A correction method for support sword resistance in underwater vehicle towing test

Abstract

This application provides a method for correcting the drag of a spar during underwater vehicle towing tests, relating to the technical field of underwater vehicle hydrodynamic performance testing. By introducing a shape factor based on correction methods in the shipbuilding field, the interference of the spar is converted into a pressure-drag correction coefficient. The interference of the spar on the pressure-drag is corrected by combining test data with numerical simulation results, thereby correcting the total drag coefficient and total resistance, reducing the impact of the spar on underwater vehicle towing tank resistance tests. Compared with traditional empirical formulas, standard model comparisons, and pure CFD analysis, this application, relying on the organic combination of test data and simulation results, significantly shortens the calculation cycle and reduces reliance on expensive computing resources. Furthermore, the corrected drag results of the underwater vehicle with spar model are more consistent and reliable than those of the standard underwater vehicle model. This method is suitable for towing tests of various underwater vehicles and has strong versatility and promotional value.

Description

Technical Field

[0001] The present application relates to the technical field of underwater vehicle hydrodynamic performance testing, and in particular to a method for correcting support sword resistance in an underwater vehicle towing test. Background Art

[0002] The resistance performance of underwater vehicles is one of the key indicators for measuring their hydrodynamic performance, which directly affects speed, endurance, propulsion power, energy efficiency and acoustic stealth performance. Therefore, it is crucial to accurately predict the resistance of underwater vehicles during the design, development and performance evaluation stages. The towing tank test is internationally recognized as the main physical test method for predicting the resistance performance of underwater vehicles. By making a scaled-down model, it is dragged at different speeds in the towing tank to measure the resistance. However, in the test, the model is usually connected to the trailer through connecting structures such as support swords. The support swords will generate additional resistance when towing and change the flow field around the model, thereby affecting the accuracy of the resistance measurement.

[0003] In order to obtain a more accurate drag value for a spacecraft, it is necessary to systematically analyze and correct the interference of the support sword. Currently, the commonly used drag correction methods include: (1) estimation correction based on empirical formulas or maps; (2) comparison correction using standard models; (3) using computational fluid dynamics (CFD) numerical simulation methods to assist in the analysis of interference effects and scale effects. However, the existing methods have certain limitations: empirical formulas are based on simplified models and are not accurate enough; the standard model comparison method has strict requirements on the database and experimental conditions and has a limited scope of application; the CFD method has high computational cost and long cycle time, and the accuracy of the calculation results is affected by the mesh quality, turbulence model selection and boundary conditions. Summary of the Invention

[0004] The purpose of this application is to provide a method for correcting the support sword resistance in the underwater vehicle towing test, in order to address the problems of low support sword resistance correction accuracy, insufficient universality and low calculation efficiency in the existing technology.

[0005] To achieve the above objectives, the technical solutions adopted in this application are as follows:

[0006] The present application provides a method for correcting the support sword resistance in an underwater vehicle towing test, comprising:

[0007] S1: define the shape factors of the underwater vehicle standard model and the underwater vehicle with a supported sword model, and calculate the pressure-drag correction coefficient of the underwater vehicle with a supported sword model according to the shape factors of the underwater vehicle standard model and the underwater vehicle with a supported sword model;

[0008] S2: Calculate the experimental pressure drag coefficient of the underwater vehicle with supported sword model based on the pressure drag correction coefficient, the shape factor of the underwater vehicle standard model and the experimental total drag coefficient of the underwater vehicle with supported sword model;

[0009] S3: Calculate the difference in pressure drag coefficient of the underwater vehicle with a supported sword model based on the simulated pressure drag coefficients of the underwater vehicle standard model and the underwater vehicle with a supported sword model, and calculate the corrected pressure drag coefficient of the underwater vehicle with a supported sword model based on the test pressure drag coefficient and the pressure drag coefficient difference;

[0010] S4: Calculate the corrected total drag coefficient of the underwater vehicle with the supported sword model according to the corrected pressure drag coefficient and the simulated friction drag coefficient of the underwater vehicle standard model, and calculate the corrected total resistance of the underwater vehicle with the supported sword model according to the corrected total drag coefficient.

[0011] Furthermore, S1 includes:

[0012] S11: Calculate the simulated total drag coefficient and simulated friction drag coefficient of the standard model of the underwater vehicle at different Reynolds numbers, and calculate the simulated total drag coefficient and simulated friction drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers;

[0013] S12: The shape factors of the standard underwater vehicle model and the underwater vehicle with support sword model are defined as:

[0014]

[0015]

[0016] in,( 1+K) is the shape factor of the standard model of underwater vehicle at different Reynolds numbers, ( 1+K) S is the shape factor of the underwater vehicle with a supported sword model at different Reynolds numbers, 1 is the reference friction resistance of the equivalent flat plate, K is the shape correction factor, which represents the difference in additional drag coefficient caused by the actual shape of the underwater vehicle. (C T ) CFD and (C F ) CFD are the simulated total drag coefficient and simulated friction drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, (C TS ) CFD and (C FS )CFD They are respectively the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0017] S13: Calculate the pressure-drag correction coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers. The calculation formula is:

[0018]

[0019] in, λ The pressure-drag correction coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0020] S14: Calculate the average value of the pressure-drag correction coefficient at different Reynolds numbers .

[0021] Furthermore, S2 includes:

[0022] S21: Measure the total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0023] S22: Calculate the test pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers. The calculation formula is:

[0024]

[0025] in, (C P ) EXP is the experimental pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, (C T ) EXP is the experimental total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers.

[0026] Furthermore, S3 includes:

[0027] S31: Calculate the simulated pressure-drag coefficients of the standard underwater vehicle model and the underwater vehicle with a supported sword model at different Reynolds numbers;

[0028] S32: Calculate the difference in simulated pressure-drag coefficient of the underwater vehicle with a supporting sword model at different Reynolds numbers. The calculation formula is:

[0029]

[0030] in, ΔC P is the difference in the simulated pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, (C P) CFD is the simulated pressure drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, (C PS ) CFD The simulated pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0031] S33: Calculate the modified pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0032]

[0033] in, (C P ) CORR The modified pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers.

[0034] Furthermore, S4 includes:

[0035] S41: The calculation formula of the simulated friction drag coefficient of the standard model of the underwater vehicle is fitted based on the empirical formula of the flat plate friction drag coefficient:

[0036]

[0037] in, (C F ) CORR is the fitting friction drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, Re is the Reynolds number;

[0038] S42: Calculate the corrected total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0039]

[0040] in, (C T ) CORR The corrected total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0041] S43: Calculate the corrected total drag of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0042]

[0043] in, (R T ) CORRis the modified total resistance of the underwater vehicle with a supported sword model at different Reynolds numbers, ρ is the density of water, V is the navigation speed of the underwater vehicle, S a Wetted surface area for underwater vehicles.

[0044] Furthermore, S3 further includes: before S33, using a logarithmic function to fit the calculation formula of the simulated pressure-resistance coefficient difference obtained in S32:

[0045]

[0046] in, ΔC P ’ The difference in the fitted pressure-drag coefficients of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0047] In S33, .

[0048] Furthermore, S4 also includes: verifying the degree of deviation between the fitted friction resistance coefficient of the underwater vehicle standard model obtained in S41 and the simulated friction resistance coefficient of the underwater vehicle standard model by calculating the variance.

[0049] Furthermore, the method further comprises:

[0050] S5: Compare the corrected total drag coefficient of the underwater vehicle with the supported sword model with the experimental total drag coefficient of the underwater vehicle standard model to verify the accuracy of the corrected total drag coefficient of the underwater vehicle with the supported sword model.

[0051] Furthermore, in S11, fluid dynamics software is used to calculate the simulated total drag coefficient and simulated friction drag coefficient of the standard model of the underwater vehicle and the simulated total drag coefficient and simulated friction drag coefficient of the underwater vehicle with support sword model.

[0052] Furthermore, the method is used to correct the support sword resistance in the towing test of the rotating body underwater vehicle.

[0053] The beneficial effects of this application include:

[0054] This application provides a method for correcting the drag of a spar during underwater vehicle towing tests. By introducing a shape factor based on correction methods used in the shipbuilding field, the interference of the spar is converted into a pressure drag correction coefficient. This correction is then combined with test data and numerical simulation results to correct the spar's interference with the pressure drag, thereby correcting the total drag coefficient and total resistance. This method reduces the impact of the spar on underwater vehicle towing tank drag tests. Compared with traditional empirical formulas, standard model comparisons, and pure CFD analysis, this application, relying on the organic combination of test data and simulation results, significantly shortens the calculation cycle and reduces reliance on expensive computing resources. Furthermore, the corrected drag results for the underwater vehicle with spar model are more consistent and reliable than those for the standard underwater vehicle model. This method is suitable for towing tests of various underwater vehicles and has strong versatility and promotional value. BRIEF DESCRIPTION OF THE DRAWINGS

[0055] In order to more clearly illustrate the technical solution of the present application, the following is a brief introduction to the drawings required for use in the embodiments. It should be understood that the following drawings only show certain embodiments of the present application and therefore should not be regarded as limiting the scope. For ordinary technicians in this field, other relevant drawings can be obtained based on these drawings without paying any creative work.

[0056] Figure 1 A flow chart of a method for correcting the support sword resistance in an underwater vehicle towing test provided in this application;

[0057] Figure 2 The fitting curve of the simulated pressure-drag coefficient difference of the underwater vehicle with a supported sword model provided in this application;

[0058] Figure 3 This is the fitting curve of the simulated friction drag coefficient of the standard model of the underwater vehicle provided in this application. DETAILED DESCRIPTION

[0059] To make the objectives, technical solutions, and advantages of this application more clear, the technical solutions of this application will be clearly and completely described below in conjunction with the accompanying drawings. Obviously, the described embodiments are only some of the embodiments of this application, not all of them. Generally, the components of this application described and shown in the drawings herein can be arranged and designed in various different configurations.

[0060] Therefore, the following detailed description of the embodiments of the present application provided in the accompanying drawings is not intended to limit the scope of the present application as claimed, but merely represents selected embodiments of the present application. It should be noted that, unless there is a conflict, the various features of the embodiments of the present application may be combined with each other, and the combined embodiments are still within the scope of protection of the present application.

[0061] It should be noted that similar reference numerals and letters denote similar items in the following drawings, and therefore, once an item is defined in one drawing, it does not need to be further defined or explained in subsequent drawings.

[0062] The technical solution of the present application is described in detail below with reference to specific embodiments.

[0063] Under the influence of the support sword, the proportion of the drag coefficient components of the underwater vehicle model changes, and the support sword has the greatest impact on the underwater vehicle model's pressure drag coefficient. Therefore, the following assumption is made during the correction: assuming that the total drag coefficient increase obtained in the towing test is caused by an increase in the pressure drag coefficient, the main direction of the correction is to correct the experimental pressure drag coefficient.

[0064] Based on this, the present application provides a method for correcting the support sword resistance in the underwater vehicle towing test, wherein the underwater vehicle model can be a body of revolution model, a wing-body fusion model or other shape model. In this embodiment, the correction method is analyzed by taking the body of revolution model as an example. First, the shape factor is introduced with reference to the correction method in the field of ships, and the influence of the support sword is introduced as a pressure drag correction coefficient. Secondly, the test pressure drag coefficient can be accurately obtained based on the shape factor, the pressure drag correction coefficient and the total test drag coefficient measured by the test. Then, the CFD comparative correction method in the aviation field is used to calculate the simulated pressure drag coefficient increment of the model with support sword compared to the standard model, and the test pressure drag coefficient is corrected to finally obtain the corrected test total drag coefficient and total resistance. As Figure 1 As shown, the method specifically includes the following steps:

[0065] S1: Define the shape factors of the underwater vehicle standard model and the underwater vehicle with supported sword model, and calculate the pressure-drag correction coefficient of the underwater vehicle with supported sword model based on the shape factors of the underwater vehicle standard model and the underwater vehicle with supported sword model.

[0066] Furthermore, S1 includes:

[0067] S11: Use CFD software to calculate the simulated total drag coefficient and simulated friction drag coefficient of the standard model of the underwater vehicle at different Reynolds numbers, and calculate the simulated total drag coefficient and simulated friction drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers;

[0068] S12: Referring to the correction method in the field of ships, the shape factors of the standard model of underwater vehicles and the model of underwater vehicles with supporting swords are defined as:

[0069]

[0070]

[0071] in,( 1+K) is the shape factor of the standard model of underwater vehicle at different Reynolds numbers, ( 1+K) S is the shape factor of the underwater vehicle with a supported sword model at different Reynolds numbers, 1 is the reference friction resistance of the equivalent flat plate, K is the shape correction factor, which represents the difference in additional drag coefficient caused by the actual shape of the underwater vehicle. In this embodiment, additional drag refers to pressure drag. (C T ) CFD and (C F ) CFD are the simulated total drag coefficient and simulated friction drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, (C TS ) CFD and (C FS ) CFD They are respectively the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0072] S13: Calculate the pressure-drag correction coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers. The calculation formula is:

[0073]

[0074] in, λ The pressure-drag correction coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0075] S14: Calculate the average value of the pressure-drag correction coefficient at different Reynolds numbers .

[0076] In this embodiment, the range of Reynolds number is The following table shows the shape factors and pressure-drag correction coefficients of the standard model of the rotating underwater vehicle and the rotating underwater vehicle with a supporting sword model at different Reynolds numbers. The average value of the pressure-drag correction coefficient in this embodiment can be calculated by S14. It is 0.8635.

[0077]

[0078] S2: Calculate the experimental pressure drag coefficient of the underwater vehicle with supported sword model based on the pressure drag correction coefficient, the shape factor of the underwater vehicle standard model and the experimental total drag coefficient of the underwater vehicle with supported sword model.

[0079] Furthermore, S2 includes:

[0080] S21: The total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers is measured using a force sensor installed in the test device;

[0081] S22: Calculate the test pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers. The calculation formula is:

[0082]

[0083] in, (C P ) EXP is the experimental pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, (C T ) EXP is the total drag coefficient of the underwater vehicle with a supported sword model under different Reynolds numbers. The range of Reynolds numbers is .

[0084] S3: Calculate the difference in pressure drag coefficient of the underwater vehicle with a supported sword model based on the simulated pressure drag coefficients of the underwater vehicle standard model and the underwater vehicle with a supported sword model, and calculate the corrected pressure drag coefficient of the underwater vehicle with a supported sword model based on the test pressure drag coefficient and the pressure drag coefficient difference;

[0085] Furthermore, S3 includes:

[0086] S31: Use CFD software to calculate the simulated pressure-drag coefficient of the standard underwater vehicle model and the underwater vehicle with a supported sword model at different Reynolds numbers;

[0087] S32: Calculate the difference in simulated pressure-drag coefficient of the underwater vehicle with a supporting sword model at different Reynolds numbers. The calculation formula is:

[0088]

[0089] in, ΔC P is the difference in the simulated pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, (C P ) CFD is the simulated pressure drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, (C PS ) CFD The simulated pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0090] The following table shows the difference in simulated pressure-drag coefficients of the rotating underwater vehicle with a supported sword model relative to the standard rotating underwater vehicle model at different Reynolds numbers.

[0091]

[0092] It should be understood that the simulated pressure-drag coefficient difference of the underwater vehicle with a support sword model at different Reynolds numbers is a discrete point, and a calculation formula can be fitted to facilitate the correction of the experimental pressure-drag coefficient. Since the order of magnitude of the Reynolds number is much larger than the drag coefficient, a simple polynomial fitting cannot be performed. A logarithmic function is used to fit the simulated pressure-drag coefficient difference in the table above, as shown in the following example: Figure 2 As shown, it is fitted as a function of Reynolds number, and the specific calculation formula is:

[0093]

[0094] in, ΔC P ’ is the difference in the fitted pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, Re is the Reynolds number, ;

[0095] S33: Calculate the modified pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0096]

[0097] in, (C P ) CORR The modified pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers.

[0098] S4: Calculate the corrected total drag coefficient of the underwater vehicle with the supported sword model according to the corrected pressure drag coefficient and the simulated friction drag coefficient of the underwater vehicle standard model, and calculate the corrected total resistance of the underwater vehicle with the supported sword model according to the corrected total drag coefficient.

[0099] Furthermore, S4 includes:

[0100] S41: Based on the empirical formula of flat plate friction drag coefficient in the aviation field, the simulated friction drag coefficient of the standard model of the rotating underwater vehicle obtained in S1 is fitted as follows: Figure 3 The curve shown in Figure 1 is used to obtain the calculation formula for the fitting friction resistance coefficient:

[0101]

[0102] in, (C F ) CORR is the fitting friction drag coefficient of the standard model of underwater vehicle at different Reynolds numbers, Re is the Reynolds number, ;

[0103] It should be noted that the deviation between the fitted friction drag coefficient of the standard model of the rotating underwater vehicle obtained by S41 and the simulated friction drag coefficient of the standard model of the rotating underwater vehicle can be verified by calculating the variance. The variance R 2 If it is greater than 0.95, it means that this formula can capture the changing trend of the data very well and is consistent with the actual situation.

[0104] S42: Calculate the corrected total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0105]

[0106] in, (C T ) CORR The corrected total drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers;

[0107] S43: Calculate the corrected total drag of the underwater vehicle with a supported sword model at different Reynolds numbers:

[0108] The calculation formula of the total drag coefficient of the underwater vehicle model is:

[0109]

[0110] The calculation formula for the corrected total resistance of the underwater vehicle with a supporting sword model is:

[0111]

[0112] in, (R T ) CORR is the modified total resistance of the underwater vehicle with a supported sword model at different Reynolds numbers, ρ is the density of water, V is the navigation speed of the underwater vehicle, S a Wetted surface area for underwater vehicles.

[0113] S5: Compare the corrected total drag coefficient of the underwater vehicle with the supported sword model with the experimental total drag coefficient of the underwater vehicle standard model to verify the accuracy of the corrected total drag coefficient of the underwater vehicle with the supported sword model.

[0114] In this embodiment, the test is conducted in a towing pool with a length of 170 m, a width of 7 m, and a depth of 6 m. The depth of the rotating body model is 2.4 m and the speed is 5 m / s.

[0115] After correcting the uncertainty of the measuring instrument, the complete expression of the average value of the five tests of the total drag coefficient of the standard model of the underwater vehicle is obtained:

[0116]

[0117] The complete expression of the modified total drag coefficient of the underwater vehicle with a supported sword model is as follows:

[0118]

[0119] Compared to the test results of a standard underwater vehicle model, the corrected error is less than 5%, demonstrating that the correction method proposed in this application effectively reduces the impact of the rapier on underwater vehicle towing tank resistance tests. Compared to traditional empirical formulas, standard model comparisons, and pure CFD analysis, this application, by integrating test data with simulation results, significantly shortens the calculation cycle and reduces reliance on expensive computing resources. Furthermore, the corrected resistance results of the underwater vehicle with rapier model are more consistent and reliable than those of the standard underwater vehicle model, making it applicable to towing tests of various underwater vehicles and showing universal applicability.

[0120] The above description is merely a preferred embodiment of the present application and is not intended to limit the present application. Various modifications and variations are possible for those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present application shall be included within the scope of protection of the present application.

Claims

1. A method for correcting the support sword resistance in an underwater vehicle towing test, characterized in that: include: S1: defining the shape factors of the underwater vehicle standard model and the underwater vehicle with a supported sword model, and calculating the pressure-drag correction coefficient of the underwater vehicle with a supported sword model according to the shape factors of the underwater vehicle standard model and the underwater vehicle with a supported sword model, wherein S1 specifically includes: S11: calculating the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle standard model at different Reynolds numbers, and calculating the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers; S12: The shape factors of the underwater vehicle standard model and the underwater vehicle with support sword model are defined as: in,( 1+K) is the shape factor of the standard model of the underwater vehicle at different Reynolds numbers, ( 1+K) S is the shape factor of the underwater vehicle with a supported sword model at different Reynolds numbers, 1 is the reference friction resistance of the equivalent flat plate, K is the shape correction factor, which represents the difference in additional drag coefficient caused by the actual shape of the underwater vehicle. (C T ) CFD and (C F ) CFD are respectively the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle standard model at different Reynolds numbers, (C TS ) CFD and (C FS ) CFD are respectively the simulated total drag coefficient and the simulated friction drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers; S13: Calculate the pressure-drag correction coefficient of the underwater vehicle with support sword model at different Reynolds numbers, and the calculation formula is: in, λ is the pressure-drag correction coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers; S14: Calculate the average value of the pressure-drag correction coefficient at different Reynolds numbers ; S2: Calculating the test pressure drag coefficient of the underwater vehicle with support sword model according to the pressure drag correction coefficient, the shape factor of the underwater vehicle standard model, and the test total drag coefficient of the underwater vehicle with support sword model, wherein S2 specifically includes: S21: measuring the total drag coefficient of the underwater vehicle with the supported sword model at different Reynolds numbers; S22: Calculate the test pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers. The calculation formula is: in, (C P ) EXP is the experimental pressure drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers, (C T ) EXP is the total drag coefficient of the underwater vehicle with a supported sword model under different Reynolds numbers; S3: calculating a difference in the pressure drag coefficient of the underwater vehicle with a supported sword model based on the simulated pressure drag coefficients of the underwater vehicle standard model and the underwater vehicle with a supported sword model, and calculating a corrected pressure drag coefficient of the underwater vehicle with a supported sword model based on the test pressure drag coefficient and the pressure drag coefficient difference; S4: Calculate the corrected total resistance coefficient of the underwater vehicle with support sword model according to the corrected pressure resistance coefficient and the simulated friction resistance coefficient of the underwater vehicle standard model, and calculate the corrected total resistance of the underwater vehicle with support sword model according to the corrected total resistance coefficient.

2. The method according to claim 1, characterized in that The S3 includes: S31: Calculating simulated pressure-drag coefficients of the underwater vehicle standard model and the underwater vehicle with support sword model at different Reynolds numbers; S32: Calculate the difference in simulated pressure-drag coefficients of the underwater vehicle with support sword model at different Reynolds numbers, using the following formula: in, ΔC P is the difference in simulated pressure-drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers, (C P ) CFD is the simulated pressure-drag coefficient of the standard model of the underwater vehicle at different Reynolds numbers, (C PS ) CFD is the simulated pressure-drag coefficient of the underwater vehicle with a supported sword model at different Reynolds numbers; S33: Calculate the modified pressure drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers: in, (C P ) CORR is the modified pressure drag coefficient of the underwater vehicle with supported sword model at different Reynolds numbers.

3. The method according to claim 2, characterized in that The S4 includes: S41: The calculation formula of the simulated friction resistance coefficient of the underwater vehicle standard model is fitted based on the empirical formula of the flat plate friction resistance coefficient: in, (C F ) CORR is the fitting friction drag coefficient of the underwater vehicle standard model at different Reynolds numbers, Re is the Reynolds number; S42: Calculate the corrected total drag coefficient of the underwater vehicle with support sword model at different Reynolds numbers: in, (C T ) CORR is the modified total drag coefficient of the underwater vehicle with supported sword model at different Reynolds numbers; S43: Calculate the corrected total resistance of the underwater vehicle with support sword model at different Reynolds numbers: in, (R T ) CORR is the modified total resistance of the underwater vehicle with supported sword model at different Reynolds numbers, ρ is the density of water, V is the navigation speed of the underwater vehicle, S a A wetted surface area is provided for the underwater vehicle.

4. The method according to claim 2, characterized in that The step S3 further includes: before the step S33, using a logarithmic function to fit the calculation formula of the simulated pressure-resistance coefficient difference obtained in the step S32: in, ΔC P ’ is the difference in fitted pressure-drag coefficients of the underwater vehicle with a supported sword model at different Reynolds numbers; In the S33, .

5. The method according to claim 3, characterized in that The S4 further includes: verifying the degree of deviation between the fitted friction resistance coefficient of the underwater vehicle standard model obtained in the S41 and the simulated friction resistance coefficient of the underwater vehicle standard model by calculating the variance.

6. The method according to any one of claims 1 to 5, characterized in that The method further comprises: S5: Compare the corrected total drag coefficient of the underwater vehicle with the supported sword model with the experimental total drag coefficient of the underwater vehicle standard model to verify the accuracy of the corrected total drag coefficient of the underwater vehicle with the supported sword model.

7. The method according to any one of claims 1 to 5, characterized in that In S11, fluid dynamics software is used to calculate the simulated total drag coefficient and simulated friction drag coefficient of the underwater vehicle standard model and the simulated total drag coefficient and simulated friction drag coefficient of the underwater vehicle with support sword model.

8. The method according to any one of claims 1 to 5, characterized in that The method is used to correct the support sword resistance in the towing test of the rotating body underwater vehicle.

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