Blade Goodman curve correction method considering crystal orientation and multi-axis stress state

Abstract

The invention relates to a blade Goodman curve correction method, device, equipment and medium considering crystal orientation and a multi-axis stress state, and relates to the technical field of mechanical engineering.The method comprises the steps that a blade Goodman curve is determined based on a correction coefficient obtained through a blade vibration fatigue test and a blade material Goodman curve; static stress and modal stress of the blade under different rotating speeds and maximum displacement and vibration frequency of a blade body under different modals are obtained; calculating allowable vibration stress according to the blade Goldman curve and the static stress, and determining the allowable vibration stress of each point on the blade at different rotating speeds; determining a dynamic stress reserve coefficient corresponding to each point on the blade; according to the circumferential displacement of a sensor preset on the blade at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency, limit value calculation is conducted, and the blade amplitude limit value corresponding to the blade is determined. The accuracy of the blade amplitude limit value in the blade stress state monitoring process can be improved.

Description

Background Art

[0002] As a key component of an aero-turbine engine, during actual operation, the blade is prone to vibration, which may cause blade damage. Vibration stress is an important basis for evaluating the vibration tolerance of the blade and predicting the blade life.

[0003] In related technologies, a non-contact measurement method such as blade timing can be used to monitor the vibration state of the blade. This method analyzes the vibration of the blade by measuring the time when the rotating blade reaches the sensor and the lead and lag of the theoretical arrival time by the sensor installed on the solid casing. However, during the monitoring of the stress state of the blade, when the vibration stress exceeds the limit, it is necessary to make a judgment in combination with the design and formulate measures to prevent the blade crack initiation and propagation caused by the excessive vibration stress and the resulting catastrophic consequences. Therefore, when monitoring the stress state of the blade, it is necessary to determine the blade amplitude limit value, which is used to reflect the state of the most dangerous point on the blade to ensure the safe operation of the test piece. However, in related technologies, there is still room for improvement in the method for determining the blade amplitude limit value during the monitoring of the stress state of the blade. Summary of the Invention

[0004] The purpose of the present disclosure is to provide a method, device, electronic device, and computer-readable storage medium for correcting the Goodman curve of a blade considering crystal orientation and multi-axial stress state. Based on the corrected Goodman curve of the blade, as well as the results of static strength analysis and modal analysis, the blade amplitude limit value can be determined, improving the accuracy of the blade amplitude limit value during the monitoring of the blade stress state.

[0005] Other features and advantages of the present disclosure will become apparent through the following detailed description, or be learned in part through the practice of the present disclosure.

[0006] According to the first aspect of the present disclosure, there is provided a method for correcting the Goodman curve of a blade considering crystal orientation and multi-axial stress state, including: determining the Goodman curve of the blade based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material; performing static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes; calculating the allowable vibration stress according to the Goodman curve of the blade and the static stress to determine the allowable vibration stress of each point on the blade at different rotational speeds; determining the dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency; performing limit value calculation according to the circumferential displacement at the corresponding position on the blade by the sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, and determining the blade amplitude limit value corresponding to the blade.

[0007] Optionally, based on the correction factor obtained from the blade vibration fatigue test and the Goodman curve of the blade material, determine the blade Goodman curve, including: obtaining the correction factor by querying the vibration fatigue test database; correcting the ordinate and abscissa of the blade material Goodman curve based on the correction factor to obtain the blade Goodman curve, and configuring the safety factor corresponding to the blade Goodman curve.

[0008] Optionally, perform static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body under different modes, including: establishing the blade simulation analysis model based on the pre-acquired blade geometric model, load information, and blade material parameters; performing static strength analysis on the blade simulation analysis model at different rotational speeds to obtain the static stress of the blade at different rotational speeds; performing modal analysis on the blade simulation analysis model at different rotational speeds to obtain the modal stress of the blade at different rotational speeds, the maximum displacement of the blade body under different modes, and the vibration frequency.

[0009] Optionally, based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency, determine the dynamic stress reserve coefficient corresponding to each point on the blade, including: determining the modal stress of each point on the blade at unit displacement and frequency based on the modal stress, maximum displacement of the blade body, and vibration frequency; determining the dynamic stress reserve coefficient corresponding to each point on the blade based on the ratio of the allowable vibration stress to the modal stress of each point on the blade at unit displacement and frequency.

[0010] Optionally, perform limit value calculation based on the circumferential displacement at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency at the position of the sensor preset on the blade to determine the blade amplitude limit value corresponding to the blade, including: obtaining the sensor position on the blade; determining the circumferential displacement at the corresponding position on the blade through modal analysis; determining the limit value and alarm value corresponding to the blade based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, and using the limit value and alarm value as the blade amplitude limit value.

[0011] Optionally, based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, determine the limit value and alarm value corresponding to the blade, including: performing limit value calculation based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency to determine the limit value corresponding to the blade; determining the alarm value corresponding to the blade based on the product of the limit value and the preset alarm coefficient.

[0012] Optionally, the above-mentioned method for correcting the blade Goodman curve considering crystal orientation and multiaxial stress state further includes: determining the risk level of each point on the blade based on the dynamic stress reserve coefficient; and taking the point with the minimum dynamic stress reserve coefficient as the most dangerous point of the blade at different rotational speeds.

[0013] According to a second aspect of the present disclosure, there is provided a device for correcting the blade Goodman curve considering crystal orientation and multiaxial stress state, including: a curve determination module for determining the blade Goodman curve based on the correction coefficient obtained from the blade vibration fatigue test and the blade material Goodman curve; a model analysis module for performing static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes; a allowable stress determination module for calculating the allowable vibration stress based on the blade Goodman curve and the static stress to determine the allowable vibration stress of each point on the blade at different rotational speeds; a reserve coefficient determination module for determining the dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency; and a limit value determination module for calculating the limit value based on the circumferential displacement at the corresponding position on the blade by a sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency to determine the blade amplitude limit value corresponding to the blade.

[0014] According to a third aspect of the present disclosure, there is provided an electronic device, including: a processor; and a memory for storing executable instructions of the processor; wherein the processor is configured to execute any one of the above methods and its possible implementations by executing the executable instructions.

[0015] According to a fourth aspect of the present disclosure, there is provided a computer-readable storage medium having a computer program stored thereon, and the computer program, when executed by a processor, implements any one of the above methods and its possible implementations.

[0016] In the technical solution provided by the embodiments of the present disclosure, on the one hand, based on the correction coefficient obtained from the blade vibration fatigue test and the blade material Goodman curve, the blade Goodman curve is determined, and more accurate blade vibration fatigue characteristics can be obtained; on the other hand, static strength analysis and modal analysis are performed on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes. Furthermore, based on the circumferential displacement at the corresponding position on the blade by a sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, the limit value is calculated to determine the blade amplitude limit value corresponding to the blade, improving the accuracy of the blade amplitude limit value in the process of monitoring the blade stress state and ensuring the safe operation of the blade test piece.

[0017] It should be understood that the above general description and the following detailed description are merely exemplary and explanatory, and do not limit the present disclosure. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] The accompanying drawings herein are incorporated into the specification and constitute a part of this specification, showing embodiments consistent with the present disclosure, and are used together with the specification to explain the principles of the present disclosure. Obviously, the accompanying drawings in the following description are only some embodiments of the present disclosure, and those of ordinary skill in the art can obtain other drawings based on these drawings without creative efforts.

[0019] Figure 1 Schematically showing a flowchart of a method for correcting the Goodman curve of a blade considering only crystal orientation and multi-axial stress state according to an embodiment of the present disclosure.

[0020] Figure 2 Schematically showing a flowchart of performing static strength analysis and modal analysis on a blade simulation analysis model according to an embodiment of the present disclosure.

[0021] Figure 3 Schematically showing a flowchart of determining the blade amplitude limit value corresponding to a blade according to an embodiment of the present disclosure.

[0022] Figure 4 Schematically showing a reference diagram for determining the limit value and alarm value corresponding to a blade according to an embodiment of the present disclosure.

[0023] Figure 5 Schematically showing a flowchart of another method for correcting the Goodman curve of a blade considering crystal orientation and multi-axial stress state according to an embodiment of the present disclosure.

[0024] Figure 6 Schematically showing a block diagram of a device for correcting the Goodman curve of a blade considering crystal orientation and multi-axial stress state according to an embodiment of the present disclosure.

[0025] Figure 7 Schematically showing a block diagram of an electronic device according to an embodiment of the present disclosure. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0026] Example embodiments will now be described more fully with reference to the accompanying drawings. However, the example embodiments can be implemented in various forms and should not be construed as limited to the examples set forth herein; rather, these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of the example embodiments to those skilled in the art. The features, structures, or characteristics described may be combined in any suitable manner in one or more embodiments. In the following description, numerous specific details are provided to give a thorough understanding of the embodiments of the present disclosure. However, those skilled in the art will realize that the technical solutions of the present disclosure can be practiced without one or more of the specific details, or other methods, components, devices, steps, etc. may be used. In other instances, well-known technical solutions are not shown or described in detail to avoid obscuring aspects of the present disclosure.

[0027] In addition, the accompanying drawings are only schematic illustrations of the present disclosure and are not necessarily drawn to scale. The same reference numerals in the drawings denote the same or similar parts, and thus repeated descriptions thereof will be omitted. Some of the block diagrams shown in the drawings are functional entities and do not necessarily correspond to physically or logically independent entities. These functional entities can be implemented in software form, or in one or more hardware modules or integrated circuits, or in different networks and / or processor devices and / or microcontroller devices.

[0028] During the operation of an aero-turbine engine, the blades are often affected by vibrations, which may cause blade damage. Statistical data shows that most blade damage accidents are caused by vibrations. Vibration stress is an important basis for evaluating the vibration tolerance of blades and predicting the blade life. To evaluate the bearing capacity of blades and estimate their service life, it is necessary to monitor their vibration stress. Generally, the method adopted in the field of blade vibration measurement is to monitor the state of rotating blades by pasting resistance strain gauges. This method can measure the dynamic stress and vibration frequency of the blades during vibration, and then evaluate the operating condition of the blades. However, since rotating blades are usually in complex environments such as high temperature, high pressure, impact loads, and high rotational speeds, it is difficult to ensure the reliability of measurement using resistance strain gauges, and the situation of patch signal failure is likely to occur.

[0029] Therefore, non-contact blade vibration monitoring technology exhibits its unique advantages in many cases. Currently, the widely used non-contact measurement method is the Blade Tip Timing (BTT) method. This method measures the difference (advance or lag) between the time when the rotating blade reaches the sensor and the theoretical arrival time by installing sensors on the solid casing, thereby analyzing the vibration condition of the blade. During the aero-engine test process, in order to ensure the safe operation of the test piece, real-time monitoring of the blade vibration stress is crucial. This helps to identify and judge whether the vibration stress exceeds the safety limit. Once it is found that the vibration stress exceeds the limit, it is necessary to conduct in-depth analysis in combination with the design and take corresponding measures to prevent the blade from cracking and further spreading, thereby avoiding possible serious consequences.

[0030] When monitoring the blade vibration state by the blade timing method, it is crucial to determine the blade amplitude limit value. This includes evaluating the danger level of each point of the blade and setting the blade amplitude limit value (including the alarm value and the limit value) to reflect the state of the most dangerous point on the blade and ensure the safe operation of the blade test piece. However, in the related technology, there is still room for improvement in the method for determining the blade amplitude limit value when monitoring the stress state of the blade. Therefore, in some embodiments, a method for correcting the blade Goodman curve considering crystal orientation and multiaxial stress state is provided. The blade amplitude limit value can be determined based on the corrected blade Goodman curve, as well as the results of static strength analysis and modal analysis, so as to improve the accuracy of the blade amplitude limit value in the blade stress state monitoring process. Refer to Figure 1 As shown in, the method for correcting the blade Goodman curve considering crystal orientation and multiaxial stress state may specifically include the following steps:

[0031] Step S110, determine the blade Goodman curve based on the correction coefficient obtained from the blade vibration fatigue test and the blade material Goodman curve;

[0032] Step S120, perform static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes;

[0033] Step S130, calculate the allowable vibration stress according to the blade Goodman curve and the static stress, and determine the allowable vibration stress of each point on the blade at different rotational speeds;

[0034] Step S140, determine the dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency;

[0035] Step S150: Calculate the limit value based on the circumferential displacement at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency of the blade preset on the blade, and determine the blade amplitude limit value corresponding to the blade.

[0036] In the technical solution provided by the embodiments of the present disclosure, on the one hand, based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material, the blade Goodman curve is determined, and more accurate blade vibration fatigue characteristics can be obtained; on the other hand, static strength analysis and modal analysis are performed on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes. Furthermore, based on the circumferential displacement at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency of the blade preset on the blade, the limit value is calculated to determine the blade amplitude limit value corresponding to the blade, improving the accuracy of the blade amplitude limit value in the blade stress state monitoring process and ensuring the safe operation of the blade test piece.

[0037] Next, with reference to Figure 1 shown in, the above steps will be described in more detail.

[0038] In step S110, the blade Goodman curve is determined based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material.

[0039] Among them, the Goodman curve can represent the relationship curve between the mean stress and the maximum and minimum stresses of components subjected to alternating stresses under the condition of equal life. The Goodman curve of the blade material can represent the Goodman curve corresponding to the material of the blade structure. The blade Goodman curve can be obtained by correcting the Goodman curve corresponding to the material of the blade structure with the correction coefficient, thereby improving the representativeness of the blade Goodman curve and enabling more accurate blade vibration fatigue characteristics to be obtained.

[0040] In addition, the blade vibration fatigue test can represent a method for testing the fatigue performance of the blade under vibration conditions. By simulating the vibration environment of the blade under actual working conditions and applying cyclic stress or alternating load to the blade, the fatigue performance and life of the blade can be detected, and correction coefficients such as the size, forging, machining, and surface treatment of the blade can be obtained.

[0041] In some embodiments, determining the blade Goodman curve based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material may specifically include the following steps: obtaining the correction coefficient by querying the vibration fatigue test database; correcting the ordinate and abscissa of the Goodman curve of the blade material based on the correction coefficient to obtain the blade Goodman curve, and configuring the safety factor corresponding to the blade Goodman curve.

[0042] Among them, the vibration fatigue test database can represent the relevant data of the vibration characteristics and fatigue performance of various materials. By querying the fatigue test database, the fatigue limit and tensile limit of the material used to construct the blade can be obtained, as well as the correction coefficients of the material used to construct the blade, such as the correction coefficients for the size of the blade, forging machining, and surface treatment. Among them, the size correction coefficient is related to the size of the blade, the forging machining correction coefficient is related to the forming process of the blade, and the surface treatment correction coefficient is related to the surface treatment of the blade. Exemplarily, the size correction coefficient can be 0.1, the forging machining correction coefficient can be 0.12, and the surface treatment correction coefficient can be 0.11. Of course, in other exemplary embodiments of the present disclosure, the size, forging machining, and surface treatment correction coefficients of the blade can also be other suitable values.

[0043] In addition, after obtaining the correction coefficients, the Goodman curve of the blade material can be corrected based on the correction coefficients, that is, both the ordinate and abscissa of the Goodman curve of the blade material are multiplied by the correction coefficients to obtain the Goodman curve of the blade. This data can reflect the correlation with temperature. After obtaining the Goodman curve of the blade, a corresponding safety factor can also be configured for the Goodman curve of the blade, and the safety factor can be used to determine the allowable vibration stress of each point on the blade subsequently. Exemplarily, according to the requirements of the safety factor in engineering, the safety factor set for the Goodman curve of the blade can be other suitable values such as 30% to 50%.

[0044] Furthermore, the fatigue limit of the blade, as a parameter of the Goodman curve of the blade, can be used to determine the allowable vibration stress of the blade under a specified static stress. However, since raw materials, forging processes, machining processes, surface treatments, etc. will all affect the fatigue limit of the blade, the fatigue limit of the blade is different from the fatigue limit corresponding to the material used to construct the blade. Therefore, in the embodiments of the present disclosure, based on the conducted blade vibration fatigue tests, the Goodman curve of the blade material can be compared to obtain relevant correction coefficients, and then the Goodman curve of the blade material can be corrected according to the relevant correction coefficients to obtain the Goodman curve of the blade. Thus, by taking all the above factors into account, more accurate blade vibration fatigue characteristics can be obtained.

[0045] In step S120, a static strength analysis and a modal analysis are performed on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes.

[0046] Among them, the blade simulation analysis model can represent a simulation model that can reflect the geometric information, load information, and material properties of the physical blade. Static strength analysis can represent the analysis of the state of the blade simulation model under static loads, and the maximum stress, strain, and displacement of the blade under a certain specific load or a series of loads can be obtained. Modal analysis can represent the analysis of the vibration state of the blade at different frequencies, and then the vibration behavior of the blade at different frequencies and the possible vibration modes can be obtained. Static stress can represent the stress generated in the blade under static loads. Modal stress can represent the stress generated by dynamic loads in the blade under a specific vibration mode. The maximum displacement of the blade body can represent the maximum amount of movement that occurs in the blade body part of the blade under a specific mode, which can reflect the degree of deformation of the blade under a specific vibration mode. The vibration frequency can represent the natural vibration frequency of the blade under a certain mode, which can reflect the speed of the blade vibration.

[0047] In some embodiments, referring to Figure 2 as shown in, the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement of the blade body and the vibration frequency under different modes, can be obtained through steps S210 to S230. Among them:

[0048] In step S210, based on the pre-obtained blade geometric model, load information, and blade material parameters, a blade simulation analysis model is established.

[0049] Specifically, the blade geometric model can represent a geometric model that is consistent with the geometric dimensions of the physical blade. At the same time, the load information and blade material parameters of the blade simulation analysis model can be kept consistent with the load information and material parameters of the physical blade, thereby improving the simulation effect of the blade simulation analysis model. In addition, before carrying out finite element simulations, namely static strength analysis and modal analysis, the input information required for carrying out finite element simulation calculations needs to be prepared, including geometric models, load information, and material parameters, etc. Then, based on the prepared input information, a blade simulation analysis model is established. Among them, the material parameters of the calculation model of the finite element simulation method can be set to be associated with temperature, that is, the material parameters are related to temperature, so that the change of material parameters with temperature can be reflected.

[0050] In step S220, static strength analysis of the blade simulation analysis model is carried out at different rotational speeds to obtain the static stress of the blade at different rotational speeds.

[0051] Specifically, the static strength analysis of the blade simulation analysis model at different rotational speeds can be carried out by means of finite element simulation. The static strength calculation of the blade simulation analysis model at different rotational speeds can be performed using other relevant finite element analysis software such as ANSYS and ABAQUS. Then, based on the calculation results, finite element simulation is adopted to analyze the prestress of the belt in different states, so as to obtain the static strength analysis results at different rotational speeds, that is, the static stress of the blade at different rotational speeds.

[0052] In step S230, the modal analysis of the blade simulation analysis model is carried out at different rotational speeds to obtain the modal stress of the blade at different rotational speeds, the maximum displacement of the blade body in different modes, and the vibration frequency.

[0053] Specifically, the modal analysis of the blade simulation analysis model at different rotational speeds can be based on other relevant finite element analysis software such as ANSYS and ABAQUS, so as to obtain the static strength analysis results at different rotational speeds, that is, the modal stress of the blade at different rotational speeds, the maximum displacement of the blade body in different modes, and the vibration frequency. This modal analysis can calculate the element solution.

[0054] In addition, since the dangerous points on the blade at different rotational speeds are not necessarily the same, and the probabilities of resonance at different rotational speeds obtained from the Campbell diagram are also different, it is beneficial to determine the dangerous points by carrying out the static strength analysis and modal analysis of the blade simulation analysis model at different rotational speeds.

[0055] Then refer to Figure 1 , in step S130, according to the Goodman curve of the blade and the static stress, the allowable vibration stress is calculated to determine the allowable vibration stress of each point on the blade at different rotational speeds.

[0056] Specifically, combining the Goodman curve of the blade and the static stress of the blade obtained from the above static strength analysis results, the allowable vibration stress is calculated, and the allowable vibration stress of each point on the blade at different rotational speeds can be obtained. Among them, the allowable vibration stress can represent the maximum vibration stress value allowed by the blade. In addition, the calculation of the allowable vibration stress can consider the safety factor corresponding to the above Goodman curve of the blade.

[0057] In step S140, based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency, the dynamic stress reserve coefficient corresponding to each point on the blade is determined.

[0058] Among them, the dynamic stress reserve coefficient is an index to evaluate the fatigue performance of materials or structures under dynamic loads. It can be used to evaluate the danger degree of each point on the blade. The smaller the dynamic stress reserve coefficient, the more dangerous the corresponding point position is.

[0059] In some embodiments, based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency, the dynamic stress reserve coefficient corresponding to each point on the blade is determined. Specifically, the following steps are included: Based on the modal stress, maximum displacement of the blade body, and vibration frequency, the modal stress of each point on the blade under unit displacement and frequency is determined; Based on the ratio of the allowable vibration stress and the modal stress of each point on the blade under unit displacement and frequency, the dynamic stress reserve coefficient corresponding to each point on the blade is determined.

[0060] Specifically, it can be obtained by calculating the modal stress of each point on the blade under unit displacement and frequency. Among them, σ AF can represent the modal stress of each point on the blade under unit displacement and frequency, A can represent the maximum displacement of the blade body in the corresponding mode, F can represent the vibration frequency of the blade in the corresponding mode, and σ 模态 can represent the modal stress of the corresponding point on the blade.

[0061] Then, after obtaining the modal stress of each point on the blade under unit displacement and frequency, it can be based on calculating the dynamic stress reserve coefficient corresponding to each point on the blade. Among them, η can represent the dynamic stress reserve coefficient corresponding to each point on the blade, and σ 许用 can represent the allowable vibration stress of the corresponding point on the blade.

[0062] Then referring to Figure 1 , in step S150, according to the circumferential displacement at the corresponding position on the blade of the sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, the limit value calculation is performed to determine the blade amplitude limit value corresponding to the blade.

[0063] Among them, the circumferential displacement can represent the rotational displacement of the sensor on the blade at the corresponding position. The sensor can be used to measure the lead or lag situation between the actual arrival time of the blade at the sensor and the theoretical arrival time. Exemplarily, the sensor can be a blade timing (BTT) sensor, which can be installed on the casing of the blade. The blade amplitude limit value can represent the maximum allowable value of the blade amplitude during the blade stress state monitoring. By setting the blade amplitude limit value, the safe operation of the blade test piece during the test can be ensured.

[0064] In some embodiments, referring to Figure 3 shown, the blade amplitude limit value corresponding to the blade can be determined through steps S310 to S330. Among them:

[0065] In step S310, the sensor position of the sensor on the blade is obtained.

[0066] Among them, the sensor position on the blade can represent the circumferential position of the sensor installed on the casing, and this position can correspond to a certain circumferential position on the blade.

[0067] In step S320, the circumferential displacement of the corresponding position of the sensor position on the blade is determined through modal analysis.

[0068] Among them, the sensor can be a blade timing sensor, and then the circumferential displacement of the blade position corresponding to the blade timing sensor position can be determined through modal analysis.

[0069] In step S330, based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, the limit value and the alarm value corresponding to the blade are determined, and the limit value and the alarm value are used as the blade amplitude limit value.

[0070] Among them, the point corresponding to the minimum value of the dynamic stress reserve coefficient is the most dangerous point on the blade. The maximum displacement of the blade body and the vibration frequency can be obtained through the modal analysis of the blade simulation analysis model at different rotational speeds as described above. The limit value can represent the maximum allowable amplitude of the blade vibration, that is, the maximum safety limit of the blade vibration. If the vibration amplitude of the blade exceeds this value, it may cause blade damage or abnormal operation of the test piece. Therefore, during the test process, if the vibration amplitude of the blade reaches or exceeds this limit value, measures must be taken immediately to reduce the vibration or stop the test. The alarm value can represent the alarm limit of the blade vibration. When the vibration amplitude of the blade approaches or reaches the alarm value, an alarm should be issued to remind the operator to pay attention and take corresponding measures.

[0071] Furthermore, by using the limit value and the alarm value as the blade amplitude limit value, the limit state and the alarm state of the most dangerous point of the blade can be reflected. And when conducting an aeroengine test, the blade amplitude limit value is provided for monitoring the blade vibration using a blade timer, so as to ensure the safe operation of the blade test piece.

[0072] In some embodiments, as shown in Figure 4 , the limit value and the alarm value corresponding to the blade can be determined through steps S410 to S420. Among them:

[0073] In step S410, the limit value is calculated according to the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency to determine the limit value corresponding to the blade.

[0074] Specifically, the limit value corresponding to the blade can be denoted as u 极限 , then Among them, η mincan represent the minimum value of the dynamic stress reserve coefficient corresponding to each point on the blade, A can represent the maximum displacement of the blade body in the corresponding mode, F can represent the vibration frequency of the blade in the corresponding mode, and u 周向 can represent the circumferential displacement of the sensor position at the corresponding position on the blade.

[0075] In step S420, based on the product of the limit value and the preset alarm coefficient, determine the alarm value corresponding to the blade.

[0076] Specifically, the alarm value corresponding to the blade can be denoted as u 报警 , then u 报警 = u 极限 * k, where k represents the alarm coefficient and k is less than 1.

[0077] In some embodiments, the dangerous state of the blade can also be determined through the following steps: determine the degree of danger of each point on the blade based on the dynamic stress reserve coefficient; take the point with the minimum dynamic stress reserve coefficient as the most dangerous point of the blade at different rotational speeds.

[0078] Among them, the dynamic stress reserve coefficient can be used to determine the degree of danger of each point on the blade. The smaller the dynamic stress reserve coefficient, the higher the degree of danger of the corresponding point on the blade; the larger the dynamic stress reserve coefficient, the lower the degree of danger of the corresponding point on the blade. Therefore, the point with the minimum dynamic stress reserve coefficient can be taken as the most dangerous point of the blade at different rotational speeds, and then the blade vibration can be restricted based on the dynamic stress reserve coefficient.

[0079] Figure 5 Schematically shows a flow chart of another method for modifying the Goodman curve of a blade considering crystal orientation and multiaxial stress state according to an embodiment of the present disclosure, which specifically includes the following steps:

[0080] Step 502, establish a blade simulation analysis model. Specifically, a blade simulation analysis model can be established based on the pre-acquired blade geometric model, load information, and blade material parameters.

[0081] Step 504, obtain the Goodman curve of the blade material.

[0082] Step 506, obtain the Goodman curve of the blade. Specifically, the correction coefficient can be obtained by querying the vibration fatigue test database, and then the ordinate and abscissa of the Goodman curve of the blade material are corrected based on the correction coefficient to obtain the Goodman curve of the blade, and the safety factor corresponding to the Goodman curve of the blade is configured.

[0083] Step 508, perform static strength analysis on the blade simulation analysis model at different rotational speeds to obtain the static stress of the blade at different rotational speeds.

[0084] Step 510: Perform modal analysis on the blade simulation analysis model at different rotational speeds to obtain the modal stress of the blade at different rotational speeds, the maximum displacement of the blade body under different modes, and the vibration frequency.

[0085] Step 512: Calculate the allowable vibration stress according to the Goodman curve of the blade and the static stress to determine the allowable vibration stress of each point on the blade at different rotational speeds.

[0086] Step 514: Determine the circumferential position where the sensor is installed on the machine brake, that is, the sensor position.

[0087] Step 516: Determine the circumferential displacement of the corresponding position of the sensor position on the blade through modal analysis.

[0088] Step 518: Based on the ratio of the allowable vibration stress and the modal stress of each point on the blade under unit displacement and frequency, determine the dynamic stress reserve coefficient corresponding to each point on the blade, and take the point with the minimum dynamic stress reserve coefficient as the most dangerous point of the blade at different rotational speeds.

[0089] Step 520: Determine the amplitude limit value of the blade. Specifically, based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, determine the limit value and alarm value corresponding to the blade, and use the limit value and alarm value as the amplitude limit value of the blade.

[0090] In the method for correcting the Goodman curve of the blade considering crystal orientation and multiaxial stress state provided by the above embodiments, the determination of the most dangerous point of the blade can consider both static stress and modal stress. When the rotational speed changes, the aerodynamic load, temperature field, and centrifugal load all change, and its most dangerous point may change, which may be the point with the maximum static stress, the point with the maximum modal stress, or the point with both being relatively large. The method involved in the present disclosure can take into account the above factors to evaluate the danger degree of each point of the blade and can determine the most dangerous point of the blade. In addition, correction coefficients such as size, forging machining, and surface treatment are used to obtain the Goodman curve of the blade, where the correction coefficients are obtained based on the accumulation of previous tests. Thus, it is possible to avoid further carrying out a large number of blade vibration fatigue tests. When judging the most dangerous point on the blade, considering the influence of static strength in combination with the Goodman curve, through the amplitude limit value of the blade, it can be used for the safety monitoring of the test. And at different rotational speeds and different orders of the blade, the numerical values of the amplitude limit value of the blade are different. By determining the amplitude limit value of the blade, the state of the most dangerous point on the blade is reflected, providing a guarantee for the safe operation of the test.

[0091] In the technical solution provided by the embodiments of the present disclosure, on the one hand, based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material, the blade Goodman curve is determined, and more accurate blade vibration fatigue characteristics can be obtained; on the other hand, static strength analysis and modal analysis are performed on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes. Furthermore, according to the circumferential displacement at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency preset on the blade, the limit value calculation is carried out to determine the corresponding blade amplitude limit value of the blade, improving the accuracy of the blade amplitude limit value in the blade stress state monitoring process and ensuring the safe operation of the blade test piece.

[0092] Next, in the embodiments of the present disclosure, a blade Goodman curve correction device considering crystal orientation and multiaxial stress state is also provided. Referring to Figure 6 as shown, the blade Goodman curve correction device 600 considering crystal orientation and multiaxial stress state may be composed of a curve determination module 601, a model analysis module 602, an allowable stress determination module 603, a reserve coefficient determination module 604, and a limit value determination module 605, where: the curve determination module 601 may be used to determine the blade Goodman curve based on the correction coefficient obtained from the blade vibration fatigue test and the Goodman curve of the blade material; the model analysis module 602 may be used to perform static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different rotational speeds, as well as the maximum displacement and vibration frequency of the blade body in different modes; the allowable stress determination module 603 may be used to calculate the allowable vibration stress according to the blade Goodman curve and the static stress to determine the allowable vibration stress of each point on the blade at different rotational speeds; the reserve coefficient determination module 604 may be used to determine the dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, modal stress, maximum displacement of the blade body, and vibration frequency; the limit value determination module 605 may be used to perform limit value calculation according to the circumferential displacement at the corresponding position on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency preset on the blade to determine the corresponding blade amplitude limit value of the blade.

[0093] In an exemplary embodiment of the present disclosure, the curve determination module may include: a correction coefficient acquisition unit, which may be used to obtain the correction coefficient by querying the vibration fatigue test database; a curve correction unit, which may be used to correct the ordinate and abscissa of the Goodman curve of the blade material based on the correction coefficient to obtain the blade Goodman curve and configure the safety factor corresponding to the blade Goodman curve.

[0094] In an exemplary embodiment of the present disclosure, the model analysis module may include: a simulation analysis model establishment unit, which can be used to establish a blade simulation analysis model based on a pre-acquired blade geometric model, load information, and blade material parameters; a static strength analysis unit, which can be used to perform static strength analysis on the blade simulation analysis model at different rotational speeds to obtain the static stress of the blade at different rotational speeds; a modal analysis unit, which can be used to perform modal analysis on the blade simulation analysis model at different rotational speeds to obtain the modal stress of the blade at different rotational speeds, the maximum displacement of the blade body in different modes, and the vibration frequency.

[0095] In an exemplary embodiment of the present disclosure, the reserve coefficient determination module may include: a modal stress determination unit, which can be used to determine the modal stress of each point on the blade under unit displacement and frequency based on the modal stress, the maximum displacement of the blade body, and the vibration frequency; a dynamic stress reserve coefficient determination unit, which can be used to determine the dynamic stress reserve coefficient corresponding to each point on the blade based on the ratio of the allowable vibration stress to the modal stress of each point on the blade under unit displacement and frequency.

[0096] In an exemplary embodiment of the present disclosure, the limit value determination module may include: a sensor position acquisition unit, which can be used to acquire the sensor position of the sensor on the blade; a circumferential displacement determination unit, which can be used to determine the circumferential displacement of the corresponding position of the sensor position on the blade through modal analysis; a limit value and alarm value determination unit, which can be used to determine the limit value and alarm value corresponding to the blade based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency, and use the limit value and alarm value as the blade amplitude limit value.

[0097] In an exemplary embodiment of the present disclosure, the limit value and alarm value determination unit may include: a limit value determination subunit, which can be used to calculate the limit value according to the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body, and the vibration frequency to determine the limit value corresponding to the blade; an alarm value determination subunit, which can be used to determine the alarm value corresponding to the blade based on the product of the limit value and a preset alarm coefficient.

[0098] In an exemplary embodiment of the present disclosure, the blade Goodman curve correction device considering crystal orientation and multiaxial stress state may further include: a most dangerous point determination unit, which can be used to determine the degree of danger of each point on the blade based on the dynamic stress reserve coefficient, and take the point with the minimum dynamic stress reserve coefficient as the most dangerous point of the blade at different rotational speeds.

[0099] It should be noted that the specific details of each part in the above-mentioned vane Goodman curve correction device considering crystal orientation and multiaxial stress state have been described in detail in the implementation manners of the vane Goodman curve correction method considering crystal orientation and multiaxial stress state. For the undisclosed detailed content, reference can be made to the implementation manners in the method part, and thus it will not be elaborated here.

[0100] In an exemplary embodiment of the present disclosure, an electronic device capable of implementing the above method is further provided.

[0101] Those skilled in the art can understand that various aspects of the present disclosure can be implemented as a system, a method, or a program product. Therefore, various aspects of the present disclosure can be specifically implemented in the following forms, namely: a complete hardware implementation manner, a complete software implementation manner (including firmware, microcode, etc.), or an implementation manner combining hardware and software aspects, which can be collectively referred to as "circuit", "module", or "system" here.

[0102] Next, refer to Figure 7 to describe the electronic device 700 according to this embodiment of the present disclosure. Figure 7 The shown electronic device 700 is only an example and should not impose any limitation on the functions and usage scope of the embodiments of the present disclosure.

[0103] As Figure 7 shown, the electronic device 700 is presented in the form of a general-purpose computing device. The components of the electronic device 700 may include, but are not limited to: at least one of the above-mentioned processing units 710, at least one of the above-mentioned storage units 720, a bus 730 connecting different system components (including the storage unit 720 and the processing unit 710), and a display unit 740.

[0104] Among them, the storage unit stores program codes, and the program codes can be executed by the processing unit 710, so that the processing unit 710 executes the steps according to various exemplary embodiments of the present disclosure described in the above-mentioned "exemplary method" part of this specification. For example, the processing unit 710 can execute the steps as Figure 1 shown.

[0105] The storage unit 720 may include a readable medium in the form of a volatile storage unit, such as a random access storage unit (RAM) 7201 and / or a cache storage unit 7202, and may further include a read-only storage unit (ROM) 7203.

[0106] The storage unit 720 may also include a program / utility 7204 having a set (at least one) of program modules 7205. Such program modules 7205 include, but are not limited to, an operating system, one or more application programs, other program modules, and program data. Each or some combination of these examples may include an implementation of a network environment.

[0107] The bus 730 may represent one or more of several types of bus structures, including a memory bus or memory controller, a peripheral bus, an accelerated graphics port, a processing unit, or a local bus using any of a variety of bus structures.

[0108] The electronic device 700 may also communicate with one or more external devices 800 (such as a keyboard, a pointing device, a Bluetooth device, etc.), may also communicate with one or more devices that enable a user to interact with the electronic device 700, and / or may communicate with any device that enables the electronic device 700 to communicate with one or more other computing devices (such as a router, a modem, etc.). Such communication may be carried out through the input / output (I / O) interface 750. Also, the electronic device 700 may communicate with one or more networks (such as a local area network (LAN), a wide area network (WAN), and / or a public network, such as the Internet) through the network adapter 760. As shown in the figure, the network adapter 760 communicates with other modules of the electronic device 700 through the bus 730. It should be understood that, although not shown in the figure, other hardware and / or software modules may be used in conjunction with the electronic device 700, including but not limited to: microcode, device drivers, redundant processing units, external disk drive arrays, RAID systems, tape drives, and data backup storage systems, etc.

[0109] Through the description of the above embodiments, those skilled in the art can easily understand that the example embodiments described herein can be implemented by software, or can be implemented by a combination of software and necessary hardware. Therefore, the technical solutions according to the embodiments of the present disclosure can be embodied in the form of a software product, which can be stored in a non-volatile storage medium (which can be a CD-ROM, a USB flash drive, a mobile hard disk, etc.) or on a network, including several instructions to enable a computing device (which can be a personal computer, a server, a terminal device, or an electronic device, etc.) to execute the method according to the embodiments of the present disclosure.

[0110] In an exemplary embodiment of the present disclosure, there is also provided a computer-readable storage medium, on which a program product capable of implementing the above methods in this specification is stored. In some possible implementation manners, various aspects of the present disclosure can also be implemented in the form of a program product, which includes program code. When the program product runs on a terminal device, the program code is used to cause the terminal device to execute the steps according to various exemplary embodiments of the present disclosure described in the above "Exemplary Method" section of this specification.

[0111] The program product for implementing the above method according to an embodiment of the present disclosure may be a portable compact disc read-only memory (CD-ROM) and includes program code, and may run on a terminal device, such as a personal computer. However, the program product of the present disclosure is not limited thereto. In this document, the readable storage medium may be any tangible medium that contains or stores a program that can be used by or in conjunction with an instruction execution system, apparatus, or device.

[0112] The program product may adopt any combination of one or more readable media. The readable media may be a readable signal medium or a readable storage medium. The readable storage medium may, for example, but not be limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, apparatus, or device, or any combination of the above. More specific examples (non-exhaustive list) of the readable storage medium include: an electrical connection having one or more wires, a portable disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disc read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination of the above.

[0113] The computer-readable signal medium may include a data signal propagated in a baseband or as part of a carrier wave, which carries the readable program code. Such a propagated data signal may take various forms, including but not limited to electromagnetic signals, optical signals, or any suitable combination of the above. The readable signal medium may also be any readable medium other than the readable storage medium, which can send, propagate, or transmit a program for use by or in conjunction with an instruction execution system, apparatus, or device.

[0114] The program code contained on the readable medium may be transmitted by any suitable medium, including but not limited to wireless, wired, optical fiber, RF, etc., or any suitable combination of the above.

[0115] Program code for performing the operations of the present disclosure can be written in any combination of one or more programming languages, including object-oriented programming languages such as Java, C++, etc., and also including conventional procedural programming languages such as the "C" language or similar programming languages. The program code can be executed entirely on the user's computing device, partially on the user's device, executed as a stand-alone software package, partially on the user's computing device and partially on a remote computing device, or entirely on a remote computing device or server. In the case of a remote computing device, the remote computing device can be connected to the user's computing device through any type of network, including a local area network (LAN) or a wide area network (WAN), or can be connected to an external computing device (e.g., by connecting through the Internet using an Internet service provider).

[0116] In addition, the above-mentioned drawings are only schematic illustrations of the processes included in the method according to the exemplary embodiments of the present disclosure, rather than for limiting purposes. It is easy to understand that the processes shown in the above-mentioned drawings do not indicate or limit the chronological order of these processes. Additionally, it is also easy to understand that these processes can be executed, for example, synchronously or asynchronously in multiple modules.

[0117] Those skilled in the art will readily conceive of other embodiments of the present disclosure after considering the specification and practicing the invention herein. This application is intended to cover any variations, uses, or adaptations of the present disclosure that follow the general principles of the present disclosure and include well-known knowledge or conventional technical means in the technical field not invented by the present disclosure. The specification and embodiments are only regarded as exemplary, and the true scope and spirit of the present disclosure are pointed out by the claims.

[0118] It should be understood that the present disclosure is not limited to the exact structures described above and shown in the drawings, and various modifications and changes can be made without departing from its scope. The scope of the present disclosure is only defined by the appended claims.

Claims

1. A method for correcting the Goodman curve of a blade considering crystal orientation and multiaxial stress state, characterized in that: include: Determine the Goodman curve of the blade based on the correction factor obtained from the blade vibration fatigue test and the Goodman curve of the blade material; Perform static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different speeds, as well as the maximum displacement and vibration frequency of the blade under different modes; According to the Goodman curve of the blade and the static stress, the allowable vibration stress is calculated to determine the allowable vibration stress of each point on the blade at different rotation speeds; Determining a dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, the modal stress, the maximum displacement of the blade body and the vibration frequency; According to the circumferential displacement of the corresponding position on the blade of the sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency, the limit value calculation is performed to determine the blade amplitude limit value corresponding to the blade.

2. The method according to claim 1, characterized in that The method of determining the blade Goodman curve based on the correction coefficient obtained from the blade vibration fatigue test and the blade material Goodman curve comprises: Obtaining the correction factor by querying a vibration fatigue test database; The ordinate and abscissa of the Goodman curve of the blade material are corrected based on the correction coefficient to obtain the blade Goodman curve, and a safety factor corresponding to the blade Goodman curve is configured.

3. The method according to claim 1, characterized in that The static strength analysis and modal analysis of the blade simulation analysis model are performed to obtain the static stress and modal stress of the blade at different rotation speeds, as well as the maximum displacement and vibration frequency of the blade under different modes, including: Establishing the blade simulation analysis model based on the pre-acquired blade geometry model, load information and blade material parameters; Performing static strength analysis on the blade simulation analysis model at different rotation speeds to obtain static stress of the blade at different rotation speeds; The blade simulation analysis model is subjected to modal analysis at different rotational speeds to obtain the modal stress of the blade at different rotational speeds, and the maximum displacement and vibration frequency of the blade body at different modes.

4. The method according to claim 1, characterized in that: Determining a dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, the modal stress, the maximum displacement of the blade body and the vibration frequency includes: Based on the modal stress, the maximum displacement of the blade body and the vibration frequency, determining the modal stress of each point on the blade at unit displacement and frequency; Based on the ratio of the allowable vibration stress to the modal stress of each point on the blade at unit displacement and frequency, a dynamic stress reserve coefficient corresponding to each point on the blade is determined.

5. The method according to claim 1, characterized in that The limiting value calculation is performed according to the circumferential displacement of the corresponding position on the blade at the sensor position preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency to determine the blade amplitude limiting value corresponding to the blade, including: obtaining a sensor position of the sensor on the blade; Determining the circumferential displacement of the sensor position corresponding to the position on the blade through the modal analysis; Based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency, the limit value and the alarm value corresponding to the blade are determined, and the limit value and the alarm value are used as the blade amplitude limit value.

6. The method according to claim 5, characterized in that The determining of the limit value and the alarm value corresponding to the blade based on the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency includes: Performing limit value calculation according to the circumferential displacement, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency, and determining the limit value corresponding to the blade; Based on the product of the limit value and a preset alarm coefficient, an alarm value corresponding to the blade is determined.

7. The method according to claim 1, characterized in that The method further comprises: Determining the degree of danger of each point on the blade based on the dynamic stress reserve coefficient; The point with the smallest dynamic stress reserve coefficient is taken as the most dangerous point of the blade at different rotation speeds.

8. A blade Goodman curve correction device considering crystal orientation and multi-axial stress state, characterized in that: include: A curve determination module, used for determining a blade Goodman curve based on a correction factor obtained from a blade vibration fatigue test and a blade material Goodman curve; The model analysis module is used to perform static strength analysis and modal analysis on the blade simulation analysis model to obtain the static stress and modal stress of the blade at different speeds, as well as the maximum displacement and vibration frequency of the blade under different modes; An allowable stress determination module is used to calculate the allowable vibration stress according to the Goodman curve of the blade and the static stress, and determine the allowable vibration stress of each point on the blade at different rotation speeds; A reserve coefficient determination module, used to determine the dynamic stress reserve coefficient corresponding to each point on the blade based on the allowable vibration stress, the modal stress, the maximum displacement of the blade body and the vibration frequency; The limit value determination module is used to calculate the limit value according to the circumferential displacement of the corresponding position on the blade of the sensor preset on the blade, the minimum value of the dynamic stress reserve coefficient, the maximum displacement of the blade body and the vibration frequency, so as to determine the blade amplitude limit value corresponding to the blade.

9. An electronic device, characterized in that: include: processor; as well as A memory, configured to store executable instructions of the processor; The processor is configured to perform the method of any one of claims 1 to 7 by executing the executable instructions.

10. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the method according to any one of claims 1 to 7 is implemented.

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