Simulation piece design method and system considering stress gradient of wheel disc after pre-rotation

Abstract

The invention discloses a design method and system for a simulation part considering the stress gradient of a pre-rotated wheel disc, and relates to the technical field of wheel disc fatigue life detection.The method comprises the steps that a geometric model of the pre-rotated wheel disc is obtained, and physical property parameters of a wheel disc preparation material at different temperatures are determined; determining first maximum stress distribution of the non-pre-rotating wheel disc and the pre-rotating wheel disc according to the geometric model and the physical property parameters based on finite element simulation software; based on a stress gradient theory, determining an effective assessment distance of the maximum principal stress of the non-pre-rotating wheel disc and the pre-rotating wheel disc; determining second maximum stress distribution according to the first maximum stress distribution and an effective assessment distance between the maximum principal stress of the non-pre-rotating wheel disc and the maximum principal stress of the pre-rotating wheel disc; and according to the second maximum stress distribution, designing the key geometric dimension, the pre-stretching load and the fatigue load of the simulation piece. According to the invention, the design complexity of the simulation part can be reduced, and the fatigue change of the pre-rotated wheel disc can be effectively verified.

Description

Technical Field

[0001] The present application relates to the technical field of wheel disk fatigue life detection, and in particular to a design method and system for a simulation component that takes into account the stress gradient of a wheel disk after pre-rotation. Background Art

[0002] At present, when predicting the fatigue life of a wheel, the traditional life prediction theory is the local stress method and the local strain method. These methods often only consider the maximum stress of the wheel during service. However, with the deepening of research in the field of fatigue, relevant scholars have found that stress gradient also has an important influence on fatigue life. Therefore, the traditional life prediction method has limitations in predicting the fatigue life of the wheel, especially for the wheel after pre-rotation, because the pre-rotation changes the stress distribution gradient near the center hole of the wheel, which makes the accurate prediction of the fatigue life of the wheel more difficult. In order to consider the influence of stress gradient, some scholars use the notch simulation part to consider the influence of stress gradient, but due to the difference in geometric dimensions between the simulation part and the wheel, the range of the stress assessment area is difficult to accurately determine; if the assessment range is too large, it will increase the difficulty of the simulation part design, and if the assessment range is too small, the influence of stress gradient cannot be fully considered. In addition, the stress distribution of the pre-rotated wheel will also change during service, which makes the design of the stress gradient of the simulation part more challenging. Summary of the invention

[0003] The purpose of this application is to provide a design method and system for a simulation part that takes into account the stress gradient of the pre-rotation wheel disc, which can reduce the complexity of the simulation part design and ensure that the fatigue changes of the pre-rotation wheel disc are effectively verified.

[0004] To achieve the above objectives, this application provides the following solutions:

[0005] In a first aspect, the present application provides a design method for a simulation component that takes into account the stress gradient of a pre-rotation wheel disc, comprising:

[0006] Obtaining a geometric model of a pre-rotated roulette wheel;

[0007] Based on the geometric model of the pre-rotated wheel, determining the physical property parameters of the wheel preparation material at different temperatures;

[0008] According to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material, based on the finite element simulation software, the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel is determined; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature;

[0009] Based on the stress gradient theory, the effective test distance of the maximum principal stress of the un-pre-rotated disk and the pre-rotated disk is determined;

[0010] According to the first maximum stress distribution and the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel, a second maximum stress distribution is determined; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel in the radial direction of the wheel under the service condition and within the test distance;

[0011] According to the second maximum stress distribution, the key geometric dimensions, pre-tension load and fatigue load of the simulation part are designed.

[0012] Optionally, according to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material, based on finite element simulation software, the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel at the service speed along the wheel radial direction is determined, specifically including:

[0013] Input the geometric model of the pre-rotated wheel disc and the physical property parameters of the wheel disc preparation material into ABAQUS finite element simulation software;

[0014] The pre-rotation speed, service speed and service temperature field of the disk are set in the ABAQUS finite element simulation software, and the finite element simulation is performed to obtain the distribution of the maximum principal stress along the radial direction of the disk at the service speed for the non-pre-rotated disk and the pre-rotated disk.

[0015] Optionally, based on the stress gradient theory, the effective assessment distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel is determined, specifically including:

[0016] According to the formula χ ef =min(χ), determine the effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk;

[0017] in, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

[0018] Optionally, the key geometric dimensions include the notch radius of the simulation component, the net cross-sectional width and the width of the working end of the simulation component.

[0019] Optionally, according to the second maximum stress distribution, key geometric dimensions, pre-tension load and fatigue load of the simulation part are designed, specifically including:

[0020] Obtaining a geometric model of a simulation component;

[0021] Set the initial notch radius of the simulated part;

[0022] Input the geometric model of the simulation component after setting the initial notch radius into the ABAQUS software, input the initial pre-stretching load and the initial fatigue load, and extract the distribution of the maximum principal stress of the simulation component along the path ab;

[0023] Determine whether the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is consistent with the maximum stress distribution gradient of the non-pre-rotated wheel within the effective test distance;

[0024] If they are inconsistent, adjust the notch radius of the simulation part and re-input the updated geometry model of the simulation part into the ABAQUS software;

[0025] If they are consistent, the optimal notch radius of the simulated part is obtained;

[0026] Adjust the net cross-sectional width W, working end width D and fatigue load of the simulation part, and extract the maximum principal stress distribution of the non-pre-stretched simulation part along the path ab under fatigue load;

[0027] Determine whether the maximum principal stress distribution of the unstretched simulation part is consistent with the maximum principal stress distribution of the unrotated wheel within the effective assessment distance;

[0028] If they are inconsistent, adjust the fatigue load of the simulation component and re-input the updated geometry model of the simulation component into the ABAQUS software;

[0029] If they are consistent, the optimal fatigue load of the simulated component is obtained;

[0030] Determine whether the maximum principal stress distribution of the pre-stretched simulated component under fatigue load is consistent with the maximum principal stress distribution of the pre-rotated wheel at the service speed within the effective test distance;

[0031] If they are inconsistent, adjust the pre-tension load of the simulation part and re-input the updated geometric model of the simulation part into the ABAQUS software;

[0032] If they are consistent, the optimal pre-tensioning load of the simulation component is obtained.

[0033] Optionally, if there is inconsistency, the notch radius of the simulation part is adjusted, and the updated geometric model of the simulation part is re-input into the ABAQUS software, specifically including:

[0034] If the maximum stress distribution gradient of the non-pre-stretched simulation piece under fatigue load is greater than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation piece is increased;

[0035] If the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is smaller than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation component is reduced.

[0036] Optionally, if there is inconsistency, the fatigue load of the simulation component is adjusted, and the updated geometric model of the simulation component is re-input into the ABAQUS software, specifically including:

[0037] If the maximum principal stress distribution of the unpre-stretched simulation piece is less than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation piece is increased;

[0038] If the maximum principal stress distribution of the unpre-stretched simulation component is greater than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation component is reduced.

[0039] Optionally, the physical property parameters include elastic modulus, yield strength, Poisson's ratio, density, and expansion coefficient.

[0040] In a second aspect, the present application provides a design system for a simulation component that takes into account the stress gradient of a pre-rotation wheel disc, the design system comprising:

[0041] A model acquisition module, used to acquire a geometric model of the pre-rotation wheel;

[0042] A parameter determination module, used for determining the physical property parameters of the wheel disc preparation material at different temperatures based on the geometric model of the pre-rotated wheel disc;

[0043] A simulation module, for determining the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel according to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material based on finite element simulation software; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature;

[0044] An effective test distance calculation module is used to determine the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel based on the stress gradient theory;

[0045] A maximum stress distribution calculation module is used to determine a second maximum stress distribution according to the first maximum stress distribution and an effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel under service conditions and within the test distance along the radial direction of the wheel;

[0046] The design module is used to design the key geometric dimensions, pre-tension load and fatigue load of the simulation part according to the second maximum stress distribution.

[0047] Optionally, the effective assessment distance calculation module specifically includes:

[0048] The effective assessment distance calculation submodule is used to calculate the distance according to the formula χ ef=min(χ), determine the effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk; where, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

[0049] According to the specific embodiments provided in this application, this application discloses the following technical effects:

[0050] The present application provides a design method and system for a simulation part that considers the stress gradient of a pre-rotated wheel. First, the geometric model of the pre-rotated wheel is obtained, which is the basis of all analyses. Then, based on the geometric model, the physical properties of the wheel preparation material at different temperatures are studied and determined. Then, the finite element simulation software is used to simulate and calculate the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel under the service condition in combination with the geometric model of the pre-rotated wheel and the physical properties of the material. The service conditions here include the service speed and the service temperature, which are both important factors affecting the stress distribution of the wheel. Next, based on the stress gradient theory, the effective assessment distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel is determined. This step helps to more accurately evaluate the fatigue performance of the wheel because the stress gradient is one of the key factors affecting the fatigue life. After determining the effective assessment distance, the second maximum stress distribution is further derived based on the first maximum stress distribution and the effective assessment distance. This distribution reflects the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel under the service condition and within the assessment distance along the radial direction of the wheel. Finally, according to the second maximum stress distribution, the key geometric dimensions, pre-tension load and fatigue load of the simulation part are designed. Since these design parameters are based on accurate stress analysis and theoretical derivation, the design difficulty of the simulation part can be greatly reduced, while ensuring that the fatigue change of the wheel disc after pre-rotation is effectively verified. BRIEF DESCRIPTION OF THE DRAWINGS

[0051] In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for use in the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present application. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying creative work.

[0052] Figure 1 A schematic flow chart of a design method of a simulation component considering the stress gradient of a wheel disc after pre-rotation provided in an embodiment of the present application;

[0053] Figure 2 A technical roadmap provided for an embodiment of the present application;

[0054] Figure 3A schematic diagram of key geometric dimensions of a simulation component provided in an embodiment of the present application;

[0055] Figure 4 A comparison diagram of the maximum principal stress gradients of a wheel disc and a simulation component provided in an embodiment of the present application;

[0056] Figure 5 A schematic diagram of increasing the thickness of the supporting end of the simulation member provided in one embodiment of the present application;

[0057] Figure 6 A schematic diagram of increasing the width of the supporting end of the simulation member provided in one embodiment of the present application;

[0058] Figure 7 A schematic diagram of the structure of a design system for a simulation component that takes into account the stress gradient of a wheel disc after pre-rotation, provided in one embodiment of the present application. DETAILED DESCRIPTION

[0059] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0060] Pre-rotation is an advanced technology to improve the fatigue performance of the roulette wheel. As a key parameter of the pre-rotation process, the determination of the pre-rotation speed needs to consider multiple factors such as the deformation of the roulette wheel after rotation, fatigue life, and equipment model. However, since the assessment period of the fatigue life of the roulette wheel is relatively long, and the results of the fatigue life have a certain degree of dispersion, multiple groups of parallel experiments are required to determine the pre-rotation speed parameters, and the research cycle and time cost are relatively high. At present, it is a common method to estimate the fatigue life of the roulette wheel through pre-rotation simulation parts, but they often do not consider the distribution gradient of the dangerous area of ​​the roulette wheel; and some simulation parts design methods that consider the distribution gradient are also difficult to scientifically determine the range of the distribution gradient, which makes the design method of the pre-rotation simulation parts less scientific, lacks theoretical basis, and is more difficult to design. In response to the above problems, the present invention combines the finite element method and fatigue theory to propose a design method for verifying the simulation parts of pre-rotation to improve the fatigue life of the roulette wheel.

[0061] The wheel is a key rotating component on an aircraft engine, mainly including turbine discs, fan discs, comb discs, compressor discs, guide discs and drum discs. Its working environment is extremely harsh, especially the center hole of the wheel is subjected to high centrifugal force during service, which is prone to fatigue failure. In order to improve the service level of the wheel, the wheel can be pre-rotated to pre-set residual compressive stress in the area near the center hole of the pre-rotated wheel, thereby reducing the load of the center hole of the wheel during service. However, since the fatigue test directly on the wheel is not only long, but also requires multiple sets of parallel tests to obtain reliable test results, it is difficult to verify the improvement of the fatigue life of the wheel after pre-rotation. Designing fatigue simulation parts according to the stress distribution of the assessment part during the service of the wheel is an important method to verify the fatigue life of the wheel. However, the stress distribution at the center hole of the wheel is complex and has a certain distribution gradient along the radial direction. The stress distribution at the center hole of the wheel after pre-rotation will also change, which greatly increases the design difficulty of the pre-rotation simulation parts, making it difficult to effectively verify the fatigue changes of the wheel after pre-rotation.

[0062] The purpose of this application is to provide a design method and system for a simulation part that takes into account the stress gradient of the pre-rotation wheel disc, which can reduce the complexity of the simulation part design and ensure that the fatigue changes of the pre-rotation wheel disc are effectively verified.

[0063] In order to make the above-mentioned objects, features and advantages of the present application more obvious and easy to understand, the present application is further described in detail below in conjunction with the accompanying drawings and specific implementation methods.

[0064] Embodiment 1

[0065] like Figure 1 As shown, this embodiment provides a design method for a simulation component considering the stress gradient of a wheel disc after pre-rotation, including:

[0066] Step 101: Obtaining a geometric model of a pre-rotated wheel;

[0067] Step 102: determining the physical property parameters of the wheel disk preparation material at different temperatures based on the geometric model of the pre-rotated wheel disk;

[0068] Step 103: According to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material, based on the finite element simulation software, determine the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature;

[0069] Step 104: Based on the stress gradient theory, determine the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel;

[0070] Step 105: determining a second maximum stress distribution according to the first maximum stress distribution and the effective test distance of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk in the radial direction of the disk under the service condition and within the test distance;

[0071] Step 106: Design the key geometric dimensions, pre-tension load and fatigue load of the simulation component according to the second maximum stress distribution.

[0072] In some embodiments, when executing steps 101-102, the specific steps may be as follows:

[0073] In this embodiment, UG software is used to draw the geometric model of the pre-rotated wheel. The physical parameters of the material for manufacturing the wheel at different temperatures are determined; the physical parameters include elastic modulus, yield strength, Poisson's ratio, density, expansion coefficient and stress-strain constitutive equation. Specifically, the elastic modulus, yield strength, Poisson's ratio, density and expansion coefficient at different temperatures are shown in Table 1, wherein the stress-strain constitutive equation at different temperatures can be obtained by high temperature tensile test.

[0074] Table 1 Physical properties of wheel materials at different temperatures

[0075]

[0076] Wherein, in some embodiments, Figure 2 As shown, when executing step 103, the specific steps may be as follows:

[0077] Input the geometric model of the pre-rotated wheel disc and the physical property parameters of the wheel disc preparation material into ABAQUS finite element simulation software;

[0078] The pre-rotation speed, service speed and service temperature field of the disk are set in the ABAQUS finite element simulation software, and the finite element simulation is performed to obtain the distribution of the maximum principal stress along the radial direction of the disk at the service speed for the non-pre-rotated disk and the pre-rotated disk.

[0079] Specifically, the geometric model and material parameters of the wheel are input into the ABAQUS finite element simulation software, and the pre-rotation speed, service speed and service temperature field of the wheel are set. For example, the pre-rotation speed is set to 34395r / min, the service speed is set to 28662r / min, the temperature at the center hole of the wheel is set to 650℃, and the temperature at the edge of the wheel is set to 750℃.

[0080] Wherein, in some embodiments, Figure 2 As shown, when executing steps 104-105, the specific steps may be as follows:

[0081] The effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk is determined based on the stress gradient theory.

[0082] In this embodiment, the effective assessment distance x ef is the stress relaxation boundary of the maximum principal stress, according to the formula χ ef =min(χ), determine the effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk; where, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

[0083] The distribution of the maximum principal stress along the radial direction of the disk within the test distance under service conditions for the disk without pre-rotation and the disk with pre-rotation is extracted.

[0084] In some embodiments, when executing step 106, the specific steps may be as follows:

[0085] Obtaining a geometric model of a simulation component;

[0086] Set the initial notch radius of the simulated part;

[0087] Input the geometric model of the simulation component after setting the initial notch radius into the ABAQUS software, input the initial pre-stretching load and the initial fatigue load, and extract the distribution of the maximum principal stress of the simulation component along the path ab;

[0088] Determine whether the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is consistent with the maximum stress distribution gradient of the non-pre-rotated wheel within the effective test distance;

[0089] If they are inconsistent, adjust the notch radius of the simulation part and re-input the updated geometry model of the simulation part into the ABAQUS software;

[0090] If they are consistent, the optimal notch radius of the simulated part is obtained;

[0091] Adjust the net cross-sectional width W, working end width D and fatigue load of the simulation part, and extract the maximum principal stress distribution of the non-pre-stretched simulation part along the path ab under fatigue load;

[0092] Determine whether the maximum principal stress distribution of the unstretched simulation part is consistent with the maximum principal stress distribution of the unrotated wheel within the effective assessment distance;

[0093] If they are inconsistent, adjust the fatigue load of the simulation component and re-input the updated geometry model of the simulation component into the ABAQUS software;

[0094] If they are consistent, the optimal fatigue load of the simulated component is obtained;

[0095] Determine whether the maximum principal stress distribution of the pre-stretched simulated component under fatigue load is consistent with the maximum principal stress distribution of the pre-rotated wheel at the service speed within the effective test distance;

[0096] If they are inconsistent, adjust the pre-tension load of the simulation part and re-input the updated geometric model of the simulation part into the ABAQUS software;

[0097] If they are consistent, the optimal pre-tensioning load of the simulation component is obtained.

[0098] If not, adjust the notch radius of the simulation part and re-input the updated simulation part geometry model into the ABAQUS software, including:

[0099] If the maximum stress distribution gradient of the non-pre-stretched simulation piece under fatigue load is greater than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation piece is increased;

[0100] If the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is smaller than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation component is reduced.

[0101] If they are inconsistent, adjust the fatigue load of the simulation component and re-input the updated geometry model of the simulation component into the ABAQUS software, including:

[0102] If the maximum principal stress distribution of the unpre-stretched simulation piece is less than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation piece is increased;

[0103] If the maximum principal stress distribution of the unpre-stretched simulation component is greater than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation component is reduced.

[0104] Specifically, the key geometric dimensions of the simulation parts are as follows: Figure 3 As shown, the notch radius R of the simulation part mainly affects the distribution gradient of the maximum principal stress, while the pre-stretching load and fatigue load mainly affect the stress magnitude at the notch of the simulation part. Therefore, when designing the simulation part, the notch radius R is determined first. First, the geometric model of the simulation part is drawn by UG software, and the notch radius of the simulation part can be consistent with the inner diameter of the wheel. The geometric model of the simulation part is input into the ABAQUS software, the material model and fatigue load are input, and the distribution of the maximum principal stress of the simulation part along the path ab is extracted. The maximum stress distribution gradient of the non-pre-stretched simulation part under fatigue load is compared within the test distance. Whether it is consistent with the maximum stress gradient distribution of the non-pre-rotated wheel, if not consistent, the notch radius needs to be redesigned. When the maximum stress distribution gradient of the simulation part is consistent with the wheel within the test distance, the notch radius design of the simulation part is completed.

[0105] Adjust the net section width W, working end width D and fatigue load of the simulation part, and extract the maximum principal stress distribution of the non-pre-stretched simulation part along the path ab under fatigue load; when the maximum principal stress distribution of the non-pre-stretched simulation part is completely consistent with the maximum principal stress distribution of the non-pre-rotated wheel within the test distance, such as Figure 4 As shown in (a) in the figure, the key geometric dimensions and fatigue loads of the simulation part have been designed.

[0106] When the stress at the bottom of the notch of the simulated part is small, the fatigue load should be increased; when the test distance of the maximum principal stress of the simulated part is smaller than the test distance of the wheel, the net section width W should be reduced or the working end width D should be increased, and vice versa.

[0107] When designing the pre-stretching load, the maximum principal stress distribution of the simulated part after pre-stretching under fatigue load is completely consistent with the maximum principal stress distribution of the wheel after pre-rotation at the service speed within the effective test distance, such as Figure 4 As shown in (b), the pre-tension load of the simulation part has been confirmed. The key geometric dimensions, pre-tension load and fatigue load of the simulation part have been designed.

[0108] In order to ensure the normal progress of the fatigue test of the simulated part, the cross-sectional area S1 of the support end of the simulated part is at least 4 times greater than the cross-sectional area S2 of the notch of the simulated part, which can be achieved by increasing the thickness of the support end of the simulated part. Studies have shown that when the cross-sectional area of ​​the support end is 4 times greater than the cross-sectional area of ​​the notch of the simulated part, the fatigue test can be successfully completed, otherwise there is a probability that the simulated part will crack at the support end.

[0109] like Figure 5 As shown, the cross-sectional area of ​​the support end is S1 = D × T, and the cross-sectional area of ​​the notch is S2 = d × W; or the width of the support end of the simulation part can be increased, such as Figure 6 As shown, the cross-sectional area of ​​the supporting end S1 = H × d, and the cross-sectional area at the notch S2 = d × W. At this point, the design of the wheel pre-rotation simulation component is completed. In the formula, D is the width of the working end of the simulation component, T is the thickness of the supporting end of the simulation component, d is the thickness of the working end of the simulation component, W is the simulated net section width, and H is the width of the supporting end of the simulation component.

[0110] According to the design plan of the simulation part, the simulation part shall be manufactured. During the manufacturing process, the surface condition of the notch of the simulation part shall be consistent with that of the center hole of the wheel disc.

[0111] The simulated parts after processing are subjected to fatigue test. One group of simulated parts is pre-stretched first and then subjected to fatigue test; the other group is directly subjected to fatigue test. In order to make the fatigue life have reference value, the number of simulated parts in each group of fatigue test is not less than 6. The difference in fatigue life between the pre-stretched simulated parts and the non-pre-stretched simulated parts is the effect of pre-rotation on improving the fatigue life of the wheel.

[0112] Embodiment 2

[0113] like Figure 7 As shown, this embodiment provides a design system for a simulation part that takes into account the stress gradient of a wheel disc after pre-rotation, and the design system includes:

[0114] A model acquisition module 701 is used to acquire a geometric model of the pre-rotation wheel;

[0115] A parameter determination module 702 is used to determine the physical property parameters of the wheel disk preparation material at different temperatures based on the geometric model of the pre-rotated wheel disk;

[0116] The simulation module 703 is used to determine the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel based on the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material based on the finite element simulation software; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature;

[0117] An effective assessment distance calculation module 704 is used to determine the effective assessment distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel based on the stress gradient theory;

[0118] The maximum stress distribution calculation module 705 is used to determine the second maximum stress distribution according to the first maximum stress distribution and the effective test distance of the maximum principal stress of the non-pre-rotated wheel disk and the pre-rotated wheel disk; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated wheel disk and the pre-rotated wheel disk in the service condition and within the test distance along the radial direction of the wheel disk;

[0119] The design module 706 is used to design the key geometric dimensions, pre-tension load and fatigue load of the simulation part according to the second maximum stress distribution.

[0120] The effective assessment distance calculation module 704 specifically includes:

[0121] The effective assessment distance calculation submodule is used to calculate the distance according to the formula χ ef =min(χ), determine the effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk; where, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

[0122] In summary, this application has the following technical effects:

[0123] 1) This application uses theories related to fatigue life to confirm the stress assessment area of ​​the wheel disc when it is in service, and proposes a design method for a simulation component so that the stress distribution in the simulation component assessment area is consistent with that when the wheel disc is in service. Finally, the fatigue simulation component support end is designed to ensure the normal progress of the fatigue experiment.

[0124] 2) The fatigue theory considering gradient distribution is used to determine the stress assessment range of the pre-rotation wheel, making the design of the pre-rotation simulation more scientific and the predicted fatigue life more reliable.

[0125] 3) The influence of the key geometric parameters of the pre-rotation simulator on the stress distribution on the path was determined, and the design criteria for the simulator's supporting end were proposed, making the design and fatigue testing of the pre-rotation simulator more feasible.

[0126] 4) The geometry of the simulation part is relatively simple and easy to manufacture. In addition, due to its low cost, multiple sets of parallel specimens can be designed to improve the reference value of fatigue life.

[0127] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0128] This article uses specific examples to illustrate the principles and implementation methods of this application. The description of the above embodiments is only used to help understand the method and core ideas of this application. At the same time, for those skilled in the art, according to the ideas of this application, there will be changes in the specific implementation methods and application scope. In summary, the content of this specification should not be understood as limiting this application.

Claims

1. A design method for a simulation component considering the stress gradient of a pre-rotation wheel disc, characterized in that: The design method comprises: Obtaining a geometric model of a pre-rotated roulette wheel; Based on the geometric model of the pre-rotated wheel, determining the physical property parameters of the wheel preparation material at different temperatures; According to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material, based on the finite element simulation software, the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel is determined; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature; Based on the stress gradient theory, the effective test distance of the maximum principal stress of the un-pre-rotated disk and the pre-rotated disk is determined; According to the first maximum stress distribution and the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel, a second maximum stress distribution is determined; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel in the radial direction of the wheel under the service condition and within the test distance; According to the second maximum stress distribution, the key geometric dimensions, pre-tension load and fatigue load of the simulation part are designed.

2. A method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 1, characterized in that: According to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material, based on the finite element simulation software, the distribution of the maximum principal stress along the wheel radial direction of the non-pre-rotated wheel and the pre-rotated wheel at the service speed is determined, specifically including: Input the geometric model of the pre-rotated wheel disc and the physical property parameters of the wheel disc preparation material into ABAQUS finite element simulation software; The pre-rotation speed, service speed and service temperature field of the disk are set in the ABAQUS finite element simulation software, and the finite element simulation is performed to obtain the distribution of the maximum principal stress along the radial direction of the disk at the service speed for the non-pre-rotated disk and the pre-rotated disk.

3. The method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 1, characterized in that: Based on the stress gradient theory, the effective test distance of the maximum principal stress of the un-pre-rotated disk and the pre-rotated disk is determined, including: According to the formula X ef =min(X), determine the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel; in, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

4. The method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 1, characterized in that: The key geometric dimensions include the notch radius of the simulation part, the net cross-sectional width and the width of the working end of the simulation part.

5. The method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 4, characterized in that: According to the second maximum stress distribution, the key geometric dimensions, pre-tension load and fatigue load of the simulation part are designed, including: Obtaining a geometric model of a simulation component; Set the initial notch radius of the simulated part; Input the geometric model of the simulation component after setting the initial notch radius into the ABAQUS software, input the initial pre-stretching load and the initial fatigue load, and extract the distribution of the maximum principal stress of the simulation component along the path ab; Determine whether the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is consistent with the maximum stress distribution gradient of the non-pre-rotated wheel within the effective test distance; If they are inconsistent, adjust the notch radius of the simulation part and re-input the updated geometry model of the simulation part into the ABAQUS software; If they are consistent, the optimal notch radius of the simulated part is obtained; Adjust the net cross-sectional width W, working end width D and fatigue load of the simulation part, and extract the maximum principal stress distribution of the non-pre-stretched simulation part along the path ab under fatigue load; Determine whether the maximum principal stress distribution of the unstretched simulation part is consistent with the maximum principal stress distribution of the unrotated wheel within the effective assessment distance; If they are inconsistent, adjust the fatigue load of the simulation component and re-input the updated geometry model of the simulation component into the ABAQUS software; If they are consistent, the optimal fatigue load of the simulated component is obtained; Determine whether the maximum principal stress distribution of the pre-stretched simulated component under fatigue load is consistent with the maximum principal stress distribution of the pre-rotated wheel at the service speed within the effective test distance; If they are inconsistent, adjust the pre-tension load of the simulation part and re-input the updated geometric model of the simulation part into the ABAQUS software; If they are consistent, the optimal pre-tensioning load of the simulation component is obtained.

6. A method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 5, characterized in that: If not, adjust the notch radius of the simulation part and re-input the updated simulation part geometry model into the ABAQUS software, including: If the maximum stress distribution gradient of the non-pre-stretched simulation piece under fatigue load is greater than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation piece is increased; If the maximum stress distribution gradient of the non-pre-stretched simulation component under fatigue load is smaller than the maximum stress distribution gradient of the non-pre-rotated wheel, the notch radius of the simulation component is reduced.

7. The method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 5, characterized in that: If they are inconsistent, adjust the fatigue load of the simulation component and re-input the updated geometry model of the simulation component into the ABAQUS software, including: If the maximum principal stress distribution of the unpre-stretched simulation piece is less than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation piece is increased; If the maximum principal stress distribution of the unpre-stretched simulation component is greater than the maximum principal stress distribution of the unpre-rotated wheel, the fatigue load of the simulation component is reduced.

8. The method for designing a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 1, characterized in that: The physical property parameters include elastic modulus, yield strength, Poisson's ratio, density, and expansion coefficient.

9. A design system for a simulation component that takes into account the stress gradient of a pre-rotation wheel disc, characterized in that: The design system includes: A model acquisition module, used to acquire a geometric model of the pre-rotation wheel; A parameter determination module, used for determining the physical property parameters of the wheel disc preparation material at different temperatures based on the geometric model of the pre-rotated wheel disc; A simulation module, for determining the first maximum stress distribution of the non-pre-rotated wheel and the pre-rotated wheel according to the geometric model of the pre-rotated wheel and the physical property parameters of the wheel preparation material based on finite element simulation software; the first maximum stress distribution is the distribution of the maximum principal stress along the radial direction of the wheel under the service condition; the service condition includes the service speed and the service temperature; An effective test distance calculation module is used to determine the effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel based on the stress gradient theory; A maximum stress distribution calculation module is used to determine a second maximum stress distribution according to the first maximum stress distribution and an effective test distance of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel; the second maximum stress distribution is the distribution of the maximum principal stress of the non-pre-rotated wheel and the pre-rotated wheel under service conditions and within the test distance along the radial direction of the wheel; The design module is used to design the key geometric dimensions, pre-tension load and fatigue load of the simulation part according to the second maximum stress distribution.

10. A design system for a simulation component considering the stress gradient of a pre-rotation wheel disc according to claim 9, characterized in that: The effective assessment distance calculation module includes: The effective assessment distance calculation submodule is used to calculate the distance according to the formula χ ef =min(χ), determine the effective test distance of the maximum principal stress between the un-pre-rotated disk and the pre-rotated disk; where, σ(r) is the distribution of the maximum principal stress of the non-pre-rotated disk and the pre-rotated disk along the radial direction of the disk.

Images