CN114912203A - Dynamic simulation analysis method for electric drive system - Google Patents
Dynamic simulation analysis method for electric drive system Download PDFInfo
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Abstract
The invention belongs to the technical field of electric vehicles, and discloses a dynamic simulation analysis method of an electric drive system, which comprises the steps of calculating the dynamic meshing stiffness of a gear pair, the dynamic meshing force of ith harmonic wave of the gear pair, the inherent frequency and the modal shape of the system nth order; determining the harmonic order of the larger vibration acceleration response under each excitation; determining the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system; the portion occupying the main strain energy is contrasted and analyzed; comparing and analyzing the resonance position and amplitude of the ODS vibration mode of the system under the natural frequency of each resonance peak, and identifying the resonance position; the order and natural frequencies occupying the dominant radiated acoustic power are identified. The invention fully considers the input, output and analysis processes of the model, improves the precision and the system integration level of the simulation model of the shaft tooth performance, and improves the calculation efficiency and the accuracy of the calculation and analysis result.
Description
Technical Field
The invention relates to the technical field of electric vehicles, in particular to a dynamic simulation analysis method of an electric drive system.
Background
In a traditional internal combustion engine automobile, engine noise well covers vibration noise of a gear transmission system, but in a pure electric automobile, electromagnetic noise and gear order noise are highlighted due to the lack of the engine noise masking effect. The rotating speed of a high-speed driving motor of an existing electric driving system is generally as high as 12000-18000 r/min, and is expected to be further improved in the future. High rotating speed causes high-frequency squeal, the dynamic response frequency of an electric drive system is further improved to 2-5 kHz, and the frequency is within the sensitive frequency range of human ears, so that the riding comfort of an automobile is seriously influenced. With the development of an electric drive system of a pure electric vehicle, the NVH problem existing in a high-speed and integrated transmission system is more complicated.
The electric drive system forms complex dynamic response under the action of a plurality of vibration excitation sources, however, the vibration excitation sources input by the current model are not considered fully, the structural vibration output by the current model is not considered fully, and the analysis process is not comprehensive, so that the problems of low precision of the shaft tooth performance simulation model, low system integration level, low calculation efficiency, inaccurate calculation and analysis results and the like are caused.
Therefore, a method for analyzing the dynamics simulation of the electric drive system is needed to solve the above existing problems.
Disclosure of Invention
The invention aims to provide a dynamic simulation analysis method of an electric drive system, which fully considers the input, output and analysis processes of a model, improves the precision and the system integration level of a simulation model of the shaft tooth performance, and improves the calculation efficiency and the accuracy of a calculation analysis result.
In order to achieve the purpose, the invention adopts the following technical scheme:
a method of electric drive system dynamics simulation analysis, comprising:
calculating the dynamic meshing stiffness of the gear pair;
calculating the dynamic meshing force of the ith harmonic of the gear pair based on the dynamic meshing stiffness of the gear pair;
calculating the natural frequency and the modal shape of the nth order of the system;
calculating the vibration acceleration response of each excitation at the bearing support seat of the dynamic model shell under the attention working condition based on the dynamic meshing stiffness of the gear pair, the dynamic meshing force analysis of the gear pair, the inherent frequency of the system and the modal shape, fitting and comparing and analyzing a noise waterfall diagram, and determining the harmonic order of the larger vibration acceleration response under each excitation;
calculating a vibration acceleration response slice at the bearing support of the shell caused by response excitation based on the analysis result of the harmonic order of the larger vibration acceleration response under each excitation, fitting and comparing and analyzing the peak value of each excitation vibration acceleration response slice, and determining the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system;
calculating the strain energy distribution of the electric drive system based on the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system, and performing comparative analysis on the part occupying the main strain energy;
calculating the ODS vibration mode occupying the main strain energy at the larger formant of the order slice of the electric drive system, and comparing and analyzing the resonance position and amplitude of the ODS vibration mode of the system under the natural frequency of each formant to identify the resonance position;
and calculating and fitting a shell radiation sound power curve under the concerned working condition and each excitation, comparing and analyzing the peak value position and the peak value size of the radiation sound power curve of each order under each excitation coupling, and identifying the order and the inherent frequency occupying the main radiation sound power.
In some possible embodiments, when calculating the gear pair dynamic mesh stiffness, the method comprises:
calculating the meshing rigidity of the primary gear pair;
and calculating the meshing rigidity of the secondary gear pair.
In some possible embodiments, when calculating the gear pair dynamic meshing force, the method comprises:
calculating the dynamic meshing force of the primary gear pair;
and calculating the dynamic meshing force of the secondary gear pair.
In some possible embodiments, when calculating the natural frequency and the mode shape of the system, the method includes:
calculating a modal vibration mode under the excitation of the transmission error of the first-stage gear pair;
calculating the modal vibration mode under the excitation of the transmission error of the secondary gear pair;
calculating a modal vibration mode under the excitation of motor torque fluctuation;
and calculating the mode vibration mode under the excitation of the radial electromagnetic force of the motor.
In some possible embodiments, when calculating the vibrational acceleration response at the dynamical model shell bearing support seat of each excitation under the operating condition of interest, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the electromagnetic force excitation in the radial direction of the motor.
In some possible embodiments, when computing a vibrational acceleration response slice at the housing bearing support caused in response to the excitation, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
In some possible embodiments, when calculating the strain energy distribution of the electric drive system, includes:
strain energy distribution of the shell system;
strain energy distribution of the shaft tooth system.
In some possible embodiments, when identifying the resonance location, the method includes:
the resonance position of the housing system or the shaft-tooth system is identified.
In some possible embodiments, when calculating and fitting the case radiated acoustic power curve under the operating condition of interest and each excitation, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
In some possible embodiments, after identifying the order and the natural frequency occupying the main radiated acoustic power, the method further includes:
comparing the radiated sound power simulation result with the experimental result under the same working condition, wherein the comparison content comprises the following steps: the integral variation trend of the order curve along with the rotating speed, the rotating speed of the peak position of the order curve and the decibel value of the peak position of the order curve;
and the simulation result of the radiation acoustic power of the shell is consistent with the experimental result by calibrating the damping coefficient of each mode of the system.
The invention has the beneficial effects that:
according to the dynamic simulation analysis method for the electric drive system, the influence of a plurality of excitation sources such as transmission errors of a motor and a gear on the electric drive system is fully considered by calculating the dynamic meshing stiffness of the gear pair, the harmonic dynamic meshing force of the gear pair, the natural frequency of the system and the modal shape, so that the vibration excitation source input by a model is considered comprehensively. By sequentially analyzing noise waterfall patterns under various excitations, vibration acceleration slice analysis of the concerned orders, strain energy analysis of an electric drive system, ODS vibration pattern analysis at the resonance peak of the order slice, and shell radiation sound power analysis, the output of structural vibration is fully considered, and comprehensive flow analysis is performed according to the analysis steps, so that the precision of a shaft tooth performance simulation model, the system integration level, the calculation efficiency and the accuracy of the calculation and analysis results are improved, the whole modeling and analysis process has strong universality, and the method can be widely applied to the dynamics analysis of the electric drive system.
Drawings
Fig. 1 is a flowchart of a simulation analysis method for dynamics of an electric drive system according to an embodiment of the present invention.
Detailed Description
In order to make the technical problems solved, technical solutions adopted and technical effects achieved by the present invention clearer, the technical solutions of the embodiments of the present invention will be described in further detail below with reference to the accompanying drawings, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
In the description of the present invention, unless expressly stated or limited otherwise, the terms "connected," "connected," and "fixed" are to be construed broadly, e.g., as meaning permanently connected, removably connected, or integral to one another; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
In the present invention, unless otherwise expressly stated or limited, "above" or "below" a first feature means that the first and second features are in direct contact, or that the first and second features are not in direct contact but are in contact with each other via another feature therebetween. Also, the first feature being "on," "above" and "over" the second feature includes the first feature being directly on and obliquely above the second feature, or merely indicating that the first feature is at a higher level than the second feature. A first feature being "under," "below," and "beneath" a second feature includes the first feature being directly under and obliquely below the second feature, or simply meaning that the first feature is at a lesser elevation than the second feature.
Through analysis, complex dynamic response formed by an electric drive system under the action of a plurality of vibration excitation sources comprises the following two aspects, one is that under different working conditions and with factors such as machining and manufacturing errors, the gear has a dislocation amount during meshing, and the dislocation amount of the gear meshing and the deformation amount generated by tooth surface contact can cause the transmission error and the fluctuation dislocation amount of a gear pair, so that the dynamic meshing force of the gear can be caused; secondly, the motor has radial, axial and tangential periodic excitation loads; when the motor drives the speed reducer, the periodic excitation load of the motor and the dynamic meshing force of the gear act together to form dynamic response, and the dynamic response is transmitted to the mounting points such as the shell, the bearing seat support and the like to form dynamic response, so that structural vibration and air noise are caused.
The embodiment provides a dynamic simulation analysis method of an electric drive system, as shown in fig. 1, including the following steps:
s1: calculating the dynamic meshing stiffness of the gear pair;
s2: calculating the dynamic meshing force of the ith harmonic of the gear pair based on the dynamic meshing stiffness of the gear pair;
s3: calculating the natural frequency and the modal shape of the nth order of the system;
s4: calculating the vibration acceleration response of each excitation at the bearing support seat of the dynamic model shell under the attention working condition based on the dynamic meshing stiffness of the gear pair, the dynamic meshing force analysis of the gear pair, the inherent frequency of the system and the modal shape, fitting and comparing and analyzing a noise waterfall diagram, and determining the harmonic order of the larger vibration acceleration response under each excitation;
s5: calculating a vibration acceleration response slice at the bearing support of the shell caused by response excitation based on the analysis result of the harmonic order of the larger vibration acceleration response under each excitation, fitting and comparing and analyzing the peak value of each excitation vibration acceleration response slice, and determining the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system;
s6: calculating the strain energy distribution of the electric drive system based on the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system, and performing comparative analysis on the part occupying the main strain energy;
s7: calculating the ODS vibration mode occupying the main strain energy at the larger formant of the order slice of the electric drive system, and comparing and analyzing the resonance position and amplitude of the ODS vibration mode of the system under the natural frequency of each formant to identify the resonance position;
s8: and calculating and fitting a shell radiation sound power curve under the concerned working condition and each excitation, comparing and analyzing the peak value position and the peak value size of the radiation sound power curve of each order under each excitation coupling, and identifying the order and the inherent frequency occupying the main radiation sound power.
By calculating the dynamic meshing stiffness of the gear pair, the harmonic dynamic meshing force of the gear pair, the natural frequency of the system and the modal shape, the influence of a plurality of excitation sources such as transmission errors of a motor and a gear on an electric drive system is fully considered, so that the vibration excitation source input by the model is considered comprehensively. By sequentially analyzing noise waterfall patterns under various excitations, vibration acceleration slice analysis of the concerned orders, strain energy analysis of an electric drive system, ODS vibration pattern analysis at the resonance peak of the order slice, and shell radiation sound power analysis, the output of structural vibration is fully considered, and comprehensive flow analysis is performed according to the analysis steps, so that the precision of a shaft tooth performance simulation model, the system integration level, the calculation efficiency and the accuracy of the calculation and analysis results are improved, the whole modeling and analysis process has strong universality, and the method can be widely applied to the dynamics analysis of the electric drive system.
Specifically, in step S1, the dynamic meshing stiffness refers to a dynamic force calculated when the meshing gear is excited by a sinusoidal transmission error of a unit micron size, and is a gear tooth meshing stiffness that dynamically changes as the gear meshing frequency ω changes. The calculation is based on the calculation formula in the prior art:
ω＝n/60*Z；
D(ω)＝C(ω)-1；
C(ω)＝C1(ω)+C2(ω)；
wherein: n is the rotating speed, Z is the number of teeth, omega is the gear meshing frequency, the unit is HZ, D (omega) is the dynamic meshing rigidity on the gear meshing line when the frequency is omega, C (omega) is the total flexibility of the two gears, C1 (omega) and C2 (omega) are the flexibility of the main gear and the auxiliary gear on the meshing line.
Further specifically, step S1 includes:
s11: calculating the meshing rigidity of the primary gear pair;
s12: and calculating the meshing rigidity of the secondary gear pair.
And respectively calculating the meshing rigidity of the primary gear pair and the secondary gear pair so as to fully consider the vibration excitation source in the speed reducer.
Specifically, in step S2, the dynamic meshing force of the gear pair is the tooth dynamic force calculated when the meshing gear pair is excited by the harmonic of the static transmission error. The calculation is based on the calculation formula in the prior art:
Fi(ω)＝D(ω)*δi；
wherein: fi (omega) is the dynamic meshing force of the ith harmonic of the gear transmission error, and delta i is the ith harmonic of the gear meshing transmission error.
Further specifically, step S2 includes:
s21: calculating the dynamic meshing force of the primary gear pair;
s22: and calculating the dynamic meshing force of the secondary gear pair.
And respectively calculating the dynamic meshing force of the primary gear pair and the secondary gear pair so as to fully consider the vibration excitation source in the speed reducer. Specifically, the attention order harmonic may be calculated according to actual conditions, and is not limited.
Specifically, in step S3, the mode is a natural vibration characteristic of the structural system. The free vibration of the linear system is decoupled into N orthogonal single degree of freedom vibration systems, corresponding to the N modes of the system. Each mode has a specific natural frequency, damping ratio and mode shape. The electric drive system is an elastic vibration system with multiple degrees of freedom, and the modal vibration modes of the electric drive system are overall vibration modes such as torsion, bending and swinging of the whole system. The calculation is based on the calculation formula in the prior art:
(K-ω2rM)φr＝0；
wherein: ω r is the r-th order natural frequency, φ r is the r-th order natural mode, M is the mass matrix, and K is the stiffness matrix.
The above formula requires that the eigenvector phir corresponding to the eigenvalue omega r is orthogonal, and the mass matrix M and the stiffness matrix K of the system are orthogonal at the same time, so that the natural frequency and the mode shape of the system can be obtained.
Specifically, the attention order harmonic may be calculated according to actual conditions, and is not limited.
As can be seen from the previous data analysis and model analysis, the motor torque ripple excitation and the radial electromagnetic force excitation have a large influence on the vibration, and in this embodiment, step S3 includes:
s31: calculating a modal vibration mode under the excitation of the transmission error of the first-stage gear pair;
s32: calculating the modal vibration mode under the excitation of the transmission error of the secondary gear pair;
s33: calculating a modal vibration mode under the excitation of motor torque fluctuation;
s34: and calculating the mode vibration mode under the excitation of the radial electromagnetic force of the motor.
The calculation is simplified, the calculation efficiency is improved, the analysis is comprehensive, and the calculation precision can be ensured. The sequence of steps S31 to S34 is not limited.
Through the above steps S1, S2, and S3, a plurality of excitation sources of motor torque ripple, radial force, gear transmission error, and the like can be obtained.
Specifically, in step S4, when calculating the vibration acceleration response of each excitation at the bearing support seat of the dynamic model shell under the condition of interest, each excitation includes:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
According to the previous data analysis and model analysis, the key order harmonic is calculated and analyzed, the calculation is simplified, the calculation efficiency is improved, the analysis is comprehensive, and the calculation precision can be guaranteed.
In this embodiment, step S4 includes:
s41: calculating the vibration acceleration response of the third harmonic at the bearing support seat of the shell of the dynamic model before the meshing of the first-stage gear pair and the second-stage gear pair under the concerned working condition;
s42: calculating vibration acceleration responses of eight-order, twenty-fourth-order and forty-eight-order harmonics of the motor at a bearing support seat of a dynamic model shell, which are caused by motor torque fluctuation excitation under the concerned working condition;
s43: calculating vibration acceleration responses of eight-order, twenty-fourth-order and forty-eight-order harmonics of the motor at a bearing support seat of a dynamic model shell, which are caused by radial electromagnetic force excitation of the motor under the concerned working condition;
s44: and comparing and analyzing the vibration acceleration amplitude of each harmonic order, and determining the gear engagement order of the speed reducer and the harmonic orders of the vibration acceleration dynamic response with larger harmonics of eight orders, twenty-four orders and forty-eight orders of the motor under the excitation of the torque fluctuation of the motor and the excitation of the radial electromagnetic force of the motor.
The order of steps S41, S42, and S43 is not limited.
Similarly, in step S5, when calculating a vibration acceleration response slice at the housing bearing support in response to the excitation, each excitation includes:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
According to the previous data analysis and model analysis, the key order harmonic is calculated and analyzed, the calculation is simplified, the calculation efficiency is improved, the analysis is comprehensive, and the calculation precision can be guaranteed.
In this embodiment, step S5 includes:
s51: analyzing a vibration acceleration response slice at the supporting position of a bearing seat of the shell, which is caused by third-order harmonic waves before the engagement of first-order and second-order gears of the speed reducer with larger vibration response;
s52: slicing and analyzing vibration acceleration response at the supporting position of a bearing seat of the shell caused by eight-order, twenty-fourth-order and forty-eight-order harmonics caused by motor torque fluctuation excitation with large vibration response;
s53: slicing and analyzing vibration acceleration response at the bearing seat support of the shell caused by eight-order, twenty-four-order and forty-eight-order harmonics caused by electromagnetic force excitation of the radial direction of the motor with large vibration response;
s54: and comparing and analyzing the peak value of each harmonic order vibration acceleration slice, and determining the gear meshing order of the speed reducer, the rotating speed of the motor eight-order, twenty-four-order and forty-eight-order harmonic waves generated by the motor torque fluctuation excitation and the motor radial electromagnetic force excitation and the natural frequency of the electric drive system.
The sequence of steps S51, S52, and S53 is not limited.
Specifically, the step S6, when calculating the strain energy distribution of the electric drive system, includes:
s61: strain energy distribution of the shell system;
s62: strain energy distribution of the shaft tooth system.
The strain energy distribution of the shell and the shaft tooth system is fully considered so as to improve the model precision. The order of steps S61 and S62 is not limited.
Specifically, the step S7, when identifying the resonance position, includes:
the resonance position of the housing system or the shaft-tooth system is identified.
Specifically, the step S7 includes the following steps:
s71: calculating the ODS vibration mode occupying larger strain energy (mostly a shell system) at the position of a larger resonance peak of the order slice of the electric drive system;
s72: and comparing and analyzing the resonance position and amplitude of the ODS vibration mode of the system under each natural frequency, and identifying the resonance position of the shell system or the shaft-gear system, wherein the resonance position is an easily excited position and a weak position of vibration excitation response of the electric drive system, an optimization direction is provided for the subsequent system vibration response optimization, and the position needs to be paid attention to preferentially during the subsequent optimization.
Similarly, in step S8, when calculating and fitting the radiation acoustic power curve of the casing under the concerned working condition and each excitation, each excitation includes:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
Specifically, step S8 includes the following steps:
s81: calculating a shell radiation acoustic power curve comprising third-order harmonic waves before meshing of a first-stage and second-stage gear pair of the speed reducer, motor torque fluctuation excitation and eighth-order, twenty-fourth-order and forty-eighth-order harmonic waves under the excitation of radial electromagnetic force of the motor under the attention working condition;
s82: comparing and analyzing the peak position and the peak size of the radiated sound power curve of each order under excitation coupling;
s83: the order and the natural frequency occupying the main radiation acoustic power are identified, the direction is provided for the subsequent system vibration response optimization, and the subsequent optimization needs to pay attention.
In this embodiment, the calculations in the steps S1 to S8 can be performed by software, so as to improve the calculation efficiency. Preferably, Masta software or Romax software is used, a system dynamics module or an NVH vibration noise simulation analysis module is selected, and corresponding calculation is carried out, so that the method is simple and convenient.
Specifically, after step S8, the method further includes:
s9: and comparing and analyzing a radiation power-rise simulation result and an experimental result, and calibrating an electric drive system dynamics model to further improve the model precision.
Specifically, step S9 includes the following steps:
s91: comparing the radiated sound power simulation result with the experimental result under the same working condition, wherein the comparison content comprises the following steps: the integral variation trend of the order curve along with the rotating speed, the rotating speed of the peak position of the order curve and the decibel value of the peak position of the order curve;
s92: and the simulation result of the radiation acoustic power of the shell is consistent with the experimental result by calibrating the damping coefficient of each mode of the system.
Specifically, the experimental method can refer to the prior art and is not described in detail.
It should be understood that the above-described embodiments of the present invention are merely examples for clearly illustrating the present invention and are not intended to limit the embodiments of the present invention. Other variations and modifications will be apparent to persons skilled in the art in light of the above description. And are neither required nor exhaustive of all embodiments. Any modification, equivalent replacement, and improvement made within the spirit and principle of the present invention should be included in the protection scope of the claims of the present invention.
Claims (10)
1. A method for simulation analysis of electric drive system dynamics, comprising:
calculating the dynamic meshing rigidity of the gear pair;
calculating the dynamic meshing force of the ith harmonic of the gear pair based on the dynamic meshing stiffness of the gear pair;
calculating the natural frequency and the modal shape of the nth order of the system;
calculating the vibration acceleration response of each excitation at the bearing support seat of the dynamic model shell under the attention working condition based on the dynamic meshing stiffness of the gear pair, the dynamic meshing force analysis of the gear pair, the inherent frequency of the system and the modal shape, fitting and comparing and analyzing a noise waterfall diagram, and determining the harmonic order of the larger vibration acceleration response under each excitation;
calculating a vibration acceleration response slice at the bearing support of the shell caused by response excitation based on the analysis result of the harmonic order of the larger vibration acceleration response under each excitation, fitting and comparing and analyzing the peak value of each excitation vibration acceleration response slice, and determining the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system;
calculating the strain energy distribution of the electric drive system based on the rotating speed of the larger vibration acceleration response generated under each excitation and the natural frequency of the electric drive system, and performing comparative analysis on the part occupying the main strain energy;
calculating the ODS vibration mode occupying the main strain energy at the larger formant of the order slice of the electric drive system, and comparing and analyzing the resonance position and amplitude of the ODS vibration mode of the system under the natural frequency of each formant to identify the resonance position;
and calculating and fitting a shell radiation sound power curve under the concerned working condition and each excitation, comparing and analyzing the peak value position and the peak value size of the radiation sound power curve of each order under each excitation coupling, and identifying the order and the inherent frequency occupying the main radiation sound power.
2. The electric drive system dynamics simulation analysis method of claim 1, when calculating gear pair dynamic mesh stiffness, comprising:
calculating the meshing rigidity of the primary gear pair;
and calculating the meshing rigidity of the secondary gear pair.
3. The electric drive system dynamics simulation analysis method of claim 2, when calculating gear pair dynamic meshing forces, comprising:
calculating the dynamic meshing force of the primary gear pair;
and calculating the dynamic meshing force of the secondary gear pair.
4. The method for analyzing the dynamics simulation of the electric drive system according to claim 1, when calculating the natural frequency and the mode shape of the system, comprising:
calculating a modal vibration mode under the excitation of the transmission error of the first-stage gear pair;
calculating the modal vibration mode under the excitation of the transmission error of the secondary gear pair;
calculating a modal vibration mode under the excitation of motor torque fluctuation;
and calculating the mode vibration mode under the excitation of the radial electromagnetic force of the motor.
5. The electric drive system dynamics simulation analysis method of claim 1, wherein when calculating a vibrational acceleration response at the dynamic model shell bearing support base for each excitation at a condition of interest, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
6. The electric drive system dynamics simulation analysis method of claim 1, wherein when computing a vibrational acceleration response slice at a housing bearing support caused by response excitations, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
7. The method of analysis according to claim 1, when calculating a strain energy distribution of the electric drive system, comprising:
strain energy distribution of the shell system;
strain energy distribution of the shaft tooth system.
8. The electric drive system dynamics simulation analysis method of claim 1, when identifying resonance locations, comprising:
the resonance position of the housing system or the shaft-tooth system is identified.
9. The method for electrical drive system dynamics simulation analysis of claim 1, wherein when calculating and fitting a casing radiated acoustic power curve for a condition of interest and for each excitation, each excitation comprises:
the first, second and third harmonics of the primary gear pair mesh, and the first, second and third harmonics of the secondary gear pair mesh;
motor eighth, twenty-fourth and forty-eighth harmonics caused by motor torque ripple excitation;
the eight, twenty-four and forty-eight harmonics of the motor are caused by the radial electromagnetic force excitation of the motor.
10. The electric drive system dynamics simulation analysis method of any of claims 1-9, further comprising, after identifying the order and natural frequencies that account for the dominant radiated acoustic power:
comparing the radiated sound power simulation result with the experimental result under the same working condition, wherein the comparison content comprises the following steps: the integral variation trend of the order curve along with the rotating speed, the rotating speed of the peak position of the order curve and the decibel value of the peak position of the order curve;
and the simulation result of the radiation acoustic power of the shell is consistent with the experimental result by calibrating the damping coefficient of each mode of the system.
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