CN114065540A - Framework modal resonance judging method based on dynamic stress, vibration and OMA (open mobile alliance) comprehensive analysis - Google Patents
Framework modal resonance judging method based on dynamic stress, vibration and OMA (open mobile alliance) comprehensive analysis Download PDFInfo
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Abstract
The invention relates to a method for comprehensively analyzing and judging framework modal resonance based on dynamic stress, vibration and OMA (open Material analysis).
Description
Technical Field
The invention relates to a framework modal resonance judging method based on dynamic stress, vibration and OMA (open mobile alliance) comprehensive analysis, and belongs to the technical field of railway vehicle bogies.
Background
At present, the phenomenon of modal resonance of the metro bogie frame in the line operation process is primarily and simply recognized at home and abroad, and the harmfulness of the modal resonance to the damage of the frame structure is also recognized. However, there is no method for determining and identifying a clearly effective modal resonance.
Currently, there are some modal identification means, such as a line operation modal test method (OMA), which can measure the modal of the bogie frame of the subway vehicle during the line operation. But the mode that appears cannot tell whether it couples with the excitation on the line and produces resonance. Therefore, it is urgently needed to research a new method for determining the modal resonance of the framework so as to accurately determine whether the modal resonance of the framework occurs in the process of operating the circuit
Disclosure of Invention
The invention provides a method for comprehensively analyzing and judging framework modal resonance based on dynamic stress, vibration and OMA (open mark analysis), which is used for comprehensively analyzing and judging whether the framework has modal resonance in the line operation or not by combining the dynamic stress level, the vibration acceleration and the OMA of a subway framework line.
The technical scheme adopted by the invention for solving the technical problems is as follows:
a method for judging framework modal resonance based on dynamic stress, vibration and OMA comprehensive analysis specifically comprises the following steps:
step S1: installing a vibration accelerometer for testing vibration acceleration on an axle box, high-mass equipment and a mounting seat of a bogie to be tested;
step S2: selecting a part with large values of stress and stress gradient on the bogie to be tested, and mounting a dynamic stress patch for dynamic stress testing;
step S3: selecting a position with a typical modal shape on the bogie to be tested and installing a vibration accelerometer for OMA test by combining a framework modal simulation result and a related structure modal test experience;
step S4: carrying out load simulation on a vehicle where the bogie to be tested is located, selecting an operation time period corresponding to the load of the vehicle, and acquiring data of the vibration accelerometer for the vibration acceleration test, the dynamic stress patch for the dynamic stress test and the vibration accelerometer for the OMA test, which are arranged in the steps S1-S3 in the running process of the vehicle;
step S5: analyzing the axle box vibration acceleration of the bogie to be tested, and carrying out Fourier transform on an axle box vibration acceleration time domain signal to obtain a power spectral density-frequency signal;
step S6: analyzing stress test data of the bogie to be tested, calculating equivalent stress amplitude of each test point by adopting a Miner linear fatigue accumulated damage rule and an S-N curve, and performing time-frequency analysis on the stress data of the stress test points with large equivalent stress amplitude;
step S7: analyzing OMA (line operation mode) test data of a bogie to be tested, performing joint analysis by adopting an enhanced frequency domain decomposition method, a random subspace method and a multi-reference-point infinite impulse response filter algorithm, and extracting modal parameters from the test data, wherein the modal parameters comprise frequency, damping and vibration mode, namely the modal frequency and the modal vibration mode of each order of the bogie to be tested;
step S8: obtaining a frequency M1 corresponding to the energy peak value of the axle box vibration acceleration of the bogie to be tested in the step S5, obtaining an obvious dominant frequency M2 of a stress measuring point with large equivalent stress amplitude in the step S6, and obtaining a corresponding frequency M3 of a modal shape of large stress generated by the stress measuring point with large equivalent stress amplitude in the step S7;
step S9: comparing the values of M1, M2 and M3, and if the following conditions are met, judging that the bogie to be tested generates modal resonance in the process of line running, specifically, judging that the bogie to be tested generates modal resonance in the process of line running
As a further preferred embodiment of the present invention, in step S3, the installed vibration accelerometers for OMA test include several vibration accelerometers, where several vibration accelerometers for OMA test cover all the elastic mode shapes within 100Hz of the bogie to be tested, and each order of mode shapes is uniquely distinguished;
specifically, the distance between adjacent accelerometers at the joints of side beams, cross beams, end beams and adjacent structures of the bogie to be tested is 0.5 m;
as a further preferred aspect of the present invention, in step S3, during the OMA test, the bogie to be tested is excited by using the wheel-rail excitation source during the vehicle running process, and the vibration response of the bogie to be tested caused by the excitation is measured;
as a further preferred method of the present invention, in step S4, the concrete method for simulating the load of the vehicle on which the bogie to be tested is located is to add sandbags to the vehicle on which the bogie to be tested is located, so that the load of the vehicle reaches C1Or C2Selecting an operation time period corresponding to the load, and acquiring data of the strain gauges and the accelerometers distributed in the steps S1 to S3 in the process of line operation;
wherein the vehicle load reaches C1The counterweight mode is as follows: one passenger per seat, the mass of the passenger is 80kg, 4-10 passengers are arranged in each square meter of the corridor and the porch, and the load of each square meter of the luggage room is 300 kg;
the load of the vehicle reaches C2The counterweight mode is as follows: one passenger per seat, the mass of the passenger is 80kg, 2-4 passengers are arranged in each square meter of the corridor and the porch, and the load of each square meter of the luggage room is 300 kg;
as a further preferred aspect of the present invention, in step S5, the axle box vibration acceleration time domain signal of the bogie to be tested is a continuous time non-periodic signal, and in practical applications, discrete sampling values x (n) of the continuous signal can be collected, fourier transformed,
wherein the content of the first and second substances,
n is 0,1, …, N-1, j is an imaginary number unit, and a power spectral density-frequency signal is obtained;
as a further preferred aspect of the present invention, the test specimen is analyzed in step S6Calculating the equivalent stress amplitude sigma of each measuring point by adopting Miner linear fatigue accumulated damage rule and S-N curve according to stress test data of the frameaeqWherein, the actual measurement kilometer number L of a stress spectrum is calculated and tested by a Miner linear fatigue accumulation damage rule1The internally generated damage is formulated as
The equivalent stress amplitude is acted for a plurality of times, and the damage formula generated by the bogie to be tested is as follows
If the safe operation mileage causing damage is set to be L kilometers, the safe operation mileage is set to be L kilometers
Substituting the formula (6.1) and the formula (6.2) into the formula (6.3) to obtain
Finally obtaining an equivalent stress amplitude;
wherein L is1The measured kilometers of a stress spectrum is generally the total mileage of a dynamic stress test; d1Is L1Damage due to a stress spectrum in kilometers; l is the safe operation mileage which is set to generate damage, namely the total mileage of the bogie to be tested; n is the number of times of the equivalent stress amplitude action set in the formula (6.2), namely the number of cycles corresponding to the fatigue limit; d is the damage generated by the bogie to be tested in the formula (6.2); n isiThe stress cycle times corresponding to each level of stress level; m is the index of an S-N curve, the cast steel material is 6.5, and the welding joint is 3.5; sigma-1aiThe amplitude of each stress level;
as a further preferred aspect of the present invention, by the obtained stress time domain data of the stress measuring point with large equivalent stress amplitude, the stress measuring point with large equivalent stress amplitude is a dangerous position measuring point, and a fourier transform is performed every fixed period of time to obtain a curve of dynamic stress frequency transformed with time, and the curve is continuously displayed in a graph to obtain the whole main frequency;
as a further preferred embodiment of the present invention, in step S7, OMA test data of the bogie to be tested is analyzed, and the specific steps of the adopted multi-reference-point infinite impulse response filtering algorithm are that the known impulse response function h (k) has an n-order mode and a structural frequency response function of
Wherein z is ejωΔtΔ t is a sampling interval, l is a waveform point number or length, N is 2N, j is an imaginary unit, and ω is;
deducing a characteristic equation coefficient by using a formula (7.1) to obtain a characteristic value of a characteristic equation, so as to obtain modal frequency and damping and extract a modal vibration mode;
as a further preferred embodiment of the present invention, in step S7, OMA test data of the bogie to be tested is analyzed, and the random subspace method is specifically implemented by using a linear system with n degrees of freedom, and the discrete filling space equation is:
{xk+1}＝[A]{xk}+{wk} (7.2)
{yk}＝[C]{xk}+{vk} (7.3)
wherein, { xkIs an n-dimensional state vector, { ykIs an N-dimensional output vector, N being the number of response points; { wkAnd { v } andkinput and output white noise with mean 0, respectively; [ A ]]And [ C]Respectively representing an N × N order state matrix and an N × N order output matrix, and solving to obtain [ A]And [ C]The modal parameters can be identified;
as a further preferred embodiment of the present invention, in step S7, OMA test data of the bogie to be tested is analyzed, and the specific steps of the enhanced frequency domain decomposition method adopted are that, assuming that x (t) is unknown unmeasured excitation, y (t) is measured response data, then the power spectrum array of the response, i.e. m × m order, m is the number of the measuring points:
wherein the power spectrum array of the response is of an m multiplied by m order, and m is the number of the measuring points; gxx(j omega) is a power spectrum array of x (t), namely r multiplied by r, and r is the number of excitation points; h (j omega) is an m multiplied by r order frequency response function matrix; the upper corner of the matrix is marked "-".T"distribution means complex conjugation and transposition; when K is constant, dkIs a constant, λkIs the pole of K order;
when ω is ω ═ ωiThen, G is estimated from the formula (7.4)yy(j omega), then carrying out singular value decomposition on the power spectrum to decompose the power spectrum into a single-degree-of-freedom system power spectrum corresponding to a multi-order mode;
when the K-order mode is the main mode, the formula (7.4) has only one term, and the mode shape is
Wherein the frequency and the damping are obtained from the logarithmic attenuation of the single degree of freedom correlation function corresponding to the mode shape.
Through the technical scheme, compared with the prior art, the invention has the following beneficial effects:
the method is based on dynamic stress, vibration and OMA, comprehensively analyzes the mode of the bogie frame of the subway vehicle in the line operation, and can accurately judge whether the mode is resonance generated by coupling with excitation on the line.
Drawings
The invention is further illustrated with reference to the following figures and examples.
FIG. 1 is a graph of power spectral density versus frequency signals obtained when analyzing axle box vibration acceleration of a truck under test, in accordance with a preferred embodiment of the present invention;
FIG. 2 is a graph of dynamic stress frequency versus time obtained when analyzing stress test data for a truck under test according to a preferred embodiment of the present invention;
fig. 3-4 are modal diagrams of different angles that the present invention provides for when analyzing OMA test data for a truck under test.
Detailed Description
The present invention will now be described in further detail with reference to the accompanying drawings. In the description of the present application, it is to be understood that the terms "left side", "right side", "upper part", "lower part", etc., indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and that "first", "second", etc., do not represent an important degree of the component parts, and thus are not to be construed as limiting the present invention. The specific dimensions used in the present example are only for illustrating the technical solution and do not limit the scope of protection of the present invention.
As explained in the background art, some existing mode identification means cannot accurately judge whether each mode is coupled with excitation on a line to generate resonance; because the present application aims to provide a completely new method for determining framework modal resonance, the principle is to comprehensively analyze the dynamic stress level, the vibration acceleration and the OMA of the metro framework line, and the determination method has high accuracy and remarkable effect.
The method specifically comprises the following steps:
step S1: installing a vibration accelerometer for testing vibration acceleration on an axle box, high-mass equipment and a mounting seat of a bogie to be tested; in the field of rail transit, only vibration transmission reference is generally made to vibration acceleration test data of the axle box, namely the vibration transmission rate of the axle box to a framework and even a vehicle body; however, it is common in the art to recognize that excitation of the rail in a fixed frequency band may excite the natural frequency of a part of the bogie, and thus the dominant frequency of the axle box vibration acceleration is identified.
Step S2: selecting a part with large values of stress and stress gradient on the bogie to be tested, and mounting a dynamic stress patch for dynamic stress testing;
step S3: selecting a position with a typical modal shape on the bogie to be tested and installing a vibration accelerometer for OMA test by combining a framework modal simulation result and a related structure modal test experience;
step S4: carrying out load simulation on a vehicle where the bogie to be tested is located, selecting an operation time period corresponding to the load of the vehicle, and acquiring data of the vibration accelerometer for the vibration acceleration test, the dynamic stress patch for the dynamic stress test and the vibration accelerometer for the OMA test, which are arranged in the steps S1-S3 in the running process of the vehicle;
step S5: analyzing the axle box vibration acceleration of the bogie to be tested, and carrying out Fourier transform on an axle box vibration acceleration time domain signal to obtain a power spectral density-frequency signal;
step S6: analyzing stress test data of the bogie to be tested, calculating equivalent stress amplitude of each test point by adopting a Miner linear fatigue accumulated damage rule and an S-N curve, and performing time-frequency analysis on the stress data of the stress test points with large equivalent stress amplitude;
step S7: analyzing OMA test data of a bogie to be tested, performing combined analysis by adopting an enhanced frequency domain decomposition method, a random subspace method and a multi-reference-point infinite impulse response filter algorithm, and extracting modal parameters from the test data, wherein the modal parameters comprise frequency, damping and vibration mode, namely modal frequency and modal vibration mode of each order of the bogie to be tested;
step S8: obtaining a frequency M1 corresponding to the energy peak value of the axle box vibration acceleration of the bogie to be tested in the step S5, obtaining an obvious dominant frequency M2 of a stress measuring point with large equivalent stress amplitude in the step S6, and obtaining a corresponding frequency M3 of a modal shape of large stress generated by the stress measuring point with large equivalent stress amplitude in the step S7;
step S9: comparing the values of M1, M2 and M3, and if the following conditions are met, judging that the bogie to be tested generates modal resonance in the process of line running, specifically, judging that the bogie to be tested generates modal resonance in the process of line running
In step S3, the installed vibration accelerometers for OMA test include a plurality of vibration accelerometers (the number of vibration accelerometers is enough), the vibration accelerometers for OMA test cover all the elastic mode shapes within 100Hz of the bogie to be tested, and each order of mode shapes is uniquely distinguished; when the OMA test is carried out, a wheel track excitation source in the running process of a vehicle is adopted to excite the bogie to be tested, and the vibration response of the bogie to be tested caused by excitation is measured.
Specifically, at the junction of a side beam, a cross beam, an end beam and an adjacent structure of a bogie to be tested, the distance between adjacent accelerometers is 0.5m, namely, one accelerometer needs to be arranged every 0.5m, and the accelerometers also need to be arranged at positions such as a large-mass suspension equipment mounting seat, so as to improve the measurement accuracy.
The concrete method for simulating the load of the vehicle where the bogie to be tested is positioned in the step S4 is that a sandbag is added to the vehicle where the bogie to be tested is positioned, and the load of the vehicle reaches C1Or C2Selecting an operation time period corresponding to the load, and acquiring data of the strain gauges and the accelerometers distributed in the steps S1 to S3 in the process of line operation;
wherein the vehicle load reaches C1The counterweight mode is as follows: one passenger per seat, the mass of the passenger is 80kg, 4-10 passengers are arranged in each square meter of the corridor and the porch, and the load of each square meter of the luggage room is 300 kg;
the load of the vehicle reaches C2The counterweight mode is as follows: one passenger per seat, with a passenger mass of 80kg, 2-4 passengers per square meter in corridors and porches, with a load of 300kg per square meter of luggage compartment.
In step S5, wait forThe axle box vibration acceleration time domain signal of the test bogie is a continuous time aperiodic signal, and in practical application, discrete sampling values x (n) of the continuous signal can be collected and subjected to Fourier transform,
wherein the content of the first and second substances,
n-0, 1, …, N-1, j being imaginary units, the power spectral density versus frequency signal shown in fig. 1 is obtained.
Analyzing stress test data of the bogie to be tested in the step S6, and calculating equivalent stress amplitude sigma of each test point by using Miner linear fatigue accumulated damage rule and S-N curveaeqWherein, the actual measurement kilometer number L of a stress spectrum is calculated and tested by a Miner linear fatigue accumulation damage rule1The internally generated damage is formulated as
The equivalent stress amplitude is acted for a plurality of times, and the damage formula generated by the bogie to be tested is as follows
If the safe operation mileage causing damage is set to be L kilometers, the safe operation mileage is set to be L kilometers
Substituting the formula (6.1) and the formula (6.2) into the formula (6.3) to obtain
Finally obtaining an equivalent stress amplitude;
wherein，L1The measured kilometers of a stress spectrum is generally the total mileage of a dynamic stress test; d1Is L1Damage due to a stress spectrum in kilometers; l is the safe operation mileage which is set to generate damage, namely the total mileage of the bogie to be tested; n is the number of times of equivalent stress amplitude action set in the formula (6.2), namely the number of cycles corresponding to the fatigue limit, and 200 ten thousand times is taken here (the welding joint is generally 200 ten thousand times, and the base metal is 1000 ten thousand times); d is the damage generated by the bogie to be tested in the formula (6.2); n isiThe stress cycle times corresponding to each level of stress level; m is the index of an S-N curve, the cast steel material is 6.5, and the welding joint is 3.5; sigma-1aiIs the magnitude of the stress level at each stage. According to the stress time domain data of the stress measuring points with large equivalent stress amplitudes, which are obtained in the previous step, the stress measuring points with large equivalent stress amplitudes are dangerous position measuring points, Fourier transform is performed at fixed intervals to obtain a curve of dynamic stress frequency along with time transform, the curve is continuously displayed in a graph, and the whole main frequency of the curve is obtained as shown in FIG. 2. It is important to explain why multiple fourier transforms are required because for dynamic stress testing, it is common practice in the industry to arrange strain gages on the structure, extract the structural strain, convert it to stress, and evaluate whether the fatigue strength of the structure meets the requirements. This patent is thought that fatigue failure takes place for the structure, and it is not necessarily because structure stress is big itself, also can be because structure natural frequency is excited by the track and is aroused in the vehicle operation in-process, produces modal resonance, has enlarged structural stress to a certain extent, has increased fatigue cycle number and has caused.
In step S7, analyzing OMA test data of the bogie to be tested, wherein a multi-reference-point infinite impulse response filter algorithm (PolyIIR) is adopted, and the method specifically comprises the steps of knowing an impulse response function h (k) with an n-order mode and a frequency response function of the structure of the known impulse response function h (k)
Wherein z is ejωΔtAnd Δ t is the sampling interval,l is the number of waveform points or the length, N is 2N, j is an imaginary unit, and omega is;
and (3) deducing the coefficient of the characteristic equation by the formula (7.1) to obtain the characteristic value of the characteristic equation, so as to obtain the modal frequency and the damping and extract the modal shape.
The adopted random subspace method (SSI) specifically comprises the following steps of a linear system with the degree of freedom n, and a discrete filling space equation of the linear system is as follows:
{xk+1}＝[A]{xk}+{wk} (7.2)
{yk}＝[C]{xk}+{vk} (7.3)
wherein, { xkIs an n-dimensional state vector, { ykIs an N-dimensional output vector, N being the number of response points; { wkAnd { v } andkinput and output white noise with mean 0, respectively; [ A ]]And [ C]Respectively representing an N × N order state matrix and an N × N order output matrix, and solving to obtain [ A]And [ C]The modal parameters can be identified.
The adopted enhanced frequency domain decomposition method (EFDD) specifically comprises the following steps of assuming that x (t) is unknown excitation which cannot be measured, y (t) is measured response data, a response power spectrum array, namely m multiplied by m, and m is the number of measuring points:
wherein the power spectrum array of the response is of an m multiplied by m order, and m is the number of the measuring points; gxx(j omega) is a power spectrum array of x (t), namely r multiplied by r, and r is the number of excitation points; h (j omega) is an m multiplied by r order frequency response function matrix; the upper corner of the matrix is marked "-".T"distribution means complex conjugation and transposition; when K is constant, dkIs a constant, λkIs the pole of K order;
when ω is ω ═ ωiThen, G is estimated from the formula (7.4)yy(j omega), then carrying out singular value decomposition on the power spectrum to decompose the power spectrum into a single-degree-of-freedom system power spectrum corresponding to a multi-order mode;
when the K-order mode is the main mode, the formula (7.4) has only one term, and the mode shape is
The frequency and the damping are obtained from the logarithmic attenuation of the single-degree-of-freedom correlation function corresponding to the mode shape, as shown in fig. 3-4.
In summary, the vibration acceleration test, the dynamic stress test and the OMA test used in the specific implementation process of the method are all test means used conventionally, but the processing of test acquisition data is different from the conventional operation, so that whether modal resonance occurs in the operation of the framework on a line can be accurately judged, and the method is suitable for being widely popularized on subway vehicles.
It will be understood by those skilled in the art that, unless otherwise defined, all terms (including technical and scientific terms) used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. It will be further understood that terms, such as those defined in commonly used dictionaries, should be interpreted as having a meaning that is consistent with their meaning in the context of the prior art and will not be interpreted in an idealized or overly formal sense unless expressly so defined herein.
The meaning of "and/or" as used herein is intended to include both the individual components or both.
The term "connected" as used herein may mean either a direct connection between components or an indirect connection between components via other components.
In light of the foregoing description of the preferred embodiment of the present invention, many modifications and variations will be apparent to those skilled in the art without departing from the spirit and scope of the invention. The technical scope of the present invention is not limited to the content of the specification, and must be determined according to the scope of the claims.
Claims (10)
1. A method for judging framework modal resonance based on dynamic stress, vibration and OMA comprehensive analysis is characterized in that: the method specifically comprises the following steps:
step S1: installing a vibration accelerometer for testing vibration acceleration on an axle box, high-mass equipment and a mounting seat of a bogie to be tested;
step S2: selecting a part with large values of stress and stress gradient on the bogie to be tested, and mounting a dynamic stress patch for dynamic stress testing;
step S3: selecting a position with a typical modal shape on the bogie to be tested and installing a vibration accelerometer for OMA test by combining a framework modal simulation result and a related structure modal test experience;
step S4: carrying out load simulation on a vehicle where the bogie to be tested is located, selecting an operation time period corresponding to the load of the vehicle, and acquiring data of the vibration accelerometer for the vibration acceleration test, the dynamic stress patch for the dynamic stress test and the vibration accelerometer for the OMA test, which are arranged in the steps S1-S3 in the running process of the vehicle;
step S5: analyzing the axle box vibration acceleration of the bogie to be tested, and carrying out Fourier transform on an axle box vibration acceleration time domain signal to obtain a power spectral density-frequency signal;
step S6: analyzing stress test data of the bogie to be tested, calculating equivalent stress amplitude of each test point by adopting a Miner linear fatigue accumulated damage rule and an S-N curve, and performing time-frequency analysis on the stress data of the stress test points with large equivalent stress amplitude;
step S7: analyzing OMA test data of a bogie to be tested, performing combined analysis by adopting an enhanced frequency domain decomposition method, a random subspace method and a multi-reference-point infinite impulse response filter algorithm, and extracting modal parameters from the test data, wherein the modal parameters comprise frequency, damping and vibration mode, namely modal frequency and modal vibration mode of each order of the bogie to be tested;
step S8: obtaining a frequency M1 corresponding to the energy peak value of the axle box vibration acceleration of the bogie to be tested in the step S5, obtaining an obvious dominant frequency M2 of a stress measuring point with large equivalent stress amplitude in the step S6, and obtaining a corresponding frequency M3 of a modal shape of large stress generated by the stress measuring point with large equivalent stress amplitude in the step S7;
step S9: comparing the values of M1, M2 and M3, and if the following conditions are met, judging that the bogie to be tested generates modal resonance in the process of line running, specifically, judging that the bogie to be tested generates modal resonance in the process of line running
2. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: in the step S3, the installed vibration accelerometers for OMA test include a plurality of vibration accelerometers, the vibration accelerometers for OMA test cover all elastic modal vibration modes within 100Hz of the bogie to be tested, and each order of modal vibration modes are uniquely distinguished;
specifically, the distance between adjacent accelerometers at the junctions of the side beams, cross beams, end beams and adjacent structures of the bogie to be tested is 0.5 m.
3. The method of determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis of claim 2, wherein: in step S3, during an OMA test, the bogie to be tested is excited by using a wheel-rail excitation source during the running of the vehicle, and the vibration response of the bogie to be tested caused by the excitation is measured.
4. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: the concrete method for simulating the load of the vehicle where the bogie to be tested is positioned in the step S4 is that a sandbag is added to the vehicle where the bogie to be tested is positioned, and the load of the vehicle reaches C1Or C2Selecting an operation time period corresponding to the load, and acquiring data of the strain gauges and the accelerometers distributed in the steps S1 to S3 in the process of line operation;
wherein the vehicle load reaches C1The counterweight mode is as follows: one passenger per seat, passengerThe weight is 80kg, 4-10 passengers are in the corridor and the porch per square meter, and the load of each square meter of luggage room is 300 kg;
the load of the vehicle reaches C2The counterweight mode is as follows: one passenger per seat, with a passenger mass of 80kg, 2-4 passengers per square meter in corridors and porches, with a load of 300kg per square meter of luggage compartment.
5. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: in step S5, the axle box vibration acceleration time domain signal of the bogie to be tested is a continuous time non-periodic signal,
in practical applications, discrete sample values x (n) of a continuous signal can be acquired, fourier transformed,
wherein the content of the first and second substances,
n is 0,1, …, N-1, j is an imaginary unit, and a power spectral density-frequency signal is obtained.
6. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: analyzing stress test data of the bogie to be tested in the step S6, and calculating equivalent stress amplitude sigma of each test point by using Miner linear fatigue accumulated damage rule and S-N curveaeqWherein, the actual measurement kilometer number L of a stress spectrum is calculated and tested by a Miner linear fatigue accumulation damage rule1The internally generated damage is formulated as
The equivalent stress amplitude is acted for a plurality of times, and the damage formula generated by the bogie to be tested is as follows
If the safe operation mileage causing damage is set to be L kilometers, the safe operation mileage is set to be L kilometers
Substituting the formula (6.1) and the formula (6.2) into the formula (6.3) to obtain
Finally obtaining an equivalent stress amplitude;
wherein L is1The measured kilometers of a stress spectrum is generally the total mileage of a dynamic stress test; d1Is L1Damage due to a stress spectrum in kilometers; l is the safe operation mileage which is set to generate damage, namely the total mileage of the bogie to be tested; n is the number of times of the equivalent stress amplitude action set in the formula (6.2), namely the number of cycles corresponding to the fatigue limit; d is the damage generated by the bogie to be tested in the formula (6.2); n isiThe stress cycle times corresponding to each level of stress level; m is the index of an S-N curve, the cast steel material is 6.5, and the welding joint is 3.5; sigma-1aiIs the magnitude of the stress level at each stage.
7. The method of claim 6 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: and performing Fourier transform at fixed intervals by using the stress time domain data of the stress measuring points with large equivalent stress amplitudes, namely the dangerous position measuring points, to obtain a curve of dynamic stress frequency along with time transform, and continuously displaying the curve in a graph to obtain the whole main frequency of the curve.
8. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: in step S7, OMA test data of the bogie to be tested is analyzed, and the adopted multi-reference-point infinite-length impulse response filtering algorithm specifically comprises the steps of knowing an impulse response function h (k) with an n-order mode and a frequency response function of the structure of n
Wherein z is ejωΔtΔ t is a sampling interval, l is a waveform point number or length, N is 2N, j is an imaginary unit, and ω is;
and (3) deducing the coefficient of the characteristic equation by the formula (7.1) to obtain the characteristic value of the characteristic equation, so as to obtain the modal frequency and the damping and extract the modal shape.
9. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: in step S7, analyzing OMA test data of the bogie to be tested, wherein the random subspace method specifically includes the following steps:
{xk+1}＝[A]{xk}+{wk} (7.2)
{yk}＝[C]{xk}+{vk} (7.3)
wherein, { xkIs an n-dimensional state vector, { ykIs an N-dimensional output vector, N being the number of response points; { wkAnd { v } andkinput and output white noise with mean 0, respectively; [ A ]]And [ C]Respectively representing an N × N order state matrix and an N × N order output matrix, and solving to obtain [ A]And [ C]The modal parameters can be identified.
10. The method of claim 1 for determining framework modal resonance based on dynamic stress, vibration and OMA integrated analysis, wherein: in step S7, analyzing OMA test data of the bogie to be tested, wherein the enhanced frequency domain decomposition method includes the specific steps of assuming that x (t) is unknown excitation which cannot be measured, y (t) is measured response data, then a power spectrum array of the response, i.e. m × m order, and m is the number of the measuring points:
wherein the power spectrum array of the response is of an m multiplied by m order, and m is the number of the measuring points; gxx(j omega) is a power spectrum array of x (t), namely r multiplied by r, and r is the number of excitation points; h (j omega) is an m multiplied by r order frequency response function matrix; the prime "-" T "distribution of the matrix represents complex conjugation and transposition; when K is constant, dkIs a constant, λkIs the pole of K order;
when ω is ω ═ ωiThen, G is estimated from the formula (7.4)yy(j omega), then carrying out singular value decomposition on the power spectrum to decompose the power spectrum into a single-degree-of-freedom system power spectrum corresponding to a multi-order mode;
when the K-order mode is the main mode, the formula (7.4) has only one term, and the mode shape is
Wherein the frequency and the damping are obtained from the logarithmic attenuation of the single degree of freedom correlation function corresponding to the mode shape.
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