Simulation method for distributed cooling system

Abstract

The invention discloses a simulation method for a distributed cooling system, and the method comprises the following steps: building a topological relation graph and a three-dimensional digital-analog graph of the distributed cooling system, building a tail radiator module, an air inlet channel module and a motor power module according to the topological relation graph and the three-dimensional digital-analog graph, and obtaining the characteristic parameters of each assembly of the distributed cooling system; establishing a one-dimensional model of the internal liquid side of the distributed cooling system by utilizing the topological relation graph and the characteristic parameters; according to the spatial position relation and the size data of the radiator module and the air inlet channel module, a distributed cooling system air inlet side three-dimensional calculation model is established; and establishing a fluid-solid-thermal coupling calculation model of the distributed cooling system by combining the liquid side one-dimensional model and the air inlet side three-dimensional model, continuously iterating in the model solving process, and determining a performance result of the distributed cooling system in the quasi-steady-state process. According to the simulation method provided by the invention, a relatively accurate performance result of the quasi-steady-state cooling system is obtained, and the design efficiency of the cooling system is remarkably improved.

Description

Technical Field

[0001] This invention relates to the field of airborne equipment cooling technology, and more specifically to a simulation method for a distributed cooling system. Background Technology

[0002] During the test, the missile's front electronic equipment compartment generates a lot of heat when running at full power. However, due to the compact layout and limited space of the front compartment, it is impossible to install complex cooling devices. The air-cooling technology that generally uses impingement cooling has low heat dissipation efficiency and large size, which can no longer meet the heat dissipation requirements of electrical equipment with high heat flux density.

[0003] Therefore, a distributed liquid cooling technology is adopted, utilizing high-altitude, low-temperature ram air for forced convection heat transfer to transfer heat from the cold-plate electronic equipment compartment to the cooling medium circulation system. The coolant then exchanges heat with the ambient low-temperature air through the heat dissipation fins of the aft compartment. This composite forced convection-liquid cooling technology has extremely high heat dissipation efficiency, significantly improving the working environment of the electrical equipment compartment. Furthermore, the distributed design approach decouples the positional structure of the heat dissipation system and the electronic equipment compartment, allowing the liquid to transport heat from the front compartment to the rear heat dissipation system via external wall-mounted pipes. This maximizes the utilization of space in each compartment while further reducing the overall weight of the missile, thus improving the overall mechanical design redundancy.

[0004] However, the aerodynamic design of distributed cooling systems is complex, involving multiphysics coupling problems involving fluid, solid, and thermal fields. The development of dynamic simulation techniques for these systems faces significant challenges, particularly the accurate calculation of heat dissipation capacity under high-altitude, long-endurance conditions. Therefore, a method is needed to accurately calculate the performance of cooling systems, thereby improving the design efficiency of distributed cooling systems. Summary of the Invention

[0005] To address the aforementioned technical problems, the present invention aims to provide a simulation method for distributed cooling systems that can accurately calculate the performance results of the cooling system, thereby improving the design efficiency of distributed cooling systems.

[0006] The specific technical solution of the present invention is as follows:

[0007] A simulation method for a distributed cooling system includes the following steps:

[0008] S1. Establish the topology diagram and three-dimensional digital model of the distributed cooling system, and construct the tail radiator module, air intake channel module, and motor power module accordingly, and obtain the characteristic parameters of each component of the distributed cooling system.

[0009] S2. Using the aforementioned topology diagram and characteristic parameters, establish a one-dimensional model of the liquid side inside the distributed cooling system;

[0010] S3. Based on the spatial positional relationship and dimensional data of the radiator module and the air intake channel module, establish a three-dimensional calculation model of the air intake side of the distributed cooling system;

[0011] S4. Combining the one-dimensional model on the liquid side and the three-dimensional model on the air intake side, establish a fluid-solid-thermal coupling calculation model for the distributed cooling system. During the model solving process, continuously iterate to determine the performance results of the distributed cooling system in the quasi-steady-state process.

[0012] Furthermore, in step S1, the rear radiator is divided into grids using the three-dimensional digital model of the distributed cooling system to establish a rear radiator module.

[0013] Furthermore, in step S1, the intake channel is divided into grids using the three-dimensional digital model of the distributed cooling system to establish an intake channel module.

[0014] Furthermore, step S1 establishes a motor power module by acquiring the characteristic parameters of the power component.

[0015] Furthermore, the specific method for establishing the one-dimensional model of the liquid side inside the distributed cooling system in step S2 is as follows:

[0016] S21. Establish the pipe flow characteristics of the distributed cooling system using the topology diagram of the distributed cooling system, the hydraulic characteristic parameters of the flow channel, and the characteristic parameters of the cooling medium itself.

[0017] S22. Based on the motor power module established in step S1, and combined with the pipeline flow characteristics, establish a one-dimensional model of the liquid side inside the distributed cooling system.

[0018] Furthermore, the specific method for establishing the three-dimensional calculation model of the intake side of the distributed cooling system in step S3 is as follows:

[0019] S31. Based on the spatial positional relationship and dimensional data of the intake channel module established in step S1, establish a three-dimensional geometric model of the intake side of the distributed cooling system.

[0020] S32. Based on the physical properties of the air at the corresponding altitude, set the characteristic parameters of the incoming flow in the external flow field, and simplify the flow of the calculation model based on the radiator module established in step S1.

[0021] S33. The three-dimensional geometric model of the air intake side is divided into meshes;

[0022] S34. Set boundary conditions, where the inlet uses mass flow rate and the outlet uses pressure rate.

[0023] S35. Based on the boundary conditions and fluid control equations, calculate the flow field characteristics within the time step, solve for the velocity, pressure, and temperature aerodynamic characteristic parameters of the external flow field, and obtain the inlet side characteristic parameters.

[0024] S36. Based on the intake side characteristic parameters, use the post-processing program to select three sections in the external flow field, calculate the average velocity, average pressure, and average temperature of each section, and take the average value of the three sections to determine the transfer boundary conditions between the external flow field simulation and the single-tube heat transfer simulation, and finally establish the three-dimensional calculation model of the intake side.

[0025] Furthermore, due to the large number of equations to be solved in multiphysics coupling calculations, coupled with the extremely small geometric feature lengths, the number of meshes increases dramatically, greatly complicating the solution. In step S32, the flow conditions of the calculation model are simplified based on the heat sink module established in step S1 to ensure computational efficiency and avoid a sharp increase in solution time after meshing. The specific method is as follows:

[0026] Based on the three-dimensional digital model of the heat sink module, the following simplified assumptions are made regarding the flow:

[0027] Several radiators are divided into several equal parts according to their cross-sections, corresponding to a number of heat exchange copper tubes, and it is assumed that the flow in the several equal parts is uniform, thus obtaining a simplified model of a single heat exchange copper tube.

[0028] The average parameters of the intermediate flow channel are calculated using a simplified model of the single heat exchange copper tube to define the parametric boundary conditions for multi-field coupling.

[0029] If the heat exchange process of the radiator is considered as co-current heat exchange, the actual heat exchange capacity is greater than the calculated heat exchange capacity, which further saves computing resources and leaves design redundancy for the system.

[0030] Furthermore, in step S34, the air intake of the external flow field is captured by the intake duct, and the mass flow rate of the external flow field is calculated according to the following formula:

[0031] q=ρvA=ρvA o φ

[0032] Where q is the external flow mass flow rate, ρ is the density, v is the space velocity, A is the equivalent inlet area, and A0 is the air velocity. o φ is the intake duct area, and φ is the area coefficient, which is set to 1.

[0033] Furthermore, the specific method for establishing the fluid-solid-thermal coupling calculation model of the distributed cooling system and determining the performance results of the distributed cooling system during the quasi-steady-state process in step S4 is as follows:

[0034] S41. Based on the radiator module established in step S1, create a single-tube geometric model of the heat exchange copper tube and perform mesh generation.

[0035] S42. Determine the single-pipe flow parameters based on the one-dimensional liquid-side model described in step S2, and determine the liquid inlet temperature of the first heat dissipation copper pipe.

[0036] S43. Determine the boundary conditions of the coupled calculation model based on the transmitted boundary conditions, and thereby complete the establishment of the fluid-solid-thermal coupled calculation model.

[0037] S44. Obtain the outlet characteristic parameters of the single heat exchange copper tube and use them as the inlet characteristic parameters of the next heat exchange copper tube for calculation. Finally, the characteristic parameters of all the split single heat exchange copper tubes are obtained. The total heat exchange power of the heat exchange copper tube is equal to the sum of the heat exchange power of all single tubes.

[0038] S45. The initial liquid supply temperature for the next iteration is obtained using the fluid-solid-thermal coupling calculation model. The actual total heat exchange power of the distributed cooling system under quasi-steady state is obtained through repeated iterations.

[0039] Furthermore, the specific method for determining the liquid inlet temperature of the first copper tube in step S42 is as follows:

[0040] The initial liquid supply temperature and the rated heat exchange power of the system are selected according to the system's operating conditions. The distributed cooling system uses high-altitude low-temperature air as the cooling medium for heat exchange. The smaller the temperature difference between the inlet and outlet medium of the cold plate side pipe, the worse the heat exchange effect. The cooling medium absorbs the heat from the front-end equipment. The higher the initial liquid supply temperature, the worse the heat exchange effect.

[0041] The temperature rise of the cooling medium can be calculated using the following formula:

[0042]

[0043] Where ΔT is the temperature difference between the inlet and outlet. ρ is the heat flow rate, q is the volumetric flow rate, ρ is the density, and C is the specific heat capacity of the cooling medium.

[0044] The inlet temperature of the first copper tube is determined using the above formula.

[0045] Compared with the prior art, the present invention has the following beneficial effects:

[0046] The simulation method for distributed cooling systems provided by this invention establishes a fluid-solid-thermal coupled calculation model by combining a liquid-side model and an intake-side model. This determines the characteristic parameters of the cooling medium and the external flow field under the corresponding topology and calculates the performance results of the cooling system. It fully considers the coupling between the components and comprehensively evaluates the coupling of the calculation method, thus obtaining relatively accurate quasi-steady-state cooling system performance results and significantly improving the design efficiency of the cooling system. Attached Figure Description

[0047] To more clearly illustrate the technical solutions disclosed in this invention, the accompanying drawings used in some embodiments of this invention will be briefly described below. Obviously, the drawings described below are merely drawings of some embodiments of this invention, and those skilled in the art can obtain other drawings based on these drawings. Furthermore, the drawings described below can be considered schematic diagrams and are not intended to limit the actual dimensions of the products or the actual flow of the methods involved in the embodiments of this invention.

[0048] Figure 1 A flowchart illustrating a simulation method for a distributed cooling system provided in an embodiment of the present invention;

[0049] Figure 2 This is a schematic diagram of the structure of a distributed cooling system provided in an embodiment of the present invention;

[0050] Figure 3 This is a schematic diagram of gas-liquid flow in a distributed cooling system provided in an embodiment of the present invention.

[0051] Figure label:

[0052] 1-External piping; 2-Control components; 3-Power unit; 4-Radiator assembly; 5-Booster oil tank; 6-Inlet duct; 7-Integrated liquid circuit assembly; 8-Cold plate inlet; 9-Cold plate outlet; 10-System direct components; 11-Pipes and components; 12-Gas flow direction; 13-Gas-liquid heat exchanger; 14-Gas passage; 15-Gas outlet. Detailed Implementation

[0053] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention. Therefore, the present invention is not limited to the specific embodiments disclosed below.

[0054] Example 1

[0055] A simulation method for distributed cooling systems, such as Figure 1 As shown, the main steps include:

[0056] S1. Establish the topology diagram and three-dimensional digital model of the distributed cooling system, and construct the tail radiator module, air intake channel module, and motor power module accordingly, and obtain the characteristic parameters of each component of the distributed cooling system.

[0057] S2. Using the aforementioned topology diagram and characteristic parameters, establish a one-dimensional model of the liquid side inside the distributed cooling system;

[0058] S3. Based on the spatial positional relationship and dimensional data of the radiator module and the air intake channel module, establish a three-dimensional calculation model of the air intake side of the distributed cooling system;

[0059] S4. Combining the one-dimensional model on the liquid side and the three-dimensional model on the air intake side, establish a fluid-solid-thermal coupling calculation model for the distributed cooling system. During the model solving process, continuously iterate to determine the performance results of the distributed cooling system in the quasi-steady-state process.

[0060] A typical schematic diagram of a distributed cooling system is shown below. Figure 2 As shown, the system includes external piping 1, control components 2, power unit 3, radiator assembly 4, booster tank 5, air intake duct 6, and integrated fluid circuit assembly 7. The basic operating principle of the system is described as follows: The coolant in the booster tank 5, under the pressure of the power unit 3, flows through the temperature regulating valve and enters the radiator assembly 4, where it exchanges heat with the outside air. Figure 2 The external compartments have been concealed, leaving only the air intake duct 6 as a schematic diagram of the system capturing high-altitude ram gas. The cooling medium then passes through a filter and enters the cold plate of the electronics bay for heat exchange, carrying away heat. Subsequently, the coolant passes through various sensors and enters the pressurization tank 5, completing one working cycle. A schematic diagram of the system's gas-liquid flow is shown below. Figure 3 As shown.

[0061] Further, in step S1, the radiator assembly 4 is meshed using the three-dimensional digital model of the distributed cooling system to establish a tail radiator module; the intake duct 6 is meshed using the three-dimensional digital model of the distributed cooling system to establish an intake channel module; and a motor power module is established by obtaining the characteristic parameters of the power unit 3, wherein the motor power module includes parameters such as current, voltage, speed, and torque of the motor used in this embodiment.

[0062] Furthermore, the characteristic parameters of each component of the distributed cooling system obtained in step S1 include: characteristic parameters of the power unit 3, radiator assembly 4, booster oil tank 5, control assembly 2, and piping system, as well as the dynamic parameters of the motor on the power unit 3 and the overall hydraulic performance data of the internal piping.

[0063] Furthermore, the specific method for establishing the one-dimensional model of the liquid side inside the distributed cooling system in step S2 is as follows:

[0064] S21. Establish the pipe flow characteristics of the distributed cooling system using the topology diagram of the distributed cooling system, the hydraulic characteristic parameters of the flow channel, and the characteristic parameters of the cooling medium itself.

[0065] S22. Based on the motor power module established in step S1, and combined with the pipeline flow characteristics, establish a one-dimensional model of the liquid side inside the distributed cooling system.

[0066] Furthermore, the specific method for establishing the three-dimensional calculation model of the intake side of the distributed cooling system in step S3 is as follows:

[0067] S31. Based on the spatial positional relationship and dimensional data of the intake channel module established in step S1, establish a three-dimensional geometric model of the intake side of the distributed cooling system.

[0068] S32. Based on the physical properties of the air at the corresponding altitude, set the characteristic parameters of the incoming flow in the external flow field, and simplify the flow of the calculation model based on the radiator module established in step S1.

[0069] S33. The three-dimensional geometric model of the air intake side is divided into meshes;

[0070] S34. Set boundary conditions, where the inlet uses mass flow rate and the outlet uses pressure rate.

[0071] S35. Based on the boundary conditions and fluid control equations, calculate the flow field characteristics within the time step, solve for the velocity, pressure, and temperature aerodynamic characteristic parameters of the external flow field, and obtain the inlet side characteristic parameters.

[0072] S36. Based on the intake side characteristic parameters, use the post-processing program to select three sections in the external flow field, calculate the average velocity, average pressure, and average temperature of each section, and take the average value of the three sections to determine the transfer boundary conditions between the external flow field simulation and the single-tube heat transfer simulation, and finally establish the three-dimensional calculation model of the intake side.

[0073] Furthermore, due to the large number of equations to be solved in multiphysics coupling calculations, coupled with the extremely small geometric feature lengths, the number of meshes increases dramatically, greatly complicating the solution. In step S32, the flow conditions of the calculation model are simplified based on the heat sink module established in step S1 to ensure computational efficiency and avoid a sharp increase in solution time after meshing. The specific method is as follows:

[0074] Based on the three-dimensional digital model of the heat sink module, the following simplified assumptions are made regarding the flow:

[0075] Several radiators are divided into several equal parts according to their cross-sections, corresponding to a number of heat exchange copper tubes, and it is assumed that the flow in the several equal parts is uniform, thus obtaining a simplified model of a single heat exchange copper tube.

[0076] The average parameters of the intermediate flow channel are calculated using a simplified model of the single heat exchange copper tube to define the parametric boundary conditions for multi-field coupling.

[0077] If the heat exchange process of the radiator is considered as co-current heat exchange, the actual heat exchange capacity is greater than the calculated heat exchange capacity, which further saves computing resources and leaves design redundancy for the system.

[0078] Furthermore, in step S34, the air intake of the external flow field is captured by the intake duct, and the mass flow rate of the external flow field is calculated according to the following formula:

[0079] q=ρvA=ρvA o φ

[0080] Where q is the external flow mass flow rate, ρ is the density, v is the space velocity, A is the equivalent inlet area, and A0 is the air velocity. o φ is the intake duct area, and φ is the area coefficient, which is set to 1.

[0081] Furthermore, the specific method for establishing the fluid-solid-thermal coupling calculation model of the distributed cooling system and determining the performance results of the distributed cooling system during the quasi-steady-state process in step S4 is as follows:

[0082] S41. Based on the radiator module established in step S1, create a single-tube geometric model of the heat exchange copper tube and perform mesh generation.

[0083] S42. Determine the single-pipe flow parameters based on the one-dimensional liquid-side model described in step S2, and determine the liquid inlet temperature of the first heat dissipation copper pipe.

[0084] S43. Determine the boundary conditions of the coupled calculation model based on the transmitted boundary conditions, and thereby complete the establishment of the fluid-solid-thermal coupled calculation model.

[0085] S44. Obtain the outlet characteristic parameters of the single heat exchange copper tube and use them as the inlet characteristic parameters of the next heat exchange copper tube for calculation. Finally, the characteristic parameters of all the split single heat exchange copper tubes are obtained. The total heat exchange power of the heat exchange copper tube is equal to the sum of the heat exchange power of all single tubes.

[0086] S45. The initial liquid supply temperature for the next iteration is obtained using the fluid-solid-thermal coupling calculation model. The actual total heat exchange power of the distributed cooling system under quasi-steady state is obtained through repeated iterations.

[0087] Furthermore, the specific method for determining the liquid inlet temperature of the first copper tube in step S42 is as follows:

[0088] The initial liquid supply temperature and the rated heat exchange power of the system are selected according to the system's operating conditions. The distributed cooling system uses high-altitude low-temperature air as the cooling medium for heat exchange. The smaller the temperature difference between the inlet and outlet medium of the cold plate side pipe, the worse the heat exchange effect. The cooling medium absorbs the heat from the front-end equipment. The higher the initial liquid supply temperature, the worse the heat exchange effect.

[0089] The temperature rise of the cooling medium can be calculated using the following formula:

[0090]

[0091] Where ΔT is the temperature difference between the inlet and outlet. ρ is the heat flow rate, q is the volumetric flow rate, ρ is the density, and C is the specific heat capacity of the cooling medium.

[0092] The liquid inlet temperature of the first copper tube is determined using the aforementioned relationship.

[0093] In summary, the simulation method for distributed cooling systems provided in this embodiment establishes a fluid-solid-thermal coupled calculation model by combining the liquid-side model and the intake-side model. This determines the characteristic parameters of the cooling medium and the external flow field under the corresponding topology and calculates the performance results of the cooling system. It fully considers the coupling between the components and comprehensively evaluates the coupling of the calculation method, thus obtaining relatively accurate quasi-steady-state cooling system performance results and significantly improving the design efficiency of the cooling system.

[0094] While the present invention has been disclosed above with reference to preferred embodiments, it is not intended to limit the invention. Any person skilled in the art can make possible variations and modifications to the technical solutions of the present invention based on the disclosed content without departing from the spirit and scope of the invention. Therefore, any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of the present invention without departing from the content of the technical solutions of the present invention shall fall within the protection scope of the present invention. The protection scope of the present invention is defined by the appended claims.

Claims

1. A simulation method for a distributed cooling system, characterized in that, The method comprises the following steps: S1, a topological relationship diagram and a three-dimensional numerical model diagram of the distributed cooling system are established, and a tail radiator module, an air inlet channel module and a motor power module are constructed according to the topological relationship diagram and the three-dimensional numerical model diagram, and characteristic parameters of components of the distributed cooling system are obtained; S2, a one-dimensional model of a liquid side of the distributed cooling system is established by using the topological relationship diagram and the characteristic parameters; S3, a three-dimensional calculation model of an air inlet side of the distributed cooling system is established according to spatial position relationship and size data of the radiator module and the air inlet channel module; S4, a flow-solid-heat coupling calculation model of the distributed cooling system is established by combining the one-dimensional model of the liquid side and the three-dimensional calculation model of the air inlet side, and performance results of the distributed cooling system in a quasi-steady state are determined by continuously iterating in a process of solving the model.

2. The simulation method for a distributed cooling system according to claim 1, wherein, In the step S1, the tail radiator module is established by grid division of the tail radiator according to the three-dimensional numerical model diagram of the distributed cooling system.

3. The simulation method for a distributed cooling system according to claim 1, wherein, In the step S1, the air inlet channel module is established by grid division of the air inlet channel according to the three-dimensional numerical model diagram of the distributed cooling system.

4. The simulation method for a distributed cooling system of claim 1, wherein, The motor power module in the step S1 is established according to the characteristic parameters of the power component.

5. The simulation method for a distributed cooling system of claim 1, wherein, The specific method of establishing the one-dimensional model of the liquid side of the distributed cooling system in the step S2 is as follows: S21, pipeline flow characteristics of the distributed cooling system are established by using the topological relationship diagram of the distributed cooling system, flow channel hydraulics characteristic parameters and characteristic parameters of the cooling medium itself; S22, the one-dimensional model of the liquid side of the distributed cooling system is established by combining the pipeline flow characteristics and the motor power module established in the step S1.

6. The simulation method for a distributed cooling system of claim 1, wherein, The specific method of establishing the three-dimensional calculation model of the air inlet side of the distributed cooling system in the step S3 is as follows: S31, a three-dimensional geometric model of the air inlet side of the distributed cooling system is established according to spatial position relationship and size data of the air inlet channel module established in the step S1; S32, characteristic parameters of an outflow field are set according to physical characteristics of corresponding height air, and a flow condition of the calculation model is simplified based on the radiator module established in the step S1; S33, the three-dimensional geometric model of the air inlet side is grid divided; S34, boundary conditions are set, in which a mass flow inlet is adopted at an inlet, and a pressure outlet is adopted at an outlet; S35, flow field characteristics in a time step are calculated according to the boundary conditions and a fluid control equation, velocity, pressure and temperature aerodynamic characteristic parameters of the outflow field are solved, and air inlet side characteristic parameters are obtained; S36, three sections are selected in the outflow field by using a post-processing program according to the air inlet side characteristic parameters, average velocity, average pressure and average temperature of each section are calculated, average values of the three sections are taken, a transfer boundary condition between the outflow field simulation and the single-pipe heat exchange simulation is determined, and finally the three-dimensional calculation model of the air inlet side is established.

7. The simulation method for a distributed cooling system according to claim 6, wherein, In the step S32, the flow condition of the calculation model is simplified based on the radiator module established in the step S1 to ensure calculation efficiency and avoid sharp increase of solving time after grid division, and the specific method is as follows: Based on the three-dimensional model of the radiator module, the following simplifying assumptions are made for the flow conditions: The radiator is divided into several equal parts by cross section, and the flow in each part is assumed to be uniform, resulting in a simplified model of a single heat exchange copper tube; The average parameters of the intermediate flow channel are calculated using the simplified model of a single heat exchange copper tube to define the parameter boundary conditions for multi-field coupling; The heat exchange process of the radiator is considered as counter-flow heat exchange, so the actual situation is greater than the calculated heat exchange capacity, further saving computing resources, and leaving design redundancy for the system.

8. The simulation method for a distributed cooling system according to claim 6, wherein, In step S34, the intake of the external flow field is captured by the intake duct, and the mass flow rate of the external flow field is calculated as follows: q = p v A = p v A o φ where q is the mass flow rate of the outflow field, p is the density, v is the velocity, A is the equivalent inlet area, A o is the inlet area, and f is the area coefficient, which is taken as 1.

9. The simulation method for a distributed cooling system of claim 1, wherein, The specific method for establishing the flow-solid-thermal coupling calculation model of the distributed cooling system and determining the performance results of the distributed cooling system in the quasi-steady state process is as follows: S41. Create a single-tube geometric model of the heat exchange copper tube based on the radiator module established in step S1, and perform meshing; S42. Determine the flow parameters of the single tube based on the one-dimensional model of the liquid side in step S2, and determine the inlet temperature of the first heat exchange copper tube; S43. Determine the boundary conditions of the coupling calculation model based on the transfer boundary conditions, and thereby complete the establishment of the flow-solid-thermal coupling calculation model; S44. Obtain the outlet characteristic parameters of the single heat exchange copper tube and use them as the inlet characteristic parameters of the next heat exchange copper tube for calculation, and finally obtain the characteristic parameters of all the split heat exchange copper tubes. The total heat exchange power of the heat exchange copper tube is equal to the sum of the heat exchange powers of all the single tubes; S45. Use the flow-solid-thermal coupling calculation model to obtain the initial liquid supply temperature for the next iteration, and obtain the actual total heat exchange power of the distributed cooling system under quasi-steady state through repeated iterations.

10. The simulation method for a distributed cooling system of claim 8, wherein, The specific method for determining the inlet temperature of the first copper tube in step S42 is as follows: Select the initial liquid supply temperature and the system rated heat exchange power according to the system operating conditions; Calculate the temperature rise of the cooling medium using the following relationship: where ΔT is the temperature difference between the inlet and outlet, is the heat flow rate, q is the volumetric flow rate, p is the density, and C is the specific heat capacity of the cooling medium. Determine the inlet temperature of the first copper tube using the above relationship.

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