Method, device, equipment and medium for analyzing high-cycle fatigue of anisotropic material blade

Abstract

The application discloses an anisotropic material blade high-cycle fatigue analysis method, device, equipment and medium, the anisotropic material blade high-cycle fatigue analysis method is based on anisotropic material blade vibration stress test data and the actual crystal direction of the measured blade, fully considers the influence of the actual blade crystal direction angle change on the blade vibration characteristic and the influence of the excitation force change caused by the resonance speed change, establishes an engineering available anisotropic material blade high-cycle fatigue evaluation method, the statistics is more comprehensive, is convenient for finding out the more dangerous maximum vibration stress point scientifically, improves the accuracy of vibration stress correction, fully considers the vibration stress superposition effect, so that the high-cycle fatigue evaluation is more scientific, and can be suitable for the high-cycle fatigue evaluation of anisotropic material blades.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of blade material analysis, in particular, to a high-cycle fatigue analysis method, device, equipment and medium for anisotropic material blade. BACKGROUND

[0002] High-cycle fatigue evaluation of an aero gas turbine engine blade is an important content in CCAR-33-R2, and the high-cycle fatigue evaluation method based on vibration strain test data is one of the conventional means for high-cycle fatigue evaluation.

[0003] At present, the high-cycle fatigue evaluation method based on vibration strain test data is to simply consider several groups of crystal direction angle combinations, and select a group of combinations of the maximum vibration stress to carry out high-cycle fatigue evaluation. However, this high-cycle fatigue evaluation method has many shortcomings, resulting in insufficient scientificity, accuracy and reliability of the evaluation results, such as:

[0004] 1. The combination of crystal direction angles is not fully considered; 2. Only the evaluation of the maximum vibration stress of the blade is considered, and the maximum vibration stress may not be the most dangerous state, and it needs to be comprehensively judged in combination with the steady-state stress, for example, a combination point of a larger vibration stress and the maximum steady-state stress may be more dangerous than the maximum vibration stress point; 3. The existing vibration stress correction considers that the maximum vibration stresses of the blades with different crystal direction angles are equal, and does not consider the influence of blade frequency change on the vibration stress; 4. The vibration stress superposition effect is not considered. SUMMARY

[0005] The present application provides a high-cycle fatigue analysis method for anisotropic material blade, which is used to solve the technical problem of insufficient scientificity, accuracy and reliability of the evaluation results of the existing high-cycle fatigue evaluation method.

[0006] The present application is realized by the following scheme:

[0007] The high-cycle fatigue analysis method for anisotropic material blade comprises the following steps:

[0008] S1. The vibration modal of the test blade and the conversion blade is calculated according to different crystal direction angles by using the finite element method, and the vibration frequency and stress distribution of each order are obtained; the strength of the blade is calculated by using the finite element method, and the steady-state stress of the blade under various states is obtained;

[0009] S2. Strain gauges are pasted on the blade, stress data are obtained by measuring the strain during the engine running process, the crystal direction angle of the test blade and the conversion blade is obtained by crystal direction analysis, the engine dynamic stress measurement test is carried out according to the relevant specifications of "Design of Measurement Points for Blade Vibration Stress Measurement Test" and "Technical Requirements for Blade Dynamic Stress Measurement Test", and the actual maximum vibration stress of the test blade is obtained.

[0010] S3, according to the strain value measured by the strain gauge attached on the blade, the vibration stress is converted, and according to the different vibration modes of each order, the maximum displacement of the test blade of each order is converted;

[0011] S4, according to the proportional relationship between the displacement of the blade and the frequency, the maximum displacement of the conversion blade of each order is obtained;

[0012] S5, the vibration stress distribution of the conversion blade is converted, and the test blade is referred to, and according to the different vibration modes of each order, the vibration stress distribution of the conversion blade of each order is converted;

[0013] S6, for any two orders of resonance speed, such as satisfying the condition, the vibration stress is superimposed, and a new stress state after superposition is obtained;

[0014] S7, according to the vibration stress and the steady stress value, a GoodMan diagram is drawn, and high cycle fatigue evaluation is carried out for the test blade and the conversion blade respectively, wherein, when the high cycle fatigue evaluation is carried out for any two orders of vibration stress, the new stress after superposition is used for evaluation, and the vibration stress is still taken before superposition when the rest of the orders are evaluated.

[0015] Further, in step S1, the vibration mode of the conversion blade is calculated according to different crystal direction angles by using the finite element method, and the vibration frequency and stress distribution of each order are obtained, which specifically includes the following steps:

[0016] S100, the crystal main axis included angle range of the conversion blade

[001] direction is determined (-θ°~θ°), and the crystal main axis included angle range of

[010] direction and

[011] direction is (-180°~180°);

[0017] S101, a plurality of included angle combinations are selected from the crystal main axis included angle range of the three directions to form a plurality of included angle combinations, and a matrix of included angle combinations is formed;

[0018] S102, the modal analysis of the conversion blade is carried out according to different crystal direction angles by using the finite element method, the corresponding group of vibration frequency calculation results are obtained, and the vibration frequency and stress distribution of each order of the conversion blade are obtained.

[0019] Further, in step S1, the vibration mode of the test blade is calculated according to different crystal direction angles by using the finite element method, and the vibration frequency and stress distribution of each order are obtained, which specifically includes the following steps:

[0020] S110, the crystal direction angle measurement of the test blade with N strain gauges is carried out, N groups of crystal direction angle data of the strain gauges are measured, the finite element calculation is carried out according to N groups of crystal direction angle data, N groups of frequency calculation results are obtained, and N groups of test blade vibration frequency and stress distribution of each order are obtained.

[0021] Furthermore, in step S3, the strain values ​​measured by the strain gauges attached to the blade are converted into vibration stress. Based on the different mode shapes of each order, the maximum displacement of the test blade at each order is calculated as follows:

[0022] ;

[0023] In the formula, σ represents the stress value obtained from the test of the test blade; Indicates the test blade number i The ratio of the maximum displacement of the vibration mode to the test stress value is obtained through modal calculation of the test blade; Indicates the test blade number i Maximum displacement of the mode shape.

[0024] Furthermore, in step S4, based on the proportional relationship between blade displacement and frequency, the maximum displacement of the converted blade for each order is obtained as follows:

[0025] ;

[0026] In the formula, Indicates the conversion of the first blade i The first frequency is obtained by modal calculation of the blade; Indicates the test blade number i The first frequency is obtained through modal calculations of the test blade; Indicates the conversion of the first blade i Maximum displacement value of the mode shape.

[0027] Further, in step S5, the vibration stress distribution of the blade is calculated. Referring to the test blade, the vibration stress distribution of each order of the blade is calculated according to the different mode shapes, specifically as follows:

[0028] ;

[0029] In the formula, This represents the stress value obtained from the blade test. Indicates the conversion of the first blade i Maximum displacement of the mode shape, Indicates the conversion of the first blade i The ratio of the maximum displacement of the mode shape to the test stress value is obtained by modal calculation of the blade.

[0030] Furthermore, step S6 specifically includes the following steps:

[0031] S61, For any two-order resonance speed , , Determine whether the conditions are met:

[0032] ;

[0033] S62, if yes, stress superposition is performed, and the method of stress superposition is as follows:

[0034] The first stress state is:

[0035] ;

[0036] wherein, σ x1 , σ y1 , σ z1 respectively represent the normal stresses in x, y and z directions under the first stress state, τ x1 , τ y1 , τ z1 respectively represent the shear stresses in x, y and z directions under the first stress state;

[0037] The second stress state is:

[0038] ;

[0039] wherein, σ x2 , σ y2 , σ z2 respectively represent the normal stresses in x, y and z directions under the second stress state, τ x2 , τ y2 , τ z2 respectively represent the shear stresses in x, y and z directions under the second stress state;

[0040] The new stress state after superposition is:

[0041] .

[0042] Another aspect of the present application also provides an anisotropic material blade high-cycle fatigue analysis device, comprising:

[0043] a blade strength vibration calculation module, configured to calculate the vibration mode of a test blade or a converted blade according to different crystal orientation angles by using a finite element method, to obtain vibration frequencies and stress distributions of each order; and calculate the strength of the blade by using the finite element method to obtain the steady stress of the blade under various states;

[0044] A dynamic stress measurement test module is used for pasting strain gauges on a blade, obtaining stress data through strain measurement during engine operation, obtaining a crystal direction angle of a test blade and a conversion blade through crystal direction analysis, performing an engine dynamic stress measurement test according to relevant specifications of "Test Point Design of Blade Vibration Stress Measurement Test" and "Technical Requirements of Blade Dynamic Stress Measurement Test", and obtaining an actual maximum vibration stress of the test blade;

[0045] A test blade maximum displacement calculation module is used for converting a strain value measured by a strain gauge pasted on a blade into a vibration stress, and converting a maximum displacement of each order of the test blade according to different vibration modes of each order;

[0046] A conversion blade maximum displacement module is used for obtaining a maximum displacement of each order of the conversion blade according to a proportional relationship between blade displacement and frequency;

[0047] A conversion blade vibration stress distribution calculation module is used for converting a vibration stress distribution of the conversion blade, and converting a vibration stress distribution of each order of the conversion blade according to different vibration modes of each order, with reference to the test blade;

[0048] A vibration stress superposition module is used for superimposing vibration stresses at any two orders of resonance rotation speed, such as a full load condition, to obtain a new stress state after superposition.

[0049] A blade high-cycle fatigue evaluation module is used for drawing a GoodMan diagram according to a vibration stress and a steady-state stress value, and performing high-cycle fatigue evaluation on a test blade and a conversion blade, wherein, when performing high-cycle fatigue evaluation on any two orders of vibration stress, a new stress after superposition is used for evaluation, and when performing evaluation on the remaining orders, the vibration stress is still taken as the stress before superposition.

[0050] Another aspect of the present application also provides an electronic device, including a memory, a processor, and a computer program stored in the memory and running on the processor, wherein the processor implements the steps of the anisotropic material blade high-cycle fatigue analysis method when executing the computer program.

[0051] Another aspect of the present application also provides a storage medium, including a stored program, wherein the program controls a device where the storage medium is located to perform the steps of the anisotropic material blade high-cycle fatigue analysis method when the program is running.

[0052] Compared with the prior art, the present application has the following beneficial effects:

[0053] The present application proposes an anisotropic material blade high-cycle fatigue analysis method, device, equipment and medium, and the anisotropic material blade high-cycle fatigue analysis method has the following advantages:

[0054] 1) Compared with the prior art, the combination of crystal direction angles is not fully considered, and dangerous crystal direction angle blades are easily missed. The application considers different crystal direction angles, and the statistics are more comprehensive.

[0055] 2) Compared with the prior art, only the evaluation of the maximum vibration stress of the blade is considered. The application considers the high-cycle fatigue evaluation of all stress points, including the maximum vibration stress point, the maximum steady-state stress point, etc., which is convenient for scientifically finding the more dangerous maximum vibration stress point.

[0056] 3) Compared with the prior art, the vibration stress correction only considers that the maximum vibration stresses of blades with different crystal direction angles are equal, and does not consider the influence of blade frequency change on vibration stress. The application fully considers the correction of vibration stress by blade frequency, which improves the accuracy of vibration stress correction.

[0057] 4) Compared with the prior art, the vibration stress superposition effect is not considered. The application fully considers the vibration stress superposition effect, making the high-cycle fatigue evaluation more scientific.

[0058] In addition to the purposes, features and advantages described above, the application has other purposes, features and advantages. The application will be further described below with reference to the drawings. BRIEF DESCRIPTION OF DRAWINGS

[0059] The drawings incorporated into the specification and forming a part thereof show embodiments consistent with the application and, together with the specification, serve to explain the principles of the application.

[0060] In order to more clearly illustrate the technical solutions in the embodiments of the application or the prior art, the drawings required to be used in the embodiments or prior art description will be briefly introduced below. Obviously, for those skilled in the art, other drawings can also be obtained from these drawings without creative labor.

[0061] Figure 1 is a flowchart of the high-cycle fatigue analysis method of the anisotropic material blade of the preferred embodiment of the application;

[0062] Figure 2 is a schematic diagram of the blade crystal direction angle;

[0063] Figure 3 is a Campbell diagram;

[0064] Figure 4 is a schematic diagram of the high-cycle fatigue analysis device module of the preferred embodiment of the application;

[0065] Figure 5 is a schematic block diagram of the electronic device of the preferred embodiment of the application;

[0066] Figure 6 is an internal structure diagram of a computer device of a preferred embodiment of the present application. DETAILED DESCRIPTION

[0067] It should be understood that the specific embodiments described herein are merely intended to explain the technical solutions of the present application, and are not intended to limit the present application.

[0068] In order to better understand the technical solutions of the present application, the following will be described in detail in combination with the drawings and specific embodiments.

[0069] It should be noted that the execution subject of the present embodiment can be a computing service device with data processing, network communication and program running functions, such as a tablet computer, a personal computer, a mobile phone, etc., or an anisotropic material blade high-cycle fatigue analysis device capable of realizing the above functions. The following will take the anisotropic material blade high-cycle fatigue analysis device as an example to describe the present embodiment and the following embodiments.

[0070] As shown in Figure 1 , the preferred embodiment of the present application provides 1. An anisotropic material blade high-cycle fatigue analysis method, characterized in that it comprises the steps of:

[0071] S1, calculating the vibration mode of the test blade and the conversion blade according to different crystal direction angles by using the finite element method, obtaining the vibration frequency and stress distribution of each order; calculating the strength of the blade by using the finite element method, obtaining the steady stress of the blade under various states;

[0072] S2, paste strain gauges on the blade, obtain stress data by measuring strain during engine operation, obtain the crystal direction angle of the test blade and the conversion blade by crystal direction analysis, perform engine dynamic stress measurement test according to relevant specifications of "Test Point Design of Blade Vibration Stress Measurement Test" and "Technical Requirements of Blade Dynamic Stress Measurement Test", and obtain the actual maximum vibration stress of the test blade;

[0073] S3, according to the strain value measured by the strain gauges on the blade, the vibration stress is converted, and according to the different vibration modes of each order, the maximum displacement of the test blade of each order is converted;

[0074] S4, according to the proportional relationship between the displacement of the blade and the frequency, the maximum displacement of the conversion blade of each order is obtained;

[0075] S5, the vibration stress distribution of the conversion blade is converted, and according to the different vibration modes of each order, the vibration stress distribution of the conversion blade of each order is converted;

[0076] S6, for any two orders of resonance speed, if the condition is met, the vibration stress is superimposed, and the new stress state after superposition is obtained;

[0077] S7, according to the vibration stress and the steady stress value, a GoodMan diagram is drawn, and high-cycle fatigue evaluation is carried out on the test blade and the conversion blade respectively, wherein, when high-cycle fatigue evaluation is carried out on any two orders of vibration stress, the new stress after superposition is used for evaluation, and when evaluation is carried out on the rest of the orders, the vibration stress is still taken before superposition.

[0078] The embodiment provides a high-cycle fatigue analysis method for an anisotropic material blade.

[0079] 1) Compared with the prior art, the combination of the crystal direction angle is not fully considered, and dangerous crystal direction angle blades are easily missed. The embodiment considers different crystal direction angles, and statistics are more comprehensive.

[0080] 2) Compared with the prior art, only the evaluation of the maximum vibration stress of the blade is considered. The high-cycle fatigue evaluation of all stress points is considered in the embodiment, including the maximum vibration stress point, the maximum steady stress point and the like, so that the more dangerous maximum vibration stress point can be found more scientifically.

[0081] 3) Compared with the prior art, the vibration stress correction only considers that the maximum vibration stress of the blade with different crystal direction angles is equal, and the influence of the blade frequency change on the vibration stress is not considered. The embodiment fully considers the correction of the vibration stress by the blade frequency, and the accuracy of the vibration stress correction is improved.

[0082] 4) Compared with the prior art, the vibration stress superposition effect is not considered. The embodiment fully considers the vibration stress superposition effect, so that the high-cycle fatigue evaluation is more scientific.

[0083] Preferably, in step S1, the finite element method is used to calculate the vibration mode of the conversion blade according to different crystal direction angles, and each order vibration frequency and stress distribution are obtained, and the step specifically includes the following steps.

[0084] S100, the crystal main axis included angle range (-θ°~θ°) of the conversion blade

[001] direction is determined, and the crystal main axis included angle range of the

[010] direction and the

[011] direction is (-180°~180°).

[0085] S101, a plurality of included angle combinations are selected from the crystal main axis included angle ranges of the three directions to obtain a plurality of groups of included angle combinations, and an included angle combination matrix is formed, for example:

[0086] The crystal main axis of the

[001] direction considers five included angles: (-θ°, -0.5θ°, 0°, 0.5θ°, θ°).

[0087] The crystal main axis of the

[010] direction considers seven included angles: (-180°, -120°, -60°, 0°, 60°, 120°, 180°).

[0088]

[011] The crystal principal axis in the direction is considered to have 7 included angles: (-180°, -120°, -60°, 0°, 60°, 120°, 180°);

[0089] This results in a total of 245 combinations of included angles, which are 5×7×7.

[0090] S102. Modal analysis was performed on the converted blades according to different crystal orientation angles using the finite element method (in commercial software), resulting in 245 sets of vibration frequency calculation results. The vibration frequencies and stress distributions of each order of the converted blades were obtained.

[0091] This embodiment considers the influence of the angle between the crystal coordinate axis and the overall coordinate axis of the model on the vibration stress. The analysis needs to cover all possible crystal orientation angles of the actual machined parts. Generally, during acceptance, only the range of the crystal principal axis angle in the

[001] direction is controlled. Compared with the existing scheme, which does not fully consider the combination of crystal orientation angles and is prone to missing dangerous crystal orientation angle blades, the statistics are more comprehensive.

[0092] Preferably, in step S1, the vibration modes of the test blade are calculated using the finite element method based on different crystal orientation angles to obtain the vibration frequencies and stress distributions of each order. Specifically, this includes the following steps:

[0093] S110, such as Figure 2 As shown, crystal orientation angle measurements were performed on a test blade with multiple strain gauges attached. Taking three strain gauges as an example, the crystal orientation angle data of the three sets of strain gauges were obtained as follows: ), ( ), ( Finite element analysis was performed based on three sets of crystal orientation angle data to obtain three sets of frequency calculation results, and the vibration frequencies and stress distributions of each order of the test blades were obtained.

[0094] This embodiment performs finite element calculations based on three sets of crystal orientation angle data to obtain three sets of frequency calculation results, thereby obtaining the vibration frequencies and stress distributions of each order of the test blades. The advantages include obtaining the average results of multiple test data and avoiding the test errors of a single test data.

[0095] Preferably, in step S3, the strain values ​​measured by the strain gauges attached to the blade are converted into vibration stress, and the maximum displacement of the test blade at each order is calculated according to the different mode shapes:

[0096] ;

[0097] In the formula, σ represents the stress value obtained from the test of the test blade; Indicates the test blade number iThe ratio of the maximum displacement of the mode shape to the test stress value is obtained by modal calculation of the test blade; The maximum displacement of the mode shape of the test blade is represented by i The maximum displacement of the mode shape of the test blade is represented by

[0098] Preferably, in step S4, the maximum displacement of the converted blade of each order is obtained according to the proportional relationship between the blade displacement and the frequency, and specifically is:

[0099]

[0100] In the formula, The maximum displacement of the mode shape of the test blade is represented by i The frequency of the converted blade of the order is obtained by modal calculation of the converted blade; The frequency of the test blade of the order is obtained by modal calculation of the test blade; i The maximum displacement of the mode shape of the test blade is represented by The maximum displacement of the mode shape of the test blade is represented by i The maximum displacement of the mode shape of the test blade is represented by

[0101] If there are multiple test blades, the maximum displacement of the converted blade of each order is calculated for each test blade, and the average value is taken as the final maximum displacement of the converted blade of each order, thereby improving the accuracy of the maximum displacement of the converted blade of each order.

[0102] Preferably, in step S5, the vibration stress distribution of the converted blade is obtained by referring to the test blade and converting the vibration stress distribution of the converted blade of each order according to different mode shapes, and specifically is:

[0103]

[0104] In the formula, The stress value of the converted blade is obtained by test, and the stress calculation formula of only one node is listed, and the calculation method of all nodes is the same (about 10,000 nodes for one blade); The maximum displacement of the mode shape of the test blade is represented by i The maximum displacement of the mode shape of the test blade is represented by The maximum displacement of the mode shape of the test blade is represented by i The ratio of the maximum displacement of the mode shape to the test stress value is obtained by modal calculation of the test blade.

[0105] Preferably, according to the basic theory of blade resonance analysis, the intersection of the diagonal line and the horizontal line is the resonance speed, and from Figure 3 It can be seen that there may be overlapping resonance speeds, for example, the intersection of K1 and the second order mode, and the intersection of K2 and the first order mode; the resonance speeds corresponding to the two intersections ​​​Overlap can occur, so the overlap effect that can occur should be fully considered when analyzing the high cycle fatigue of the blade, therefore, the step S6 specifically comprises the steps of:

[0106] S61, for any two order resonance rotating speed 、 , , judge whether the condition is met:

[0107] ;

[0108] S62, if yes, stress superposition is carried out, the method of stress superposition is as follows:

[0109] The first stress state is:

[0110] ;

[0111] Among them, σ x1 、 σ y1 、 σ z1 respectively represent the x, y, z direction normal stress under the first stress state, τ x1 、 τ y1 、 τ z1 respectively represent the x, y, z direction shear stress under the first stress state;

[0112] The second stress state is:

[0113] ;

[0114] Among them, σ x2 、 σ y2 、 σ z2 respectively represent the x, y, z direction normal stress under the second stress state, τ x2 、 τ y2 、 τ z2 respectively represent the x, y, z direction shear stress under the second stress state;

[0115] The new stress state after superposition is:

[0116] .

[0117] The above-mentioned first i order and the second jWhen the order vibration stress is used for high cycle fatigue assessment, the vibration stress should be the new stress after superposition. The vibration stress is still the previous stress when the rest of the order is assessed. Compared with the existing scheme, the vibration stress superposition effect is not considered. The embodiment fully considers the vibration stress superposition effect, so that the high cycle fatigue assessment is more scientific.

[0118] The method of the above embodiment has been successfully applied to the AES100 engine, providing important technical support for the smooth development of the AES100 engine. After applying the method, the AES100 engine blade has passed tens of engine bench tests for nearly 16000 hours, single engine accelerated endurance test for 5000 hours, engine whole machine verification under high altitude table, field flight test, and more than 200 hours of air flight test. The verification results show that after using the scheme to assess the high cycle fatigue of the blade, the blade can work safely and stably.

[0119] As shown in Figure 4 Another preferred embodiment of the present application also provides a high cycle fatigue analysis device for an anisotropic material blade, comprising:

[0120] A blade strength vibration calculation module is configured to calculate the vibration mode of a test blade and a conversion blade according to different crystal orientation angles by using a finite element method, to obtain vibration frequencies and stress distribution of each order; and calculate the strength of the blade by using the finite element method to obtain the steady stress of the blade under various states.

[0121] A dynamic stress measurement test module is configured to paste strain gauges on the blade, to obtain stress data by measuring the strain during engine operation, to obtain the crystal orientation angle of the test blade and the conversion blade by crystal orientation analysis, to perform engine dynamic stress measurement test according to relevant specifications of "Blade Vibration Stress Measurement Test Point Design" and "Blade Dynamic Stress Measurement Test Technical Requirements", and to obtain the actual maximum vibration stress of the test blade.

[0122] A test blade maximum displacement calculation module is configured to convert the strain measured by the strain gauges on the blade into vibration stress, to obtain the maximum displacement of each order of the test blade according to different vibration modes.

[0123] A conversion blade maximum displacement module is configured to obtain the maximum displacement of each order of the conversion blade according to the proportional relationship between the displacement of the blade and the frequency.

[0124] A conversion blade vibration stress distribution calculation module is configured to convert the vibration stress distribution of the conversion blade, to refer to the test blade, and to convert the vibration stress distribution of each order of the conversion blade according to different vibration modes.

[0125] A vibration stress superposition module is configured to superimpose the vibration stress of any two orders of resonance speed, such as the condition, to obtain the new stress state after superposition.

[0126] The blade high-cycle fatigue evaluation module is used for drawing a GoodMan diagram according to the vibration stress and the steady-state stress value, and performing high-cycle fatigue evaluation on the test blade and the conversion blade respectively, wherein when high-cycle fatigue evaluation is performed on any two orders of vibration stress, the new stress after superposition is used for evaluation, and when evaluation is performed on the remaining orders, the vibration stress is still taken as the stress before superposition.

[0127] The blade high-cycle fatigue analysis device provided by the embodiment adopts the blade high-cycle fatigue analysis method of the above embodiment, and solves the technical problem of the existing high-cycle fatigue evaluation method that the evaluation result is not scientific, accurate and reliable. Compared with the prior art, the blade high-cycle fatigue analysis device provided by the present application has the same beneficial effects as the blade high-cycle fatigue analysis method provided by the above embodiment, and other technical features in the blade high-cycle fatigue analysis device are the same as the features disclosed in the above embodiment method, which will not be repeated here.

[0128] As shown in Figure 5 The preferred embodiment of the present application further provides an electronic device, which includes a memory, a processor and a computer program stored in the memory and executable on the processor, and the processor implements the steps of the blade high-cycle fatigue analysis method of the above embodiment when executing the computer program.

[0129] The electronic device provided by the present application adopts the blade high-cycle fatigue analysis method of the above embodiment, and solves the technical problem of the existing high-cycle fatigue evaluation method that the evaluation result is not scientific, accurate and reliable. Compared with the prior art, the electronic device provided by the present application has the same beneficial effects as the blade high-cycle fatigue analysis method provided by the above embodiment, and other technical features in the electronic device are the same as the features disclosed in the above embodiment method, which will not be repeated here.

[0130] As shown in Figure 6 The preferred embodiment of the present application further provides a computer device, which can be a terminal or a living body detection server, and the internal structure diagram thereof can be as shown in Figure 6As shown in the figure. The computer device includes a processor, a memory and a network interface connected through a system bus. Among them, the processor of the computer device is used to provide computing and control capabilities. The memory of the computer device includes a non-volatile storage medium, an internal memory. The non-volatile storage medium stores an operating system and a computer program. The internal memory provides an environment for the operating system and the computer program in the non-volatile storage medium to run. The network interface of the computer device is used to communicate with other computer devices outside through network connection. The computer program is executed by the processor to implement the steps of the anisotropic material blade high-cycle fatigue analysis method described above.

[0131] Those skilled in the art can understand that, Figure 6 The structure shown in the figure is only a block diagram of part of the structure related to the scheme of the present application, and does not constitute a limitation on the computer device to which the scheme of the present application is applied. The specific computer device can include more or fewer components than those shown in the figure, or combine certain components, or have a different component arrangement.

[0132] The computer device provided by the application adopts the anisotropic material blade high-cycle fatigue analysis method in the above-mentioned embodiments to solve the technical problems of the scientificity, accuracy and reliability of the evaluation results of the existing high-cycle fatigue evaluation method. Compared with the prior art, the computer device provided by the application has the same beneficial effects as the anisotropic material blade high-cycle fatigue analysis method provided by the above-mentioned embodiments, and the other technical features in the electronic device are the same as the features disclosed in the above-mentioned embodiment method, which will not be repeated here.

[0133] The preferred embodiments of the present application also provide a storage medium, which includes a stored program, which controls the device where the storage medium is located to execute the steps of the anisotropic material blade high-cycle fatigue analysis method in the above-mentioned embodiments when the program runs.

[0134] It should be noted that the steps shown in the flowchart of the figure can be executed in a computer system such as a set of computer executable instructions, and although the logical order is shown in the flowchart, in some cases, the steps shown or described herein can be executed in an order different from that shown.

[0135] If the functions of the method in the embodiments are implemented in the form of software function units and sold or used as independent products, the software function units can be stored in one or more computer readable storage media. Based on such an understanding, the part of the prior art or the part of the technical solutions of the embodiments of the present application that make contributions to the prior art can be embodied in the form of a software product, which is stored in a storage medium and includes several instructions for causing a computer (which can be a personal computer, a server, a mobile computing device, or a network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present application. The aforementioned storage medium includes: U disk, mobile hard disk, read-only memory (ROM, Read-Only Memory), random access memory (RAM, Random Access Memory), magnetic disk or optical disk, and various media that can store program codes.

[0136] Those skilled in the art should understand that the embodiments of the present application can be provided as a method, a system, or a computer program product. Therefore, the present application can take the form of an entirely hardware embodiment, an entirely software embodiment, or an embodiment combining software and hardware aspects. Moreover, the present application can take the form of a computer program product implemented on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROMs, optical storage, etc.) containing computer-usable program code. The solutions in the embodiments of the present application can be implemented in various computer languages, such as the object-oriented programming language C++ and the embedded programming language C.

[0137] The present application is described with reference to flowcharts and / or block diagrams according to the methods, devices (systems), and computer program products of the embodiments of the present application. It should be understood that each flow and / or block in the flowcharts and / or block diagrams, and the combination of flows and / or blocks in the flowcharts and / or block diagrams can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing device to produce a machine, so that the instructions executed by the processor of the computer or other programmable data processing device produce a device that implements the functions specified in the flowcharts and / or block diagrams. Figure 1 The functions specified in one or more flows and / or blocks Figure 1 The functions specified in one or more flows and / or blocks

[0138] These computer program instructions can also be stored in a computer readable storage medium that can direct the computer or other programmable data processing device to work in a specific manner, so that the instructions stored in the computer readable storage medium produce a manufactured product including instruction devices that implement the functions specified in the flowcharts and / or block diagrams. Figure 1 The functions specified in one or more flows and / or blocks Figure 1 The functions specified in one or more flows and / or blocks

[0139] These computer program instructions can also be loaded into a computer or other programmable data processing devices, so that a series of operational steps are performed on the computer or other programmable devices to generate computer-implemented processes, so that the instructions executed on the computer or other programmable devices provide a process for implementing the functions specified in the flowchart Figure 1 one flow or multiple flows and / or the functions specified in one block or multiple blocks. Figure 1 one flow or multiple flows and / or the functions specified in one block or multiple blocks.

[0140] The application also provides a computer program product comprising a computer program which, when executed by a processor, implements the steps of the anisotropic material blade high-cycle fatigue analysis method as described above.

[0141] The computer program product provided by the application solves the technical problem of the lack of scientificity, accuracy and reliability of the evaluation results of the existing high-cycle fatigue evaluation method. Compared with the prior art, the beneficial effects of the computer program product provided by the application are the same as those of the anisotropic material blade high-cycle fatigue analysis method provided by the above-mentioned embodiments, and will not be repeated here.

[0142] Although the preferred embodiments of the application have been described, those skilled in the art can make additional changes and modifications to the embodiments once they know the basic inventive concept. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments and all changes and modifications falling within the scope of the application.

[0143] Obviously, those skilled in the art can make various modifications and variations to the application without departing from the spirit and scope of the application. Thus, if these modifications and variations of the application fall within the scope of the claims of the application and their equivalent technologies, the application also intends to include these modifications and variations.

Claims

1. A method for high-cycle fatigue analysis of anisotropic material blades, characterized in that, Including the following steps: S1. Using the finite element method (FEM) to calculate the vibration modes of the test blade and the converted blade based on different crystal orientation angles, the vibration frequencies and stress distributions of each order are obtained; the strength of the blade is calculated using the FEM to obtain the steady-state stress of the blade under various conditions; the vibration modes of the converted blade are calculated using the FEM based on different crystal orientation angles, the vibration frequencies and stress distributions of each order are obtained, specifically including the following steps: S100. Determine the crystal principal axis angle range (-θ°~θ°) in the [001] direction of the conversion blade, and the crystal principal axis angle range (-180°~180°) in the [010] and [011] directions. S101. Select several angles from the range of the crystal principal axis angles in three directions to form various angle combinations, and obtain several sets of angle combinations to form an angle combination matrix; S102. Using the finite element method, modal analysis was carried out on the equivalent blade according to different crystal orientation angles to obtain the corresponding set of vibration frequency calculation results, and to obtain the vibration frequency and stress distribution of each order of the equivalent blade. S2. Strain gauges are attached to the blades, and stress data is obtained by measuring the strain during engine operation. The test blade is obtained through crystal orientation analysis, and the crystal orientation angle of the blade is calculated. The engine dynamic stress measurement test is carried out according to the relevant specifications of "Blade Vibration Stress Measurement Test Measurement Point Design" and "Blade Dynamic Stress Measurement Test Technical Requirements" to obtain the actual maximum vibration stress of the test blade. S3. Based on the strain values ​​measured by the strain gauges attached to the blade, convert them into vibration stress. Based on the different vibration modes of each order, calculate the maximum displacement of the test blade at each order. S4. Based on the proportional relationship between blade displacement and frequency, the maximum displacement of the blades for each order is obtained. S5. Calculate the vibration stress distribution of the blade. Referring to the test blade, calculate the vibration stress distribution of each order of the blade according to the different vibration modes. S6. For any two resonant rotational speeds, if the condition is met, the vibration stress is superimposed to obtain a new stress state after superposition. The specific steps include: S61, For any two-order resonance speed , , Determine whether the conditions are met: ； S62. If so, then stress superposition is performed. The method for stress superposition is as follows: The first stress state is: ； in, σ x1 , σ y1 , σ z1 These represent the normal stresses in the x, y, and z directions under the first stress state, respectively. τ x1 , τ y1 , τ z1 These represent the shear stresses in the x, y, and z directions respectively under the first stress state; The second stress state is: ； in, σ x2 , σ y2 , σ z2 These represent the normal stresses in the x, y, and z directions under the second stress state, respectively. τ x2 , τ y2 , τ z2 These represent the shear stresses in the x, y, and z directions respectively under the second stress state; The new stress state after superposition is: ； S7. Based on the vibration stress and steady-state stress values, draw a GoodMan diagram and conduct high-cycle fatigue assessments on the test blade and the equivalent blade respectively. When conducting high-cycle fatigue assessments for any two orders of vibration stress, the new stress after superposition is used for assessment. For assessments of other orders, the vibration stress is still taken as the stress before superposition.

2. The method for high-cycle fatigue analysis of anisotropic material blades according to claim 1, characterized in that, In step S1, the vibration modes of the test blade are calculated using the finite element method based on different crystal orientation angles to obtain the vibration frequencies and stress distributions of each order. The specific steps include: S110. Perform crystal orientation angle measurements on the test blade with N strain gauges attached, obtain N sets of crystal orientation angle data for the strain gauges, perform finite element calculations based on the N sets of crystal orientation angle data, obtain N sets of frequency calculation results, and obtain the vibration frequencies and stress distributions of each order of the N sets of test blades.

3. The method for high-cycle fatigue analysis of anisotropic material blades according to claim 1, characterized in that, In step S3, the strain values ​​measured by the strain gauges attached to the blade are converted into vibration stress. Based on the different mode shapes of each order, the maximum displacement of the test blade at each order is calculated as follows: ； In the formula, σ represents the stress value obtained from the test of the test blade; Indicates the test blade number i The ratio of the maximum displacement of the vibration mode to the test stress value is obtained through modal calculation of the test blade; Indicates the test blade number i Maximum displacement of the mode shape.

4. The method for high-cycle fatigue analysis of anisotropic material blades according to claim 3, characterized in that, In step S4, based on the proportional relationship between blade displacement and frequency, the maximum displacement of the converted blades for each order is obtained as follows: ； In the formula, Indicates the conversion of the first blade i The first frequency is obtained by modal calculation of the blade; Indicates the test blade number i The first frequency is obtained through modal calculations of the test blade; Indicates the conversion of the first blade i Maximum displacement value of the mode shape.

5. The method for high-cycle fatigue analysis of anisotropic material blades according to claim 1, characterized in that, In step S5, the vibration stress distribution of the blade is calculated. Referring to the test blade, the vibration stress distribution of each order of the blade is calculated according to the different vibration modes. Specifically: ； In the formula, This represents the stress value obtained from the blade test. Indicates the conversion of the first blade i Maximum displacement of the mode shape, Indicates the conversion of the first blade i The ratio of the maximum displacement of the mode shape to the test stress value is obtained by modal calculation of the blade.

6. A high-cycle fatigue analysis device for anisotropic material blades, characterized in that, include: The blade strength vibration calculation module is used to calculate the vibration modes of the test blade and the converted blade based on different crystal orientation angles using the finite element method (FEM), obtaining the vibration frequencies and stress distributions of each order; to calculate the blade strength using the FEM, obtaining the steady-state stress of the blade under various conditions; and to calculate the vibration modes of the converted blade based on different crystal orientation angles using the FEM, obtaining the vibration frequencies and stress distributions of each order. Specifically, it is used for: The range of the crystal principal axis included angle in the [001] direction of the transformation blade is determined to be (-θ°~θ°), and the range of the crystal principal axis included angle in the [010] direction and the [011] direction is (-180°~180°). Several angles are selected from the range of the principal axes of the crystal in three directions to form various angle combinations, resulting in several sets of angle combinations, forming an angle combination matrix; The finite element method was used to perform modal analysis on the equivalent blade according to different crystal orientation angles, and the corresponding set of vibration frequency calculation results were obtained. The vibration frequencies and stress distribution of each order of the equivalent blade were obtained. The dynamic stress measurement test module is used to attach strain gauges to the blades, obtain stress data by measuring the strain during engine operation, obtain the test blade through crystal orientation analysis, calculate the crystal orientation angle of the blade, and conduct engine dynamic stress measurement tests according to the relevant specifications of "Blade Vibration Stress Measurement Test Measurement Point Design" and "Blade Dynamic Stress Measurement Test Technical Requirements" to obtain the actual maximum vibration stress of the test blade. The test blade maximum displacement calculation module is used to convert the strain values ​​measured by the strain gauges attached to the blade into vibration stress, and to calculate the maximum displacement of the test blade at each order according to different vibration modes. The maximum displacement module for the blade is used to obtain the maximum displacement of the blade for each order based on the ratio of blade displacement to frequency. The blade vibration stress distribution calculation module is used to calculate the vibration stress distribution of blades. Referring to the test blade, it calculates the vibration stress distribution of each order of the blade according to different vibration modes. The vibration stress superposition module is used to superimpose vibration stresses for any two resonant rotational speeds if certain conditions are met, resulting in a new stress state after superposition. Specifically, it is used for: For any two-order resonant rotational speed , , Determine whether the conditions are met: ； If so, stress superposition is performed, and the method for stress superposition is as follows: The first stress state is: ； in, σ x1 , σ y1 , σ z1 These represent the normal stresses in the x, y, and z directions under the first stress state, respectively. τ x1 , τ y1 , τ z1 These represent the shear stresses in the x, y, and z directions respectively under the first stress state; The second stress state is: ； in, σ x2 , σ y2 , σ z2 These represent the normal stresses in the x, y, and z directions under the second stress state, respectively. τ x2 , τ y2 , τ z2 These represent the shear stresses in the x, y, and z directions respectively under the second stress state; The new stress state after superposition is: ； The blade high-cycle fatigue assessment module is used to draw GoodMan diagrams based on vibration stress and steady-state stress values, and to conduct high-cycle fatigue assessments on the test blade and the equivalent blade respectively. When assessing high-cycle fatigue for any two orders of vibration stress, the new stress after superposition is used for assessment, while for other orders of assessment, the vibration stress is still taken as the stress before superposition.

7. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the high-cycle fatigue analysis method for anisotropic material blades as described in any one of claims 1 to 5.

8. A storage medium comprising a stored program, characterized in that, When the program is running, it controls the device containing the storage medium to perform the steps of the high-cycle fatigue analysis method for anisotropic material blades as described in any one of claims 1 to 5.

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