat exchanger into a porous medium region and replacing complex solids with geometric structures, the number of meshes can be significantly reduced.

[0073] It should be noted that the specific content of the geometric structure in this embodiment can be adaptively adjusted according to actual needs. For example, the geometric structure is a cuboid, which is only used as an example.

[0074] Step S102 : Meshing the area where the heat exchanger is located to obtain a first mesh area including a porous medium area and a second mesh area not including a porous medium area.

[0075] It should be noted that the specific content of the grid division in this embodiment can be implemented by referring to conventional methods in the field, such as using the snappyHexMesh module (i.e., a grid generation tool) in OpenFOAM (Open Field Operation and Manipulation, an open source computational fluid dynamics library) to implement grid division. The specific implementation method can be referred to the relevant technology and is not limited in detail here.

[0076] In this embodiment, the first grid area includes a cold side grid area and a hot side grid area, wherein the cold side grid area and the hot side grid area are two sets of grid areas that overlap in spatial position and are independent of each other, and the types of fluids in the cold side grid area and the hot side grid area are different; the dual fluid temperatures include the cold side fluid temperature and the hot side fluid temperature.

[0077] Step S103 , performing flow field simulation on the first grid area and the second grid area, and coupling solving the fluid temperature field of the first grid area to obtain the dual fluid temperatures of the heat exchanger.

[0078] In this embodiment, the dual fluid temperatures include a cold-side fluid temperature and a hot-side fluid temperature.

[0079] It should be noted that fluid is a form of matter that can flow, including two major categories: liquid and gas. In practical applications, the flow field (such as velocity field and pressure field) is the core factor affecting heat transfer (such as flow velocity determines the intensity of convective heat transfer). If the traditional fluid simulation method ignores the coupling of the flow field and the temperature field (such as directly assuming the flow velocity distribution), it will cause distortion in the temperature field calculation. In this embodiment, the flow field simulation is first performed until convergence to obtain a stable velocity field and pressure field, and then the temperature field is solved based on this. This ensures that the temperature field calculation is based on the actual flow state (such as the area with high flow velocity has strong convective heat transfer and the temperature change is more significant), avoids the errors caused by the assumption of flow parameters, and makes the simulation results closer to the actual working conditions (such as the high temperature area caused by the low local flow velocity of the heat exchanger can be accurately captured).

[0080] A dual-fluid temperature simulation calculation method for a heat exchanger provided in an embodiment of the present invention replaces complex entities with geometric structures, specifically simplifying the heat exchanger into a porous medium area adapted to its physical size, which can effectively reduce the number of subsequent grids and thus significantly shorten the simulation cycle; and the area where the heat exchanger is located is gridded, flow field simulated and coupled to solve separately, to obtain stable velocity and pressure fields, which not only lays the foundation for the subsequent calculation of the fluid temperature field, but also makes the simulation results more accurately reflect the actual working state of the fluids on both sides of the heat exchanger, greatly improving the accuracy and reliability of the dual-fluid temperature field calculation of the heat exchanger, and at the same time providing an efficient and reliable technical means for the performance evaluation and optimization of the dual-fluid heat exchanger, meeting the high-precision simulation requirements of the dual-fluid temperature of the heat exchanger.

[0081] In this embodiment, a heat exchanger dual-fluid temperature simulation calculation method is provided. Figure 2 FIG. 1 is a flow chart of another heat exchanger dual-fluid temperature simulation calculation method according to an embodiment of the present invention. Figure 2 As shown, the process includes the following steps:

[0082] Step S201 : simplifying the heat exchanger into a porous medium region, where the porous medium region has a geometric structure that matches the physical size of the heat exchanger.

[0083] It should be noted that due to the dense presence of fins, pipes, and other structures within a real heat exchanger, the fluid will encounter two types of resistance when flowing through it: viscous resistance (dominant at low flow rates, caused by friction between the fluid and the solid wall) and inertial resistance (dominant at high flow rates, caused by kinetic energy loss resulting from changes in fluid flow direction, contraction, or expansion of the flow channel). Therefore, it is necessary to add the inertial resistance coefficient and the viscous resistance coefficient to the fluid simulation calculation to quantify the impact of these two resistances. This ensures that the resistance effect of the porous medium region on the fluid is consistent with that of a real heat exchanger (e.g., viscous resistance dominates at low flow rates, and inertial resistance dominates at high flow rates). This further ensures that the velocity field and pressure field distribution (e.g., pressure drop and flow velocity distribution) in subsequent flow field simulations are highly consistent with the flow characteristics of the actual heat exchanger, providing reliable basic flow data for temperature field calculations. Therefore, after simplifying the heat exchanger into a porous medium region, the heat exchanger dual-fluid temperature simulation calculation method of this embodiment further includes: adding the inertial resistance coefficient and the viscous resistance coefficient to the porous medium region to simulate the fluid resistance flowing through the porous medium region.

[0084] It should be noted that the inertial drag coefficient and viscous drag coefficient in this embodiment can be obtained through experimental measurement. Specifically, by adding inertial drag coefficients and viscous drag coefficients to the porous medium region to simulate fluid resistance, the actual flow resistance characteristics of the heat exchanger can be accurately reproduced, further improving the accuracy of the flow field simulation and laying a solid foundation for the subsequent temperature field coupling solution.

[0085] Step S202 : Meshing the area where the heat exchanger is located to obtain a first mesh area including a porous medium area and a second mesh area not including a porous medium area.

[0086] Specifically, the above step S202 includes:

[0087] Step S2021: Divide the area where the heat exchanger is located into a volume grid to obtain a volume grid area containing multiple grid units.

[0088] In this embodiment, this step aims to construct a volume mesh containing all regions, and then segment the first and second mesh regions from it through subsequent steps. The mesh generation logic of this embodiment, which first divides the entire mesh and then segments it, can ensure that the meshes of the two regions maintain continuity at the boundary (for example, the coordinates of the boundary nodes of the first mesh coincide with the coordinates of the adjacent nodes of the second mesh, and the mesh density transition is smooth).

[0089] Step S2022: based on the current spatial position of the heat exchanger, a first grid area corresponding to the porous medium area is divided from the volume grid area.

[0090] It should be noted that, since the spatial position of the heat exchanger in the vehicle is fixed (such as the specific coordinate range of the radiator at the front of the vehicle), its spatial position can be determined according to the actual vehicle conditions.

[0091] In this embodiment, this step aims to ensure that the porous medium region (i.e., the first grid region) strictly corresponds to the actual physical position of the heat exchanger (e.g., the coordinate ranges completely overlap), thus avoiding the "geometric misalignment" that may result from "directly drawing the first grid alone" (e.g., the porous medium region is offset from the actual heat exchanger position). This ensures that in subsequent flow field simulations, the path of the fluid flowing through the porous medium region is consistent with the path of the actual fluid flowing through the heat exchanger, laying a geometric foundation for the accurate calculation of the resistance coefficient and heat transfer coefficient, and reducing simulation distortion caused by position deviation.

[0092] Step S2023: Subtract the first grid area from the volume grid area to obtain a second grid area.

[0093] In this embodiment, this step can clearly define the boundary between the first grid area (ie, the porous medium area) and the second grid area, which helps to avoid overlapping or missing areas.

[0094] In the embodiment of the present invention, a volume grid containing all regions is first constructed, and then the logic of dividing the first and second grid regions therefrom is adopted to ensure that the grids of the two regions can maintain continuity at the boundary; and the first grid region is divided from the volume grid region based on the current spatial position of the heat exchanger, so that the porous medium region and the actual physical position of the heat exchanger are strictly corresponded, thereby ensuring that the path of the fluid flowing through the porous medium region in the subsequent flow field simulation is consistent with the path of the actual fluid flowing through the heat exchanger, providing a high-quality grid foundation for the flow field solution and temperature field coupling of the dual-fluid simulation of the heat exchanger, and helping to improve the stability of the flow field and temperature field solutions.

[0095] Step S203 , performing flow field simulation on the first grid area and the second grid area, and coupling solving the fluid temperature field of the first grid area to obtain the dual fluid temperatures of the heat exchanger.

[0096] Specifically, the above step S203 includes:

[0097] Step S2031 : merging the first grid area into the second grid area to obtain a grid area to be simulated, and establishing a data exchange channel for data exchange between the cold-side grid area and the second grid area.

[0098] In this embodiment, the process of merging the first grid area into the second grid area not only retains the depiction of the details of the two fluids by the cold-side and hot-side grids, but also forms a unified calculation domain by merging the grids, avoiding the boundary processing redundancy caused by independent calculations of multiple regions; at the same time, the independence of the cold-side and hot-side grids allows local grid encryption of key areas (such as the high flow velocity area on the hot side) rather than overall encryption. While ensuring the accuracy of key details, the amount of unnecessary grids is reduced, thereby achieving efficient simulation with limited computing resources.

[0099] In this embodiment, the data exchange channel can clearly define the correspondence between inlet and outlet boundaries, facilitating data exchange between these boundaries. Because the fluid type in the cold-side grid area and the second grid area is the same (e.g., both are air), data exchange ensures a smooth transition between parameters such as velocity and pressure for the same fluid in different areas (e.g., matching the cold-side outlet velocity with the second grid inlet velocity), avoiding numerical discontinuities (e.g., sudden changes in flow rate or pressure) caused by grid separation.

[0100] It should be noted that the grid area merging operation in this embodiment can be implemented by referring to conventional methods in the art and will not be described in detail here.

[0101] Step S2032: Simulate the grid area to be simulated based on preset simulation parameters, and solve the fluid momentum equation to obtain the velocity field and pressure field. The preset simulation parameters at least include fluid physical property parameters such as fluid density, viscosity and specific heat capacity, as well as initial boundary conditions of velocity and pressure.

[0102] In the embodiment of the present invention, a design in which the cold-side grid area and the hot-side grid area are "spatially overlapped and independent of each other" is adopted, which not only ensures that the flow and heat transfer processes of the two different fluids can be accurately simulated separately, but also, due to the "spatial overlap" feature, truly restores the heat exchange scene of the fluids on both sides of the heat exchanger at the same physical position, thereby making the heat transfer process of the two fluids closer to the actual physical laws, and significantly improving the accuracy of the coupled simulation; at the same time, a data exchange channel is established between the cold-side grid area and the second grid area, which solves the problem of "discontinuous flow parameters between independent grids" and reduces the risk of calculation divergence caused by parameter discontinuity; finally, the simulation design is performed based on the real flow parameters, so that the flow field results are closer to the actual test data, further enhancing the reliability of the flow field results, and laying a high-quality flow data foundation for the subsequent temperature field coupling solution.

[0103] Step S2033 : determining the cold fluid velocity distribution in the cold-side grid area based on the velocity field and the pressure field, where the cold fluid velocity distribution includes the cold fluid velocity of each grid unit.

[0104] Step S2034, calculating the target heat transfer coefficient based on a preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution. The preset heat transfer performance table is a mapping relationship table obtained through experimental measurement that contains different cold-side fluid mass flow rates and corresponding heat transfer powers.

[0105] In this embodiment, since the heat transfer performance of the heat exchanger is significantly affected by structural details (such as fin roughness and flow channel corners), it is difficult for the theoretical formula to fully cover these complex factors; while the experimental data directly reflects the actual heat transfer law, the target heat transfer coefficient calculated based on this is more in line with the actual working conditions.

[0106] Specifically, the target heat transfer coefficient is calculated in step S2034 according to the preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution, including:

[0107] Step A1: determining the cold side fluid inlet temperature and the hot side fluid inlet temperature respectively, and calculating the inlet temperature difference between the cold side fluid inlet temperature and the hot side fluid inlet temperature.

[0108] Step A2: determining the global heat transfer coefficient according to the ratio of the heat transfer power to the inlet temperature difference in the preset heat transfer performance table.

[0109] Step A3: determining the unit heat transfer coefficient according to the ratio of the global heat transfer coefficient to the total number of grid cells in the first grid area.

[0110] Step A4: Solve each temperature control equation based on the unit heat transfer coefficient to obtain the cold-side fluid temperature and the hot-side fluid temperature of the grid unit.

[0111] It should be noted that the temperature control equation in this embodiment is the energy equation in fluid mechanics, which is used to describe the energy conversion and transfer laws of the fluid. It is based on the principle of conservation of energy, that is, the net inflow / outflow rate of energy at any point in the fluid is equal to the rate of decrease of energy in the area at that point. For the specific content of the equation, please refer to the relevant content below and will not be elaborated here.

[0112] Step A5: Calculate the current average temperature difference based on the cold-side fluid temperature and the hot-side fluid temperature of all grid cells, and calculate the current heat exchange power based on the current average temperature difference.

[0113] Step A6: Calculate the heat exchange error based on the current heat exchange power and the heat exchange power in the preset heat exchange performance table, and determine the target heat exchange coefficient based on the magnitude relationship between the heat exchange error and the first preset power threshold.

[0114] In the embodiment of the present invention, by splitting the global coefficient into each grid unit, the heat transfer coefficient of each unit is associated with the flow characteristics of its own position, providing a "grid-level adjustment carrier" for subsequent iterative optimization combined with local flow velocity, and ultimately achieving a better match between the heat transfer coefficient of each grid unit and the actual flow state, which helps to improve the calculation accuracy of the subsequent temperature field; and the dynamic adjustment of the heat transfer coefficient is inferred from the real-time state of the temperature field, that is, a process of "solving the current average temperature difference based on the temperature of all grid units, calculating the current heat transfer power, comparing the test power to obtain the error and correct the target heat transfer coefficient" is designed. Through dynamic feedback correction of the temperature difference, it not only adapts to the changes in heat transfer characteristics under complex flow, but also further makes the heat transfer coefficient of each unit more matched with the actual flow, while also enhancing the adaptability of the changes in heat transfer characteristics under different working conditions; the above scheme ensures the physical authenticity of the target heat transfer coefficient and improves its adaptability to complex working conditions, providing core support for the accurate solution of the dual-fluid temperature field, and ultimately making the heat exchanger temperature simulation results more reliable and closer to engineering practice.

[0115] In this embodiment, determining the target heat transfer coefficient based on the relationship between the heat transfer error and the first preset power threshold in step A6 includes:

[0116] Step A61: If the heat exchange error is less than the first preset power threshold, the unit heat exchange coefficient is determined as the target heat exchange coefficient.

[0117] In this embodiment, the specific value of the first preset power threshold is adaptively determined according to actual needs.

[0118] In step A62, if the heat exchange error is not less than the first preset power threshold, the process returns to the step of solving each temperature control equation based on the unit heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the heat exchange error is less than the first preset power threshold.

[0119] In the embodiment of the present invention, an iterative feedback mechanism is designed to achieve precise calibration of the heat transfer coefficient. Specifically, the heat transfer error is compared with the first preset power threshold to dynamically iteratively determine the target heat transfer coefficient, so that the unit heat transfer coefficient automatically approaches the true value in each cycle, making the target heat transfer coefficient more closely matched with the actual heat transfer capacity of each grid, greatly reducing the calculation error of the local heat transfer coefficient, and further ensuring the credibility of the simulation results.

[0120] In step S2035, the temperature control equations for each grid unit are constructed respectively, with the cold side fluid temperature in the cold side grid area and the hot side fluid temperature in the hot side grid area as unknown quantities. Each temperature control equation is solved based on the target heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the corresponding grid unit.

[0121] In this embodiment, the temperature control equation includes a first fluid energy equation for each grid cell in the cold-side grid region and a second fluid energy equation for each grid cell in the hot-side grid region.

[0122] It should be noted that the flow of fluid in the heat exchanger is continuous along the process (for example, the cold side fluid flows through each grid unit from the inlet to the outlet in sequence, and the temperature of the upstream grid will directly affect the downstream grid). In this embodiment, taking the above characteristics into consideration, the equation is constructed with the temperature of the upstream grid of the cold flow or hot flow as a known quantity, accurately capturing this continuity along the process. For example, when the cold side fluid flows through the current grid, its initial temperature is the outlet temperature of the upstream grid, and the temperature change of the current grid (due to heat absorption and temperature rise) will become a known condition for the downstream grid. This chain association of "upstream → current → downstream" makes the distribution of the temperature field strictly follow the energy transfer logic in the direction of fluid flow, avoiding the physical distortion caused by "isolated grid temperature calculation", and making the simulation results closer to the actual temperature evolution process in the heat exchanger (for example, the error of the temperature gradient along the process can be reduced). Specifically, in the above step S2035, the temperature control equations for each grid unit are constructed respectively with the temperature of the cold side fluid in the cold side grid area and the temperature of the hot side fluid in the hot side grid area as unknown quantities, including:

[0123] Step B1, taking the cold side fluid temperature of the current grid unit in the cold side grid area as an unknown quantity and the cold flow upstream grid temperature as a known quantity, and combining the obtained cold side fluid mass flow rate, cold side fluid specific heat capacity and unit heat transfer coefficient to construct the first fluid energy equation of the current grid unit; wherein, the cold flow upstream grid temperature is the fluid temperature of the upstream grid unit in the cold flow direction of the current grid unit.

[0124] Step B2, taking the hot side fluid temperature of the current grid unit in the hot side grid area as an unknown quantity and the heat flow upstream grid temperature as a known quantity, and combining the hot side fluid mass flow rate, the hot side fluid specific heat capacity and the unit heat transfer coefficient to construct the second fluid energy equation of the current grid unit; wherein, the heat flow upstream grid temperature is the fluid temperature of the upstream grid unit in the heat flow direction of the current grid unit.

[0125] In the embodiment of the present invention, an equation is constructed with the grid temperature upstream of the cold flow or hot flow as a known quantity to accurately capture the continuous flow of the fluid, so that the distribution of the temperature field strictly follows the energy transfer logic of the fluid flow direction, making the simulation results closer to the temperature evolution process in the actual heat exchanger; and each grid unit is designed to construct an energy equation separately, further decomposing the heat transfer process to the micro grid scale, which can independently reflect the local heat transfer intensity of the grid, and realize fine modeling at the grid level; at the same time, taking into account the differences in the characteristics of the two fluids, the energy equations of the first and second fluids are constructed separately, further ensuring the physical adaptability of the energy equations; in addition, strong coupling of the two fluids is achieved through the unit heat transfer coefficient, which truly restores the microscopic mechanism of "heat transfer from the hot side to the cold side through the solid wall surface", avoids the temperature field drift caused by energy imbalance, and further improves the reliability of the simulation results.

[0126] Step S2036: Obtain dual fluid temperatures of the heat exchanger based on the cold-side fluid temperature and the hot-side fluid temperature of all grid cells in the first grid area.

[0127] In the embodiment of the present invention, the differences in cold fluid velocities between different grid cells are taken into account. The local heat transfer coefficient is calculated through the grid-level velocity distribution, so that the heat transfer power of each grid matches the actual flow rate, and the temperature control equation is constructed separately for each grid cell. The temperature gradient of the cold-side and hot-side fluids at the microscale can be accurately captured, thereby making the dual-fluid temperature distribution closer to the actual heat transfer details inside the heat exchanger; and a preset heat transfer performance table is obtained through experimental measurement to directly reflect the actual heat transfer law, so that the target heat transfer coefficient subsequently calculated based on this is more in line with the actual working conditions, further enhancing the reliability of the dual-fluid temperature simulation calculation results; at the same time, the "cold-side fluid temperature and hot-side fluid temperature are unknown quantities" are solved separately, and the coupling relationship between the two is established through the target heat transfer coefficient, which can avoid the simplification and distortion of the fluid characteristics on the other side of the traditional "single fluid model", so that the temporal or spatial changes of the temperature field are more in line with the actual heat transfer logic. While ensuring the accuracy and reliability of the temperature field calculation, it can provide a high-precision and high-reliability solution for the dual-fluid temperature simulation of the heat exchanger.

[0128] In practical applications, because the accuracy of the local grid temperature field is not directly equivalent to meeting the overall performance standard (i.e., the core design goal of the heat exchanger to meet the overall heat transfer power requirement), local errors may offset each other, but the overall error may exceed the standard. For example, the heat transfer power of some grids is too high, while that of others is too low, and the total deviation from the target is large. To further improve simulation accuracy, after coupling the fluid temperature field of the first grid area to obtain the dual-fluid temperature of the heat exchanger, the heat exchanger dual-fluid temperature simulation calculation method of this embodiment also includes:

[0129] Step C1: multiply the difference between the hot-side fluid temperature and the cold-side fluid temperature of each grid unit in the first grid area by the target heat transfer coefficient to obtain the corresponding single-grid heat transfer power.

[0130] Step C2: summing the heat exchange powers of all single grids to obtain the actual heat exchange power of the heat exchanger.

[0131] Step C3, calculating the actual heat exchange error between the actual heat exchange power and the corresponding heat exchange power in the preset heat exchange performance table.

[0132] In step C4, when the actual heat exchange error is not less than the second preset power threshold, the process returns to the step of solving each temperature control equation based on the target heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the actual heat exchange error is less than the second preset power threshold.

[0133] In this embodiment, the specific value of the second preset power threshold is adaptively adjusted according to actual needs.

[0134] In the embodiment of the present invention, the core design goal of the heat exchanger in actual applications is to meet the overall heat exchange power requirements. The actual heat exchange power is designed by summing the heat exchange powers of all single grids, shifting the focus from local temperature to overall performance. The actual heat exchange error is then compared with the second preset power threshold for iterative correction to ensure that the overall heat exchange capacity of the heat exchanger strictly meets the engineering requirements, further improving the calculation accuracy of the dual-fluid temperature simulation.

[0135] It should be noted that because traditional single-fluid models can only solve the temperature distribution of the fluid on one side (such as the air side), the temperature of the fluid on the other side (such as the coolant side) is simplified through preset boundary conditions and cannot reflect the actual thermal interaction between the two fluids (such as the dynamic coupling of the hot-side fluid cooling due to heat release and the cold-side fluid heating due to heat absorption). Therefore, given the importance of heat exchanger simulation in automotive thermal management simulation and the difficulty of current single-fluid models in simultaneously calculating the liquid-side fluid temperature, a dual-fluid three-dimensional simulation solution is proposed that can simultaneously calculate the fluid temperature on both sides of the automotive heat exchanger. This can accurately calculate the temperature distribution of the fluids on both sides of the heat exchanger after heat exchange, which is beneficial to improving the calculation accuracy of automotive thermal management simulation.

[0136] In a specific embodiment, in order to address the current difficulties in directly modeling and simulating the heat exchanger to calculate the temperature of the fluid passing through the heat exchanger, this embodiment achieves the calculation of the temperature distribution of the fluid on both sides of the radiator by simplifying and abstracting the heat exchanger region into a porous medium region without directly modeling the heat exchanger. Figure 3 This is a flow chart of the two-fluid temperature field calculation process, which includes the following steps:

[0137] The first step is to simplify and abstract the heat exchanger.

[0138] In this embodiment, the heat exchanger is simplified and abstracted into a porous medium region, and the resistance effect of the heat exchanger on the fluid passing through the heat exchanger is described by adding an inertial resistance coefficient and a viscous resistance coefficient.

[0139] Specifically, the heat exchanger is simplified and abstracted into a porous medium area, and simplified into a rectangular parallelepiped structure according to the physical size of the heat exchanger. When calculating the flow, the inertial resistance coefficient is added. and the viscous drag coefficient To describe the resistance effect of the heat exchanger on the fluid passing through it, the two coefficients are generally obtained through experimental measurements. The inertial resistance coefficient and the viscous resistance coefficient are used to calculate the inertial resistance F and viscous drag D , the formulas are: ,in represents the fluid density, Represents fluid viscosity. Note that fluid density and viscosity are inherent properties of the fluid. Different types of fluids have different densities and viscosities, which can be found in public fluid property tables.

[0140] The second step is to divide the computational grid.

[0141] In this embodiment, the volume meshing module (i.e., the snappyHexMesh module in OpenFOAM) is used to draw the volume meshes of the porous medium area of ​​the heat exchanger (i.e., the first mesh area) and the main calculation area (i.e., the second mesh area).

[0142] Specifically, the snappyHexMesh module is used to draw the body mesh of the porous medium area of ​​the heat exchanger and the main calculation area excluding the heat exchanger area according to the spatial position coordinates of the heat exchanger in the vehicle. The porous medium area mesh of the heat exchanger includes two sets of meshes, which are used to calculate the temperature of the cold side fluid and the hot side fluid respectively. The cross-sectional diagram after the mesh division is completed is shown as follows: Figure 4 shown.

[0143] It should be noted that in this embodiment, the porous medium area is set as the heat exchange area of ​​the heat exchanger. Figure 4Region ① is marked as the cold-side mesh of the heat exchanger's porous media region, region ② is marked as the main computational region mesh, and region ③ is marked as the hot-side mesh of the heat exchanger's porous media region. Heat in the heat exchanger is transferred from the high-temperature fluid to the low-temperature fluid through regions ① and ③. Note that ① and ③ are two identical sets of meshes—that is, ③ is copied from ① and is spatially identical, overlapping in space but independent of each other. Both ① and ③ are surrounded by ②. Region ③ contains a high-temperature fluid, while region ① contains a low-temperature fluid, but the fluid types in the two regions are different. Regions ① and ② contain the same fluid, typically air, and heat is transferred from region ① to region ②.

[0144] Furthermore, since the grids of area ① and area ② are independent of each other, but data exchange is required between the two when calculating and solving the flow field, a data exchange channel needs to be established between the two. That is, in this embodiment, the mergeMesh method is used to merge the porous medium grid of the heat exchanger into the grid of the main calculation area, and then the topoSet and createPatch instructions are used to establish a data exchange channel between the cold side grid of the porous medium of the heat exchanger and the grid of the main calculation area, that is, Figure 4 In the example, inlet1 and inlet2, outlet1 and outlet2 are each a set of data exchange boundaries.

[0145] It should be explained that the mergeMesh method is a command in OpenFOAM for merging multiple meshes, and is mainly used to merge meshes in different areas into an overall computational domain. The topoSet command is used to create a point set, face set, or volume set for a specified area, and to generate a topological set by selecting specific mesh elements. For example, when you need to set an inlet and outlet in a simulation, you can select the corresponding mesh faces through topoSet and generate the corresponding set, and then use the createPatch tool to generate the physical boundary. The createPatch command is used to create a physical boundary based on a topological set, and it must be used in conjunction with the set generated by topoSet. For example, after selecting the inlet area through topoSet, createPatch is used to specify the physical properties of the area (such as flow velocity and flow) to generate boundary conditions with specific physical meanings. When the two are used in combination, the geometric area is usually defined first through topoSet, and then the physical parameters are assigned using createPatch to achieve the setting of custom boundary conditions.

[0146] The third step is to simulate and calculate the flow field.

[0147] In this embodiment, the flow field is simulated and calculated until convergence, and a stable distribution of the velocity field and the pressure field is obtained.

[0148] Specifically, the control file is used to set the physical properties of the fluid, physical parameters such as the turbulence model, and initial boundary conditions such as velocity and pressure to perform flow field calculations and obtain stable velocity and pressure fields.

[0149] It should be noted that the velocity field and pressure field in this embodiment are obtained by solving the continuity equation and momentum conservation equation in fluid mechanics. The specific solution method can be found in conventional methods in the art and is not limited in detail here.

[0150] The fourth step is to couple and solve the temperature fields on both sides of the heat exchanger.

[0151] In this embodiment, the temperature fields of the hot fluid and the cold fluid in the dual-fluid grid area are solved, and the heat flow inlet temperature cycle coupling calculation is corrected according to the actual heat exchange power.

[0152] Specifically, the temperature fields on both sides of the heat exchanger are solved in a coupled manner. The specific temperature solution algorithm flow chart is as follows: Figure 5 As shown. Figure 5 It can be seen that the specific solution steps include:

[0153] Step 1: Set the target heat exchange power of the heat exchanger, the initial value of the hot side fluid inlet temperature, the mass flow rate, and the thermal measurement fluid physical properties.

[0154] In this embodiment, the target heat exchange power of the heat exchanger is set , initial value of hot side fluid inlet temperature , hot side fluid mass flow rate , thermal physical parameters of the hot side fluid, i.e. the specific heat capacity of the hot fluid, etc.

[0155] Step 2: Set the heat exchanger heat transfer performance interpolation table.

[0156] In this embodiment, a heat exchange performance interpolation table of the heat exchanger is set based on experimental test data (i.e., obtained through experimental measurement), which describes the relationship between different air volumes flowing through the radiator and the heat exchange power. The heat exchange performance interpolation table is specifically referred to the following table.

[0157] Table 1

[0158]

[0159] Step 3: Extract the fluid velocity field on the cold side of the heat exchanger area.

[0160] In this example, the calculated steady-state flow field data is extracted to obtain the velocity distribution of the cold fluid in the heat exchanger region. It should be noted that after the flow field calculation is completed, the fluid velocity within each volume grid is saved as a file, and the velocity distribution value is obtained by reading the calculation result file.

[0161] Step 4: Calculate the local heat transfer coefficient of the heat exchanger.

[0162] In this embodiment, the local heat transfer coefficient of the heat exchanger is calculated based on a heat exchanger heat transfer performance interpolation table. The local heat transfer coefficient table (containing multiple local heat transfer coefficients, i.e., local heat transfer coefficients) for the heat exchanger region is then interpolated based on the actual velocity distribution of the extracted cold fluid in the heat exchanger and the calculated local heat transfer coefficient table. This local heat transfer coefficient is then used to solve the subsequent heat transfer process for the fluids on both sides of the heat exchanger. Specifically, the calculation method for the local heat transfer coefficient table includes:

[0163] Step 4.1: Select the cold side fluid mass flow rate from Table 1 and heat transfer power The global heat transfer coefficient is calculated based on the data of The calculation formula is:

[0164]

[0165] in, is the hot side fluid inlet temperature, is the cold side fluid inlet temperature (all of which are known values ​​determined during the test process). It should be noted that other known values ​​determined during the test process in this embodiment also include: the hot fluid mass flow rate is also called the hot side fluid mass flow rate , specific heat of cold fluid , specific heat of thermal fluid , cold fluid density Calculate the local heat transfer coefficient using the above known values .

[0166] Step 4.2: Assumptions ,in is the total number of grid cells in the heat exchanger.

[0167] Step 4.3: Form a linear system of equations by constructing the following system of equations in each grid cell, as shown below:

[0168]

[0169] in, 、 、 、 is the unknown temperature in the local grid cell, Figure 6 It is a schematic diagram of the local grid unit temperature. Specifically, the equations of all grid units of the heat exchanger are combined together to calculate the unknown grid unit temperature. and To solve, the boundary condition equations need to be specified only at the inlet boundary of the heat exchanger, that is, and . Please note that the cold fluid temperature of the current grid cell and thermal fluid temperature In the process of solving and is a known quantity, namely the temperature of the two fluids in the upstream grid cell, where represents the cold fluid temperature of the upstream grid cell, represents the temperature of the thermal fluid in the upstream grid cell. Note that the meanings of the remaining parameters in the formula are as mentioned above and are not repeated here.

[0170] Step 4.4: After all grid cell temperatures are solved, calculate the average temperature difference between the hot and cold fluids. The calculation formula is:

[0171]

[0172] in, Indicates the grid cell number, Indicates the The thermal fluid temperature of each grid cell, Indicates the The cold fluid temperature of each grid cell.

[0173] Step 4.5, then according to the calculation formula Calculate the estimated total heat transfer (i.e. the actual heat transfer power calculated in the current iteration process), and then use the formula Update the value of the local heat transfer coefficient.

[0174] It should be noted that the above steps 4.3 to 4.5 are repeated until the maximum number of iterations set by the user is met or the convergence condition is met, that is, So far, among them The convergence tolerance set by the user.

[0175] Finally, the formula , and combined with the formula in step 4.5 above , and the cold side fluid mass flow rate in Table 1 and heat transfer power , the cold side fluid velocity can be calculated and local heat transfer coefficient The relationship table between them. Please note that is the inlet boundary area of ​​the cold fluid of the heat exchanger. Its specific value can be solved in advance. The solution method refers to conventional means in the field.

[0176] Step 5: Couple and solve the fluid temperature field on both sides of the heat exchanger.

[0177] In this embodiment, the fluid temperature field in region ① and region ③ is solved in a coupled manner according to the temperature control equation. The control equation is as follows:

[0178]

[0179] in, is the cold fluid temperature of the current grid cell, is the temperature of the thermal fluid in the current grid cell, which are all quantities to be solved; is the cold flow upstream grid temperature, is the temperature of the grid upstream of the heat flow, which is a known quantity read in real time during the calculation process. is the local heat transfer coefficient. Note that the meanings of the remaining parameters in the formula are as mentioned above and will not be repeated here.

[0180] Step 6: Determine whether the actual heat exchange power is equal to the target heat exchange power.

[0181] In this embodiment, the actual heat transfer power of the heat exchanger is calculated based on the temperature distribution of the fluids on both sides. The actual heat transfer power is obtained by first calculating the heat transfer power between a single grid unit and then summing the heat transfer power of all grid units in the heat exchanger. The specific calculation method is as follows:

[0182]

[0183] in, Indicates the The heat transfer power of each grid unit. Please note that the meanings of the other parameters in the formula can be found in the previous text and will not be repeated here.

[0184] In this embodiment, it is determined whether the set target heat exchange power has been reached based on the calculated actual heat exchange power. The determination method is as follows: To determine, The threshold value for determining whether the two are equal can be specified by the user. Convergence tolerance set by the user in the previous text Both represent the user's set threshold value for heat exchange power error. The specific values ​​can be determined according to actual needs. For example, the two can be set to the same value or different values.

[0185] In this embodiment, if the target heat exchange power is not reached (i.e., the actual heat exchange power is not equal to the target heat exchange power), the inlet temperature of the fluid on the hot side of the heat exchanger is corrected, and the process from step 5 to step 6 is repeated until the set target heat exchange power is reached, and then the calculation process of the coupled solution of the temperature field on both sides of the heat exchanger is terminated.

[0186] In summary, in the embodiment of the present invention, by simplifying the heat exchanger into a porous medium area adapted to its physical size, dividing each grid area and performing flow field simulation and coupled solution, it is possible to simulate the fluid temperature on both sides of the heat exchanger. This not only shortens the calculation cycle, but also makes the simulation results more accurately reflect the actual working state of the heat exchanger, greatly improving the simulation calculation accuracy and meeting the high-precision simulation requirements.

[0187] This embodiment also provides a heat exchanger dual-fluid temperature simulation and calculation device, which is used to implement the above-mentioned embodiments and preferred embodiments. Details already described will not be repeated here. As used below, the term "module" refers to a combination of software and / or hardware that implements a predetermined function. Although the devices described in the following embodiments are preferably implemented in software, implementation using hardware, or a combination of software and hardware, is also possible and contemplated.

[0188] This embodiment provides a heat exchanger dual-fluid temperature simulation calculation device, such as Figure 7 As shown, the device includes:

[0189] The simplification module 701 is used to simplify the heat exchanger into a porous medium region, where the porous medium region is a geometric structure that is adapted to the physical size of the heat exchanger.

[0190] The division module 702 is used to divide the area where the heat exchanger is located into grids to obtain a first grid area including a porous medium area and a second grid area not including a porous medium area. The first grid area includes a cold side grid area and a hot side grid area. The cold side grid area and the hot side grid area are two sets of grid areas that overlap in spatial position and are independent of each other. The types of fluids in the cold side grid area and the hot side grid area are different.

[0191] The calculation module 703 is used to simulate the flow field of the first grid area and the second grid area, and couple the fluid temperature field of the first grid area to obtain the dual fluid temperatures of the heat exchanger, which include the cold side fluid temperature and the hot side fluid temperature.

[0192] In some optional embodiments, the simplification module 701 includes: a simplification submodule, configured to add an inertial resistance coefficient and a viscous resistance coefficient to the porous medium region to simulate the resistance of the fluid flowing through the porous medium region.

[0193] In some optional embodiments, the division module 702 includes: a first division submodule, a second division submodule and a third division submodule; wherein the first division submodule is used to divide the body grid of the area where the heat exchanger is located to obtain a body grid area containing multiple grid units; the second division submodule is used to divide the first grid area corresponding to the porous medium area from the body grid area based on the current spatial position of the heat exchanger; the third division submodule is used to subtract the first grid area from the body grid area to obtain the second grid area.

[0194] In some optional embodiments, the calculation module 703 includes: a first calculation submodule, a second calculation submodule, a third calculation submodule, a fourth calculation submodule, a fifth calculation submodule and a sixth calculation submodule; wherein the first calculation submodule is used to merge the first grid area into the second grid area to obtain a grid area to be simulated, and establish a data exchange channel for data exchange between the cold side grid area and the second grid area; the second calculation submodule is used to simulate the grid area to be simulated based on preset simulation parameters, and solve the fluid momentum equation to obtain a velocity field and a pressure field, wherein the preset simulation parameters at least include fluid physical property parameters such as fluid density, viscosity and specific heat capacity, and initial boundary conditions of velocity and pressure; the third calculation submodule is used to determine the cold fluid velocity distribution in the cold side grid area based on the velocity field and the pressure field, The cold fluid velocity distribution includes the cold fluid velocity of each grid unit; the fourth calculation submodule is used to calculate the target heat transfer coefficient based on the preset heat transfer performance table, the total number of grid units in the first grid area and the cold fluid velocity distribution. The preset heat transfer performance table is a mapping relationship table containing different cold side fluid mass flow rates and corresponding heat transfer powers obtained through experimental measurements; the fifth calculation submodule is used to construct the temperature control equation for each grid unit respectively with the cold side fluid temperature in the cold side grid area and the hot side fluid temperature in the hot side grid area as unknown quantities, and solve each temperature control equation based on the target heat transfer coefficient to obtain the cold side fluid temperature and hot side fluid temperature of the grid unit; the sixth calculation submodule is used to obtain the dual fluid temperature of the heat exchanger based on the cold side fluid temperature and the hot side fluid temperature of all grid units in the first grid area.

[0195] In some optional embodiments, the fourth calculation submodule includes: a first calculation unit, a second calculation unit, a third calculation unit, a fourth calculation unit, a fifth calculation unit and a sixth calculation unit; wherein the first calculation unit is used to determine the cold side fluid inlet temperature and the hot side fluid inlet temperature respectively, and calculate the inlet temperature difference between the cold side fluid inlet temperature and the hot side fluid inlet temperature; the second calculation unit is used to determine the global heat transfer coefficient based on the ratio of the heat transfer power to the inlet temperature difference in the preset heat transfer performance table; the third calculation unit is used to determine the unit heat transfer coefficient based on the ratio of the global heat transfer coefficient to the total number of grid units in the first grid area; the fourth calculation unit is used to solve each temperature control equation based on the unit heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit; the fifth calculation unit is used to solve the current average temperature difference based on the cold side fluid temperature and the hot side fluid temperature of all grid cells, and calculate the current heat transfer power based on the current average temperature difference; the sixth calculation unit is used to calculate the heat transfer error based on the current heat transfer power and the heat transfer power in the preset heat transfer performance table, and determine the target heat transfer coefficient based on the relationship between the heat transfer error and the first preset power threshold.

[0196] In some optional embodiments, the sixth calculation unit includes: a first judgment subunit and a second judgment subunit; wherein, the first judgment subunit is used to determine the unit heat transfer coefficient as the target heat transfer coefficient if the heat transfer error is less than the first preset power threshold; the second judgment subunit is used to return to the step of solving each temperature control equation based on the unit heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit if the heat transfer error is not less than the first preset power threshold, until the heat transfer error is less than the first preset power threshold.

[0197] In some optional embodiments, the fifth calculation submodule includes: a first construction unit and a second construction unit; wherein, the first construction unit is used to construct the first fluid energy equation of the current grid unit with the cold side fluid temperature of the current grid unit in the cold side grid area as an unknown quantity, the cold flow upstream grid temperature as a known quantity, and the obtained cold side fluid mass flow rate, cold side fluid specific heat capacity and unit heat transfer coefficient; wherein, the cold flow upstream grid temperature is the fluid temperature of the upstream grid unit in the cold flow direction of the current grid unit; the second construction unit is used to construct the second fluid energy equation of the current grid unit with the hot side fluid temperature of the current grid unit in the hot side grid area as an unknown quantity, the hot flow upstream grid temperature as a known quantity, and the hot side fluid mass flow rate, hot side fluid specific heat capacity and unit heat transfer coefficient; wherein, the hot flow upstream grid temperature is the fluid temperature of the upstream grid unit in the hot flow direction of the current grid unit.

[0198] In some optional embodiments, the device also includes: a correction module, which is used to multiply the difference between the hot side fluid temperature and the cold side fluid temperature of each grid unit in the first grid area by the target heat transfer coefficient to obtain the corresponding single grid heat transfer power; summing all single grid heat transfer powers to obtain the actual heat transfer power of the heat exchanger; calculating the actual heat transfer error between the actual heat transfer power and the corresponding heat transfer power in the preset heat transfer performance table; when the actual heat transfer error is not less than the second preset power threshold, returning to the execution of the steps of solving each temperature control equation based on the target heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the actual heat transfer error is less than the second preset power threshold.

[0199] The further functional description of each of the above modules is the same as that of the above corresponding embodiments and will not be repeated here.

[0200] The heat exchanger dual-fluid temperature simulation calculation device in this embodiment is presented in the form of a functional unit, where the unit refers to an ASIC (Application Specific Integrated Circuit) circuit, a processor and memory that executes one or more software or fixed programs, and / or other devices that can provide the above functions.

[0201] The heat exchanger dual-fluid temperature simulation and calculation device of the embodiment of the present invention replaces complex entities with geometric structures, which can effectively reduce the number of subsequent grids and greatly shorten the simulation cycle; and by gridding the area where the heat exchanger is located, and coupling the flow field simulation and temperature field of the grid area, a stable velocity field and pressure field can be obtained, which lays the foundation for the subsequent calculation of the fluid temperature field, and makes the simulation results more accurately reflect the actual working state of the fluids on both sides of the heat exchanger, which not only improves the accuracy and reliability of the heat exchanger dual-fluid temperature field calculation, but also provides an efficient and reliable technical means for the performance evaluation and optimization of the dual-fluid heat exchanger, and meets the high-precision simulation requirements of the heat exchanger dual-fluid temperature.

[0202] An embodiment of the present invention further provides a vehicle including a controller. The controller in this embodiment is a vehicle controller, configured to power on / off, and wake up its connected sub-controllers and network nodes, and to collect real-time output current from each power supply interface. Other controllers with the aforementioned functions are also applicable.

[0203] Figure 8 : is a schematic diagram of the structure of the controller provided in an optional embodiment of this embodiment, such as Figure 8As shown, the controller includes: one or more processors 10, a memory 20, and interfaces for connecting various components, including high-speed interfaces and low-speed interfaces. The various components utilize different buses to communicate with each other and can be installed on a common mainboard or installed in other ways as needed. The processor can process the instructions executed in the controller, including instructions stored in or on the memory to display graphical information of a GUI on an external input / output system (such as a display device coupled to the interface). In some optional embodiments, if necessary, multiple processors and / or multiple buses can be used together with multiple memories and multiple memories. Similarly, multiple controllers can be connected, and each controller provides some necessary operations (for example, as a server array, a group of blade servers, or a multi-processor system). Figure 8 A processor 10 is taken as an example.

[0204] The processor 10 may be a central processing unit, a network processor, or a combination thereof. The processor 10 may further include a hardware chip. The hardware chip may be an application-specific integrated circuit, a programmable logic device, or a combination thereof. The programmable logic device may be a complex programmable logic device, a field programmable gate array, a general purpose array logic, or any combination thereof.

[0205] The memory 20 stores instructions that can be executed by at least one processor 10, so as to enable at least one processor 10 to execute the method shown in the above embodiment.

[0206] The memory 20 may include a program storage area and a data storage area, wherein the program storage area may store an operating system and application programs required for at least one function; the data storage area may store data created according to the use of the controller, etc. In addition, the memory 20 may include a high-speed random access memory, and may also include a non-transient memory, such as at least one disk storage device, a flash memory device, or other non-transient solid-state storage device. In some optional embodiments, the memory 20 may optionally include a memory remotely located relative to the processor 10, and these remote memories may be connected to the controller via a network. Examples of the above-mentioned network include, but are not limited to, the Internet, an intranet, a local area network, a mobile communication network, and combinations thereof.

[0207] The memory 20 may include a volatile memory, such as a random access memory; the memory may also include a non-volatile memory, such as a flash memory, a hard disk or a solid-state drive; the memory 20 may also include a combination of the above types of memory.

[0208] The controller further includes a communication interface 30 for the main control chip to communicate with other devices or a communication network.

[0209] A computer-readable storage medium is also provided in an embodiment of the present invention. The above-mentioned method according to the embodiment of the present invention can be implemented in hardware, firmware, or implemented as a computer code that can be recorded in a storage medium, or implemented as a computer code that is originally stored in a remote storage medium or a non-temporary machine-readable storage medium and downloaded through a network and will be stored in a local storage medium, so that the method described herein can be stored in such software processing on a storage medium using a general-purpose computer, a dedicated processor, or programmable or dedicated hardware. Among them, the storage medium can be a magnetic disk, an optical disk, a read-only storage memory, a random access memory, a flash memory, a hard disk or a solid-state drive, etc.; further, the storage medium can also include a combination of the above-mentioned types of memory. It can be understood that a computer, a processor, a microprocessor main control chip or programmable hardware includes a storage component that can store or receive software or computer code. When the software or computer code is accessed and executed by a computer, a processor or hardware, the method shown in the above embodiment is implemented.

[0210] Although the embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art may make various modifications and variations without departing from the spirit and scope of the embodiments, and such modifications and variations are all within the scope defined by the appended claims.

Claims

1. A heat exchanger dual-fluid temperature simulation calculation method, characterized in that: The method comprises: Simplifying the heat exchanger into a porous medium region, wherein the porous medium region is a geometric structure adapted to the physical size of the heat exchanger; Meshing the area where the heat exchanger is located to obtain a first mesh area including the porous medium area and a second mesh area not including the porous medium area, wherein the first mesh area includes a cold-side mesh area and a hot-side mesh area, wherein the cold-side mesh area and the hot-side mesh area are two sets of mesh areas that overlap in spatial position and are independent of each other, and the fluid types in the cold-side mesh area and the hot-side mesh area are different; Performing flow field simulation on the first grid area and the second grid area, and coupling solving the fluid temperature field of the first grid area to obtain dual fluid temperatures of the heat exchanger, the dual fluid temperatures including a cold side fluid temperature and a hot side fluid temperature; The coupled solution of the fluid temperature field in the first grid area to obtain the dual-fluid temperatures of the heat exchanger includes: determining a cold fluid velocity distribution in a cold-side grid area based on the velocity field and the pressure field, wherein the cold fluid velocity distribution includes a cold fluid velocity in each grid cell; Calculating a target heat transfer coefficient based on a preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution, wherein the preset heat transfer performance table is a mapping relationship table containing different cold-side fluid mass flow rates and corresponding heat transfer powers obtained through experimental measurements; Taking the cold-side fluid temperature in the cold-side grid area and the hot-side fluid temperature in the hot-side grid area as unknown quantities, construct a temperature control equation for each grid unit respectively, and solve each temperature control equation based on the target heat transfer coefficient to obtain the cold-side fluid temperature and the hot-side fluid temperature of the grid unit accordingly; The dual fluid temperatures of the heat exchanger are obtained based on the cold-side fluid temperatures and the hot-side fluid temperatures of all grid cells in the first grid area.

2. The heat exchanger dual-fluid temperature simulation calculation method according to claim 1, characterized in that: The performing flow field simulation on the first grid area and the second grid area includes: Merging the first grid area into the second grid area to obtain a grid area to be simulated, and establishing a data exchange channel for data exchange between the cold-side grid area and the second grid area; The grid area to be simulated is simulated based on preset simulation parameters, and the fluid momentum equation is solved to obtain the velocity field and pressure field. The preset simulation parameters at least include fluid physical property parameters such as fluid density, viscosity and specific heat capacity, as well as initial boundary conditions of velocity and pressure.

3. The heat exchanger dual-fluid temperature simulation calculation method according to claim 1, characterized in that: The calculating the target heat transfer coefficient according to the preset heat transfer performance table, the total number of grid cells in the first grid area, and the cold fluid velocity distribution includes: Determining a cold side fluid inlet temperature and a hot side fluid inlet temperature respectively, and calculating an inlet temperature difference between the cold side fluid inlet temperature and the hot side fluid inlet temperature; Determining a global heat transfer coefficient based on the ratio of the heat transfer power in the preset heat transfer performance table to the inlet temperature difference; determining a unit heat transfer coefficient according to a ratio of the global heat transfer coefficient to the total number of grid cells in the first grid area; Solving each of the temperature control equations based on the unit heat transfer coefficient to obtain the cold-side fluid temperature and the hot-side fluid temperature of the grid unit; Calculating a current average temperature difference based on the cold-side fluid temperature and the hot-side fluid temperature of all grid cells, and calculating a current heat exchange power based on the current average temperature difference; A heat exchange error is calculated based on the current heat exchange power and the heat exchange power in the preset heat exchange performance table, and a target heat exchange coefficient is determined based on a magnitude relationship between the heat exchange error and a first preset power threshold.

4. The heat exchanger dual-fluid temperature simulation calculation method according to claim 3, characterized in that: The determining of the target heat transfer coefficient based on the magnitude relationship between the heat transfer error and the first preset power threshold includes: If the heat exchange error is less than the first preset power threshold, determining the unit heat exchange coefficient as the target heat exchange coefficient; If the heat exchange error is not less than the first preset power threshold, the process returns to the step of solving each of the temperature control equations based on the unit heat exchange coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit, until the heat exchange error is less than the first preset power threshold.

5. The heat exchanger dual-fluid temperature simulation calculation method according to claim 3, characterized in that: The temperature control equation includes a first fluid energy equation for each grid cell in the cold-side grid area and a second fluid energy equation for each grid cell in the hot-side grid area. The temperature control equation for each grid cell is constructed using the cold-side fluid temperature in the cold-side grid area and the hot-side fluid temperature in the hot-side grid area as unknown quantities, including: The cold side fluid temperature of the current grid cell in the cold side grid area is used as an unknown quantity, the cold flow upstream grid temperature is used as a known quantity, and the first fluid energy equation of the current grid cell is constructed by combining the obtained cold side fluid mass flow rate, cold side fluid specific heat capacity, and unit heat transfer coefficient; wherein the cold flow upstream grid temperature is the fluid temperature of the upstream grid cell in the cold flow direction of the current grid cell; The hot side fluid temperature of the current grid unit in the hot side grid area is taken as an unknown quantity, the heat flow upstream grid temperature is taken as a known quantity, and the hot side fluid mass flow rate, the hot side fluid specific heat capacity and the unit heat transfer coefficient are combined to construct the second fluid energy equation of the current grid unit; wherein, the heat flow upstream grid temperature is the fluid temperature of the upstream grid unit in the heat flow direction of the current grid unit.

6. The heat exchanger dual-fluid temperature simulation calculation method according to any one of claims 3 to 4, characterized in that: After the coupled solution of the fluid temperature field in the first grid area is performed to obtain the dual-fluid temperatures of the heat exchanger, the method further includes: Multiplying the difference between the hot-side fluid temperature and the cold-side fluid temperature of each grid cell in the first grid area by the target heat transfer coefficient to obtain the corresponding single-grid heat transfer power; Sum the heat transfer powers of all single grids to obtain the actual heat transfer power of the heat exchanger; Calculate the actual heat transfer error between the actual heat transfer power and the corresponding heat transfer power in the preset heat transfer performance table; When the actual heat exchange error is not less than the second preset power threshold, the step of solving each of the temperature control equations based on the target heat exchange coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit is returned to execution until the actual heat exchange error is less than the second preset power threshold.

7. The heat exchanger dual-fluid temperature simulation calculation method according to claim 1, characterized in that: The grid division of the area where the heat exchanger is located to obtain a first grid area including the porous medium area and a second grid area not including the porous medium area includes: Dividing the area where the heat exchanger is located into a volume grid to obtain a volume grid area containing multiple grid units; Dividing a first grid area corresponding to the porous medium area from the body grid area based on the current spatial position of the heat exchanger; The first mesh area is subtracted from the volume mesh area to obtain a second mesh area.

8. The heat exchanger dual-fluid temperature simulation calculation method according to claim 1, characterized in that: After simplifying the heat exchanger into porous media regions, the method further includes: An inertial resistance coefficient and a viscous resistance coefficient are added to the porous medium region to simulate the fluid resistance flowing through the porous medium region.

9. A heat exchanger dual-fluid temperature simulation calculation device, characterized in that: The device comprises: A simplification module, configured to simplify the heat exchanger into a porous medium region, wherein the porous medium region is a geometric structure adapted to the physical size of the heat exchanger; a partitioning module, configured to perform grid division on the area where the heat exchanger is located, to obtain a first grid area including the porous medium area, and a second grid area not including the porous medium area, wherein the first grid area includes a cold-side grid area and a hot-side grid area, wherein the cold-side grid area and the hot-side grid area are two sets of grid areas that overlap in spatial position and are independent of each other, and the fluid types in the cold-side grid area and the hot-side grid area are different; a calculation module, configured to perform flow field simulation on the first grid area and the second grid area, and to couple and solve the fluid temperature field of the first grid area to obtain dual fluid temperatures of the heat exchanger, wherein the dual fluid temperatures include a cold-side fluid temperature and a hot-side fluid temperature; Among them, the coupled solution of the fluid temperature field in the first grid area obtains the dual fluid temperature of the heat exchanger, including: determining the cold fluid velocity distribution in the cold side grid area based on the velocity field and the pressure field, and the cold fluid velocity distribution includes the cold fluid velocity of each grid unit; calculating the target heat transfer coefficient according to the preset heat transfer performance table, the total number of grid units in the first grid area and the cold fluid velocity distribution, and the preset heat transfer performance table is a mapping relationship table containing different cold side fluid mass flow rates and corresponding heat transfer powers obtained through experimental measurements; taking the cold side fluid temperature in the cold side grid area and the hot side fluid temperature in the hot side grid area as unknown quantities, constructing the temperature control equation for each grid unit respectively, and solving each of the temperature control equations based on the target heat transfer coefficient to obtain the cold side fluid temperature and the hot side fluid temperature of the grid unit; based on the cold side fluid temperature and the hot side fluid temperature of all grid units in the first grid area, the dual fluid temperature of the heat exchanger is obtained.

10. A vehicle, characterized in that: The vehicle includes a controller, which includes: a memory and a processor, the memory and the processor are communicatively connected to each other, the memory stores computer instructions, and the processor executes the heat exchanger dual-fluid temperature simulation calculation method according to any one of claims 1 to 8 by executing the computer instructions.

11. A computer-readable storage medium, characterized in that The computer-readable storage medium stores computer instructions, and the computer instructions are used to enable a computer to execute the heat exchanger dual-fluid temperature simulation calculation method according to any one of claims 1 to 8.

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