Temperature control board heat exchange capacity calculation method considering turbulent flow structure

Abstract

The invention relates to a temperature control board heat exchange capacity calculation method considering a turbulent flow structure. The method comprises the steps that the Reynolds number in a flow channel of the turbulent flow structure is calculated according to the fluid density, the incoming flow speed, the pipe diameter and the fluid viscosity in the flow channel of the turbulent flow structure; according to the Reynolds number in the flow channel of the turbulent flow structure and the shape of the turbulent flow structure, a corresponding Nusselt number calculation formula is determined; according to the determined Nusselt number calculation formula and the Reynolds number in the flow channel of the turbulent flow structure, the average convective heat transfer coefficient of the surface of the turbulent flow structure is calculated; the turbulent flow structure is regarded as a pin-fin structure, and the rib efficiency of the turbulent flow structure is calculated; and according to the average convective heat transfer coefficient of the surface of the turbulent flow structure and the rib efficiency of the turbulent flow structure, the theoretical heat exchange amount of the temperature control board with the turbulent flow structure is calculated.

Description

Technical Field

[0001] The present application relates to the technical field of heat transfer capacity calculation, and particularly to a method for calculating the heat transfer capacity of a temperature control plate considering a flow disturbance structure. Background Art

[0002] For structures such as the columns of machine tools, temperature control plates are required for heat dissipation. Cooling channels are provided inside the temperature control plate, and heat is transferred from the heat source to the coolant through heat conduction and convective heat transfer to achieve temperature control. To improve the temperature control effect, it is necessary to design a temperature control plate structure with better heat transfer capacity to ensure the best heat transfer effect of the temperature control plate under the same working conditions.

[0003] Modifying the flow channel size and adding flow disturbance structures of different shapes are two common methods for enhancing the heat transfer capacity of the temperature control plate. In the prior art, the calculation method for the heat transfer capacity of the temperature control plate with a flow disturbance structure is not accurate. Summary of the Invention

[0004] To at least overcome to some extent the problem that the calculation method for the heat transfer capacity of the temperature control plate with a flow disturbance structure in the related art is not accurate, the present application provides a method for calculating the heat transfer capacity of a temperature control plate considering a flow disturbance structure.

[0005] The solution of the present application is as follows:

[0006] A method for calculating the heat transfer capacity of a temperature control plate considering a flow disturbance structure, comprising:

[0007] Calculating the Reynolds number in the flow channel of the flow disturbance structure according to the fluid density, the incoming flow velocity, the tube diameter, and the fluid viscosity in the flow channel of the flow disturbance structure;

[0008] Determining the corresponding Nusselt number calculation formula according to the Reynolds number in the flow channel of the flow disturbance structure and the shape of the flow disturbance structure;

[0009] Calculating the average convective heat transfer coefficient on the surface of the flow disturbance structure according to the determined Nusselt number calculation formula and the Reynolds number in the flow channel of the flow disturbance structure;

[0010] Regarding the flow disturbance structure as a pin fin structure and calculating the fin efficiency of the flow disturbance structure;

[0011] Calculating the theoretical heat transfer amount of the temperature control plate with the flow disturbance structure according to the average convective heat transfer coefficient on the surface of the flow disturbance structure and the fin efficiency of the flow disturbance structure.

[0012] Preferably, the method further comprises:

[0013] Determining the arrangement structure of the flow disturbance structure along the fluid flow direction;

[0014] If the arrangement structure of the flow disturbing structure in the fluid flow direction is a multi-row distribution, correct the average convective heat transfer coefficient on the surface of the flow disturbing structure.

[0015] Preferably, the method further includes:

[0016] Calculate the heat transfer amount of the rib wall and the heat transfer amount of the rib surface of the flow disturbing structure;

[0017] Add the heat transfer amount of the rib wall of the flow disturbing structure to the rib base and modify the convective heat transfer coefficient of the rib base.

[0018] Preferably, the method further includes:

[0019] Calculate the actual heat transfer amount of the temperature control board according to the actual measurement results;

[0020] Calculate the actual thermal resistance of the temperature control board according to the actual heat transfer amount of the temperature control board;

[0021] Based on the least squares method, fit the relationship between the actual thermal resistance of the temperature control board, the Reynolds number, and the coolant flow rate to generate a linear regression equation.

[0022] Preferably, the method further includes:

[0023] Adjust the average convective heat transfer coefficient in the total flow channel according to the actual thermal resistance of the temperature control board calculated this time and the pre-generated linear regression equation.

[0024] Preferably, the method further includes:

[0025] Calculate the theoretical heat transfer amount of the temperature control board without the flow disturbing structure;

[0026] Calculate the percentage difference between the theoretical heat transfer amount of the temperature control board without the flow disturbing structure and the theoretical heat transfer amount of the temperature control board with the flow disturbing structure.

[0027] The technical solution provided by this application may include the following beneficial effects:

[0028] This technical solution calculates the Reynolds number in the flow channel of the turbulence structure to clarify the flow state of the fluid, providing a scientific basis for the subsequent selection of the Nusselt number and making the heat transfer model closer to the actual working conditions. According to the specific geometric shape of the turbulence structure, an appropriate Nusselt number calculation formula is determined. This customized Nusselt number processing method avoids the deviation caused by using the general formula, thus more accurately reflecting the influence of the turbulence structure on heat transfer. By calculating the average convective heat transfer coefficient on the surface of the turbulence structure through the relationship between the Nusselt number and the Reynolds number, this step can truly reflect the heat exchange ability between the coolant and the surface of the temperature control plate, improving the credibility of theoretical calculations. Regarding the turbulence structure as a pin fin structure, its fin efficiency is calculated to equivalently correct the uneven local temperature distribution caused by the turbulence structure. The introduction of fin efficiency makes the overall effective heat transfer area of the temperature control plate more accurate, making up for the deficiency of simple convective calculation. Generally speaking, this technical solution comprehensively utilizes the convective heat transfer coefficient and fin efficiency to calculate the theoretical heat transfer amount of the temperature control plate under the condition of adding the turbulence structure, providing a scientific basis for designers to optimize parameters such as the shape and flow channel size of the turbulence structure, and ensuring the best heat dissipation effect under the same working conditions.

[0029] It should be understood that the above general description and the following detailed description are only exemplary and explanatory, and cannot limit this application. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The accompanying drawings herein are incorporated into the specification and constitute a part of this specification, showing embodiments consistent with this application and used together with the specification to explain the principles of this application.

[0031] Figure 1 is a schematic flowchart of a method for calculating the heat transfer capacity of a temperature control plate considering a turbulence structure provided by an embodiment of this application;

[0032] Figure 2 is a schematic diagram of a turbulence structure analysis provided by an embodiment of this application;

[0033] Figure 3 is a schematic flowchart of a method for calculating the heat transfer capacity of a temperature control plate considering a turbulence structure provided by another embodiment of this application;

[0034] Figure 4 is a structural diagram of a device for measuring the heat transfer amount of a temperature control plate provided by an embodiment of this application;

[0035] Figure 5 is a structural diagram of a temperature control plate provided by an embodiment of this application;

[0036] Figure 6 is an internal structural diagram of a flow plate provided by an embodiment of this application;

[0037] Figure 7It is a structural diagram of a heat exchange plate with different spoiler structures provided by an embodiment of the present application.

[0038] Reference numerals: First main board body of the temperature control board - 100; Liquid inlet / outlet - 110; S-shaped flow channel - 120; Elastic washer groove - 130; First main board body of the temperature control board - 200; Hexagonal spoiler structure - 210; Triangular spoiler structure - 220; Square spoiler structure - 230; Cylindrical spoiler structure - 240; Stud - 250; Adapter block - 300; Temperature sensor - 400; Heating plate - 500; Flow sensor - 600; Temperature control system control module - 700; Coolant outlet - 710; Coolant return port - 720; Temperature control system acquisition module - 800; Flow acquisition module - 810; Temperature acquisition module - 820. Detailed implementation manners

[0039] Here, the exemplary embodiments will be described in detail, and the examples are shown in the drawings. When the following description refers to the drawings, unless otherwise indicated, the same numbers in different drawings represent the same or similar elements. The implementation manners described in the following exemplary embodiments do not represent all implementation manners consistent with the present application. On the contrary, they are merely examples of devices and methods consistent with some aspects of the present application as detailed in the appended claims.

[0040] Figure 1 It is a schematic flowchart of a method for calculating the heat exchange capacity of a temperature control board considering a spoiler structure provided by an embodiment of the present application. Figure 2 It is a schematic diagram of spoiler structure analysis provided by an embodiment of the present application. Referring to Figure 1 - Figure 2 , a method for calculating the heat exchange capacity of a temperature control board considering a spoiler structure includes:

[0041] S11: Calculate the Reynolds number in the spoiler structure flow channel according to the fluid density, incoming flow velocity, tube diameter, and fluid viscosity in the spoiler structure flow channel;

[0042] S12: Determine the corresponding Nusselt number calculation formula according to the Reynolds number in the spoiler structure flow channel and the shape of the spoiler structure;

[0043] S13: Calculate the average convective heat transfer coefficient on the surface of the spoiler structure according to the determined Nusselt number calculation formula and the Reynolds number in the spoiler structure flow channel;

[0044] It should be noted that the calculation of the convective heat transfer coefficient on the surface of the spoiler structure needs to be regarded as a heat transfer problem of the fluid sweeping across the tube bundle. First, the Reynolds number in the spoiler structure flow channel needs to be calculated based on the fluid density, incoming flow velocity, tube diameter and fluid viscosity in the spoiler structure flow channel. After obtaining the Reynolds number in the spoiler structure flow channel, the calculation formula of the Nusselt number is selected according to the Reynolds number and the shape of the spoiler structure. Generally speaking, the Reynolds number of the internal flow channel of the temperature control plate is generally 1000-40000, and the calculation formula of the Nusselt number is as follows:

[0045] Nu=CRe n Pr 1 / 3 ;

[0046] For the cylindrical spoiler structure, the coefficient is C = 0.193, n = 0.618;

[0047] For the square cross-section spoiler structure, the coefficient is C = 0.102, n = 0.675;

[0048] For the spoiler structure with regular hexagonal cross section, the coefficient is C = 0.153, n = 0.638;

[0049] The remaining regular structures need to be fitted according to the experimental results, and the remaining cases are calculated using the following standard formula:

[0050]

[0051] S14: Consider the spoiler structure as a pin-fin structure and calculate the rib efficiency of the spoiler structure;

[0052] Since the spoiler structure is a small cylindrical structure, it can be regarded as a pin-fin structure, and the rib efficiency of the spoiler structure can be calculated.

[0053] S15: Calculate the theoretical heat transfer when the temperature control plate has a spoiler structure based on the average convection heat transfer coefficient on the spoiler structure surface and the rib efficiency of the spoiler structure.

[0054] Reference Figure 5 - Figure 7 The temperature control board includes a first main board body 100 and a second main board body 200. At least one S-shaped flow channel 120 is opened inside the first main board body 100 for the circulation of the coolant. The starting section and the ending section of the flow channel have a liquid inlet and a liquid outlet 110, which are connected to the temperature control system loop through an adapter block 300. Threaded holes are opened at the corners of the loop and the center area of ​​the adapter block for connecting a temperature sensor 400 for measuring the coolant temperature. An elastic gasket groove 130 is opened on the outside of the flow channel to place an elastic gasket for sealing.

[0055] A cylindrical turbulator structure for enhancing heat transfer is installed on the second main board body 200. The turbulator structure includes a hexagonal turbulator structure 210, a triangular turbulator structure 220, a square turbulator structure 230, and a cylindrical turbulator structure 240. The board body and the turbulator structure are connected by stud bolts 250. Turbulator structures with different shapes and sizes can be freely replaced and arranged. The contact surface between the turbulator structure and the heat exchange plate is enhanced in heat transfer through thermal grease. The turbulator structure mainly enhances heat transfer by increasing the heat transfer area of the surface and increasing the Reynolds number near the turbulator structure.

[0056] For the same external heat source and under the same coolant flow state, the heat transfer capacity of the temperature control board is judged by the temperature difference between the coolant inlet and outlet, and the heat transfer amount during the heat transfer process is calculated based on the measured temperature.

[0057] Refer to Figure 4 , this embodiment also provides a test experimental device for the heat transfer amount of the temperature control board.

[0058] The heat transfer amount measuring device includes a temperature control board, a heating plate 500, a flow sensor 600, a temperature control system control module 700, and a temperature control system acquisition module 800.

[0059] The heating plate is attached to the heat transfer surface 100 of the temperature control board for controlling and obtaining the heat source temperature.

[0060] The temperature control system control module 700 can control the flow rate, pressure, and temperature of the coolant at the coolant outlet 710 and monitor the flow rate, pressure, and temperature at the coolant return port 720.

[0061] The temperature control system acquisition module 800 includes a flow rate acquisition module 810 and a temperature acquisition module 820, which are used to acquire the inlet and outlet flow rates of the control module and the temperatures of the coolant in each section of the flow channel.

[0062] The temperature and power of the heat source are controlled by the heating plate, and the inlet temperature and flow rate of the coolant are controlled by the active temperature control system. Experiments are carried out under different flow rates and heat source temperature conditions;

[0063] During the experiment, the coolant flow rate and the temperatures T1, T2... Tn of the coolant in each section of the flow channel are measured, and the actual heat transfer amount of each section is calculated based on the measured coolant temperature.

[0064] Based on the above structure, in this embodiment, a calculation method for the heat transfer capacity of a temperature control board considering a turbulence structure is provided. By calculating the Reynolds number in the flow channel of the turbulence structure, the flow state of the fluid is clarified, providing a scientific basis for the selection of the Nusselt number in the subsequent steps, and making the heat transfer model closer to the actual working conditions. According to the specific geometric shape of the turbulence structure, a suitable Nusselt number calculation formula is determined. This customized Nusselt number processing method avoids the deviation caused by using a general formula, thus more accurately reflecting the influence of the turbulence structure on heat transfer. By calculating the average convective heat transfer coefficient on the surface of the turbulence structure through the relationship between the Nusselt number and the Reynolds number, this step can truly reflect the heat exchange capacity between the coolant and the surface of the temperature control board, improving the credibility of the theoretical calculation. Regarding the turbulence structure as a pin fin structure, its fin efficiency is calculated, thereby equivalently correcting the uneven local temperature distribution caused by the turbulence structure. The introduction of fin efficiency makes the overall effective heat transfer area of the temperature control board more accurate, compensating for the deficiency of simple convective calculation. Generally speaking, this technical solution comprehensively utilizes the convective heat transfer coefficient and fin efficiency to calculate the theoretical heat transfer amount of the temperature control board under the condition of adding a turbulence structure, providing a scientific basis for designers to optimize parameters such as the shape and flow channel size of the turbulence structure, and ensuring the best heat dissipation effect under the same working conditions.

[0065] It should be noted that the method further includes:

[0066] Determine the arrangement structure of the turbulence structure along the fluid flow direction;

[0067] If the arrangement structure of the turbulence structure along the fluid flow direction is multi-row distribution, correct the average convective heat transfer coefficient on the surface of the turbulence structure.

[0068] In this embodiment, considering the heat transfer influence caused by the change in the arrangement of the turbulence structure, for a single-row turbulence structure, calculate based on the arrangement distance, calculate the fin surface area based on the number of turbulence structures, and for the case of multi-row turbulence structures in the same flow direction, use the Zhukauskas correlation to correct the Nusselt number.

[0069] By determining the specific arrangement structure of the turbulence structure in the fluid flow direction, different working conditions of single-row and multi-row turbulence structures are distinguished, avoiding the problem of ignoring or overly simplifying the arrangement influence in traditional methods, and thus making the calculation more in line with the actual situation. In the case of multi-row turbulence structures in the same flow direction, interference will occur between rows, affecting the local flow velocity distribution and temperature field. Using the Zhukauskas correlation to correct the Nusselt number can correct the error caused by multi-row arrangement in traditional calculation methods, making the corrected average convective heat transfer coefficient closer to the actual heat transfer effect.

[0070] It should be noted that the method further includes:

[0071] Calculate the heat transfer amount of the fin wall and the heat transfer amount of the fin surface of the turbulence structure;

[0072] Add the heat transfer amount of the rib wall of the turbulence structure to the rib base and modify the convective heat transfer coefficient of the rib base.

[0073] It should be noted that in this embodiment, the turbulence structure is regarded as a pin fin structure. At this time, the protruding part of the turbulence structure is the rib wall, the part of the turbulence structure on the temperature control plate is the rib base, and the rib surface is the outer surface of the rib wall and the rib base.

[0074] Calculation of rib efficiency considering the size of the turbulence structure: Since the turbulence structure is a cylindrical structure with a small size, it can be regarded as a pin fin structure. Assuming that the diameter or hydraulic diameter of the turbulence structure is D and the height is H, the calculation formula for the rib efficiency of the pin fin is as follows:

[0075]

[0076] In the formula, H is the height of the turbulence structure, D is the characteristic size of the turbulence structure, with the unit of m, λ is the thermal conductivity of the solid material, with the unit of W / (m·K), and h is the average convective heat transfer coefficient on the surface of the turbulence structure, with the unit of W / (m2·K).

[0077] Calculation of the heat transfer amount of the rib wall and the total rib surface: Assuming that the average temperature of the surface of the temperature control plate connected to the turbulence structure is T0, the coolant temperature is Tf, the surface area of the temperature control plate connected to the turbulence structure is Ar, and the surface area of the turbulence structure is Af, the calculation of the heat transfer amount of the rib wall and the total rib surface is as follows:

[0078]

[0079] Add the heat transfer amount of the rib wall of the turbulence structure to the rib base and modify the convective heat transfer coefficient of the rib base:

[0080]

[0081] Superimposing the heat transfer amount of the rib wall on the rib base can correct the deficiency of the original convective heat transfer coefficient of the rib base, thereby obtaining a more realistic local heat transfer coefficient. This correction makes the heat transfer performance of the temperature control plate under the actual working condition easier to predict and provides more reliable data support for subsequent design optimization.

[0082] It should be noted that with reference to Figure 3 , the method further includes:

[0083] S21: Calculate the actual heat transfer amount of the temperature control plate according to the actual measurement results;

[0084] S22: Calculate the actual thermal resistance of the temperature control plate according to the actual heat transfer amount of the temperature control plate;

[0085] S23: Based on the least squares method, fit the relationship between the actual thermal resistance of the temperature control plate, the Reynolds number, and the coolant flow rate to generate a linear regression equation.

[0086] Further, the method further includes:

[0087] S24: Adjust the average convective heat transfer coefficient in the total flow channel according to the actual thermal resistance of the temperature control board calculated this time and the pre-generated linear regression equation.

[0088] It should be noted that the method further includes:

[0089] Calculate the theoretical heat transfer amount when there is no flow disturbance structure on the temperature control board;

[0090] Calculate the difference percentage between the theoretical heat transfer amount when there is no flow disturbance structure on the temperature control board and the theoretical heat transfer amount when there is a flow disturbance structure on the temperature control board.

[0091] In specific practice, the setting of boundary conditions: The upper surface is set as a constant temperature heat source, and the temperature of the upper surface, as well as the temperature and flow rate of the coolant inlet, are set;

[0092] Calculation of the equivalent model thermal resistance: The thermal resistance of the square cross-section pipe mainly consists of four parts: the contact thermal resistance Rcontact between the plate and the contact surface, the solid conduction thermal resistance Rcond, the convective heat transfer thermal resistance Rconv, and the fluid enthalpy thermal resistance Rheat. The contact thermal resistance is affected by the solid and surface roughness. The conduction thermal resistance depends on the size of the contact surface and the size of the pipe wall surface. The convective heat transfer thermal resistance mainly depends on the convective heat transfer coefficient and the heat transfer area. The fluid enthalpy thermal resistance depends on the flow rate of the fluid and the material property parameters. The thermal resistance of the model is linearly superimposed in series by the above four parts.

[0093] When there is no flow disturbance structure on the temperature control board, the specific calculation formula for the thermal resistance of the model is as follows:

[0094]

[0095] R total = R contact + R cond + R conv + R heat ;

[0096] Among them, R total is the total thermal resistance. Combining the calculated total thermal resistance R total , calculate the heat transfer amount Q of the temperature control board:

[0097]

[0098] Experimental verification link: Measure the coolant temperatures T in , T out , T1, T2... T n at corresponding positions through sensors at different positions under the same working conditions and structures, and calculate the heat transfer amount of the temperature control board through Newton's cooling formula:

[0099] Q1 = c p q m (T out - T in ),

[0100] where q m is the mass flow rate of the coolant in the flow channel, with the unit of kg / s, and T in is the inlet temperature of the coolant, and T out is the outlet temperature of the coolant.

[0101] Calculate the error between the measured heat transfer amount and the theoretical heat transfer amount in the experiment

[0102]

[0103] Numerical correction based on experimental results: Based on the experimental results, correct the calculated thermal resistance. Since for the temperature control board with the same material and size, among the above four thermal resistances, the thermal conduction thermal resistance and the contact thermal resistance remain unchanged, and both the fluid enthalpy thermal resistance and the convective heat transfer thermal resistance are functions related to the coolant flow rate, the thermal resistance function can be simplified to the following form:

[0104]

[0105] where A n , B n and C n are constants.

[0106] When considering the turbulence structure, the specific calculation formula for the thermal resistance of the model is as follows:

[0107]

[0108] R total = R contact + R cond + R conv + R heat .

[0109] Since the turbulence structure will affect the flow state of the fluid in the entire flow channel, resulting in a certain difference in the calculated convective heat transfer coefficient, in this embodiment, the actual heat transfer amount of the temperature control board is calculated according to the actual measurement results; the actual thermal resistance of the temperature control board is calculated according to the actual heat transfer amount of the temperature control board; the relationship between the actual thermal resistance of the temperature control board, the Reynolds number, and the coolant flow rate is fitted based on the least squares method to generate a linear regression equation. Finally, according to the actual thermal resistance of the temperature control board calculated this time and the pre-generated linear regression equation, the average convective heat transfer coefficient in the total flow channel is adjusted, thereby significantly improving the accuracy of predicting the heat transfer capacity of the temperature control board.

[0110] Calculate the percentage difference between the theoretical heat transfer amount when there is no flow disturbance structure on the temperature control board and the theoretical heat transfer amount when there is a flow disturbance structure on the temperature control board:

[0111]

[0112] Among them, Q 有 represents the theoretical heat transfer amount when there is a flow disturbance structure on the temperature control board, and Q 无 represents the theoretical heat transfer amount when there is no flow disturbance structure on the temperature control board.

[0113] According to the percentage difference between the theoretical heat transfer amount when there is no flow disturbance structure on the temperature control board and the theoretical heat transfer amount when there is a flow disturbance structure on the temperature control board, the heat transfer capacity evaluation of the temperature control board considering the flow disturbance result can be carried out.

[0114] It can be understood that the same or similar parts in the above embodiments can be referred to each other, and the content not detailed in some embodiments can be referred to the same or similar content in other embodiments.

[0115] It should be noted that in the description of the present application, the terms "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance. In addition, in the description of the present application, unless otherwise stated, the meaning of "plurality" refers to at least two.

[0116] Any process or method description in the flowchart or described in other ways herein can be understood as representing a module, segment, or part of code including one or more executable instructions for implementing a specific logical function or process, and the scope of the preferred embodiments of the present application includes additional implementations, where the functions can be executed in a way that is not shown or discussed, including in a substantially simultaneous manner or in a reverse order according to the involved functions, which should be understood by those skilled in the technical field to which the embodiments of the present application belong.

[0117] It should be understood that each part of the present application can be implemented by hardware, software, firmware, or a combination thereof. In the above embodiments, multiple steps or methods can be implemented by software or firmware stored in a memory and executed by a suitable instruction execution system. For example, if implemented by hardware, as in another embodiment, any one of the following well-known technologies in the art or their combinations can be used: discrete logic circuits with logic gate circuits for implementing logical functions on data signals, application-specific integrated circuits with appropriate combinational logic gate circuits, programmable gate arrays (PGAs), field-programmable gate arrays (FPGAs), etc.

[0118] Those of ordinary skill in the art can understand that all or part of the steps carried out in the method of the above embodiments can be completed by instructing relevant hardware through a program, and the program can be stored in a computer-readable storage medium. When the program is executed, it includes one or a combination of the steps of the method embodiments.

[0119] In addition, in each of the embodiments of the present application, the functional units can be integrated into one processing module, or each unit can exist physically alone, or two or more units can be integrated into one module. The above integrated module can be implemented in the form of hardware or in the form of a software functional module. When the above integrated module is implemented in the form of a software functional module and sold or used as an independent product, it can also be stored in a computer-readable storage medium.

[0120] The above-mentioned storage medium can be a read-only memory, a magnetic disk, an optical disc, or the like.

[0121] In the description of this specification, the descriptions with reference to the terms "one embodiment", "some embodiments", "example", "specific example", or "some examples", etc. mean that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described can be combined in a suitable manner in any one or more embodiments or examples.

[0122] Although the embodiments of the present application have been shown and described above, it can be understood that the above embodiments are exemplary and should not be construed as limiting the present application. Those of ordinary skill in the art can make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present application.

Claims

1. A calculation method for the heat exchange capacity of a temperature control board considering a spoiler structure, characterized in that Including: Calculating the Reynolds number in the flow channel of the spoiler structure based on the fluid density, incoming flow velocity, tube diameter, and fluid viscosity in the flow channel of the spoiler structure; Determining the corresponding Nusselt number calculation formula according to the Reynolds number in the flow channel of the spoiler structure and the shape of the spoiler structure; Calculating the average convective heat transfer coefficient on the surface of the spoiler structure according to the determined Nusselt number calculation formula and the Reynolds number in the flow channel of the spoiler structure; Regarding the spoiler structure as a pin fin structure and calculating the fin efficiency of the spoiler structure; Calculating the theoretical heat transfer amount of the temperature control plate with the spoiler structure based on the average convective heat transfer coefficient on the surface of the spoiler structure and the fin efficiency of the spoiler structure.

2. The method according to claim 1, characterized in that, The method further includes: Determining the arrangement structure of the spoiler structure along the fluid flow direction; If the arrangement structure of the spoiler structure along the fluid flow direction is multi-row distribution, correcting the average convective heat transfer coefficient on the surface of the spoiler structure.

3. The method according to claim 1, wherein The method further includes: Calculating the heat transfer amount of the rib wall and the heat transfer amount of the rib surface of the spoiler structure; Adding the heat transfer amount of the rib wall of the spoiler structure to the rib base and modifying the convective heat transfer coefficient of the rib base.

4. The method according to claim 1, wherein The method further includes: Calculating the actual heat transfer amount of the temperature control plate according to the actual measurement results; Calculating the actual thermal resistance of the temperature control plate according to the actual heat transfer amount of the temperature control plate; Fitting the relationship among the actual thermal resistance of the temperature control plate, the Reynolds number, and the coolant flow rate based on the least squares method to generate a linear regression equation.

5. The method according to claim 4, wherein The method further includes: Adjusting the average convective heat transfer coefficient in the total flow channel according to the actual thermal resistance of the temperature control plate calculated this time and the pre-generated linear regression equation.

6. The method according to claim 1, wherein The method further includes: Calculating the theoretical heat transfer amount of the temperature control plate without the spoiler structure; Calculating the percentage difference between the theoretical heat transfer amount of the temperature control plate without the spoiler structure and the theoretical heat transfer amount of the temperature control plate with the spoiler structure.

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