Test identification method and apparatus for vibration-involved dynamic parameters of bearing pedestal and using additional masses

Abstract

Provided in the present invention application is a test identification method and apparatus for vibration-involved dynamic parameters of a bearing pedestal and using additional masses. The method comprises: simplifying a dynamic model of a bearing pedestal into a single-degree-of-freedom system; applying an excitation force to the bearing pedestal, testing a response, plotting a frequency spectrogram, and obtaining a resonance frequency; adding additional masses to the bearing pedestal, and testing inherent frequencies under different additional masses; calculating vibration-involved masses on the basis of test results; plotting a curve of the vibration-involved masses changing with the additional masses, performing fitting by using the least-squares method, and performing extrapolation, so as to obtain a vibration-involved mass for when the additional mass is 0 and use same as a vibration-involved mass of the bearing pedestal; adding additional masses to the bearing pedestal, and testing damped vibration responses under different additional masses, so as to obtain logarithmic decrements and damping factors; plotting a curve of the damping factors changing with the additional masses, obtaining a damping factor in the same manner to use as a damping factor of the bearing pedestal, and performing calculation on the basis of the damping factor and the mass to obtain a vibration-involved stiffness coefficient of the bearing pedestal. The present invention using the solution can realize accurate identification of vibration-involved dynamic parameters of a bearing pedestal.

Description

Bearing seat parametric dynamic parameters additional mass test identification method and device Technical Field

[0001] The present invention relates to the technical field of rotating machinery, and in particular to a method and device for identifying the parametric dynamic parameters of a bearing seat by an additional mass test. Background Art

[0002] Bearing seats are crucial components of rotating machinery and a vital part of the rotor-bearing system. They play a key role in supporting the rotor. Their parametric dynamics significantly influence the dynamic characteristics of the rotating machinery system and the safe and stable operation of the unit. Key application areas include large rotating machinery such as compressors, generators, steam turbines, gas turbines, pumps, and fans in power, metallurgy, petrochemical, and aviation industries.

[0003] The parametric dynamic parameters of the bearing seat can be obtained by the following methods: (1) Frequency response function method. By applying an impact excitation force to the bearing seat, the vibration response under external force excitation is obtained, and the frequency response function between force and vibration is obtained using a dynamic signal analyzer. The frequency response function is fitted with a polynomial, and the parametric dynamic parameters of the bearing seat are solved by methods such as the least squares method; (2) Unbalance response correction method. Assuming the parametric dynamic parameters such as the mass and stiffness coefficient of the bearing seat, the unbalance response is calculated, and the unbalance response is measured through experiments. This method believes that the error between the calculated unbalance response value and the experimental measured value comes from the inaccurate dynamic parameters of the bearing seat. Based on this, the dynamic parameters are corrected until the calculated unbalance response and the measured unbalance response are consistent; (3) Critical speed correction method. The critical speed of the rotor-bearing system is measured experimentally, and the critical speed of the rotor-bearing system is calculated by modeling. This method believes that the error between the calculated critical speed value and the experimental measured value comes from the inaccurate dynamic parameters of the bearing seat. Based on this, the dynamic parameters are corrected until the calculated critical speed and the measured critical speed are consistent; (4) Finite element modeling analysis method. A three-dimensional solid model of the bearing seat is established, and the finite element method is used to calculate the bearing seat stiffness coefficient and bearing seat mass.

[0004] The frequency response function method is a widely used technique and a fundamental approach for modal parameter identification. While this method offers high accuracy, it requires specialized dynamic signal analyzers and modal parameter identification software, leading to high testing costs. Impact testing can cause double-strikes and nonlinearity, and the amplitude of the excitation force can influence the test results. Multiple excitations are required to obtain the coherence function at the frequencies of interest and determine the reliability of the frequency response function.

[0005] The unbalanced response method assumes that the error between calculation and measurement is primarily due to the bearing seat dynamic parameters. In reality, many factors can cause errors in unbalanced response calculations, such as large errors in the calculation of the oil film stiffness and damping coefficients, errors in boundary conditions, and errors in the shafting dynamics modeling. Attributing all errors to the bearing seat is unreasonable, resulting in large identification errors in this method.

[0006] The critical speed method assumes that the error between calculation and measurement is primarily due to the bearing seat dynamic parameters. In reality, there are many factors that can cause errors in critical speed calculation, such as large errors in the calculation of the oil film stiffness and damping coefficients, errors in boundary conditions, and errors in the shafting dynamics modeling. It is unreasonable to attribute all errors to the bearing seat, resulting in large identification errors in this method.

[0007] Finite element modeling analysis: Due to the structural complexity of the bearing housing and the difficulty in accurately describing the contact state between the bearing housing and the foundation, this method has limited accuracy and cannot accurately reflect the bearing housing's damping characteristics. Because the bearing housing is connected to the foundation, the parametric mass of the bearing housing is difficult to accurately calculate, and the boundary conditions are difficult to accurately set.

[0008] Summary of the Invention

[0009] The present invention is intended to solve one of the technical problems in the related art at least to a certain extent.

[0010] To this end, the first purpose of the present invention application is to propose a method for additional mass test identification of bearing seat parametric dynamic parameters, which solves the technical problems of low reliability and large errors of existing methods, and can conveniently and reliably perform test identification of bearing seat parametric dynamic parameters, thereby improving the accuracy of test identification results.

[0011] The second purpose of the present invention is to provide an additional mass test identification device for the parametric dynamic parameters of a bearing seat.

[0012] To achieve the above-mentioned purpose, the first embodiment of the present invention proposes a method for testing the additional mass of the bearing seat parametric dynamic parameters, comprising: simplifying the bearing seat dynamic model into a single-degree-of-freedom system, wherein the single-degree-of-freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient; measuring the first vibration response when a transient excitation force is applied to the bearing seat, and determining the first resonant frequency point based on the first vibration response; measuring the additional mass of different amplitudes applied above the bearing seat, and the vibration response set and the vibration attenuation response set when a transient excitation force is applied to the bearing seat, and determining the first resonant frequency point based on the first vibration response; measuring the additional mass of different amplitudes applied above the bearing seat, and the vibration response set and the vibration attenuation response set when a transient excitation force is applied to the bearing seat, and determining the first resonant frequency point based on the response set, the vibration attenuation response set and the vibration attenuation response set. The attenuation response set determines the second resonance frequency point set and the logarithmic attenuation rate set respectively; the parametric mass of the bearing seat under different amplitudes of added mass is calculated based on the first resonance frequency point set and the second resonance frequency point set, and the parametric mass of the bearing seat is determined based on the parametric mass of the bearing seat under different amplitudes of added mass; the parametric damping factor of the bearing seat under different amplitudes of added mass is calculated based on the logarithmic attenuation rate set, and the parametric damping factor of the bearing seat is determined based on the parametric damping factor of the added mass under different amplitudes; the parametric damping coefficient and the parametric stiffness coefficient of the bearing seat are determined based on the parametric mass of the bearing seat and the parametric damping factor of the bearing seat.

[0013] The method for identifying the vibration-parametric dynamic parameters of a bearing seat by adding mass testing in an embodiment of the present invention is to obtain the change in the bearing seat's natural frequency and vibration attenuation by impact testing bearing seats with different masses attached. The vibration-parametric mass of the bearing seat is calculated based on the model of the influence of mass on the natural frequency of the system by vibration theory. The damping coefficient is calculated based on the vibration attenuation response curve, and then the stiffness coefficient is calculated. The identification method proposed in the present invention application has a clear physical meaning, the identification environment is consistent with the actual working state of the bearing seat, and identification can be performed based on the vibration response curve under transient excitation force, which is simple and convenient.

[0014] Optionally, in one embodiment of the present invention, determining the first resonant frequency point based on the first vibration response includes:

[0015] Determining the relationship between vibration amplitude and frequency based on the first resonance response;

[0016] Determine multiple frequency points corresponding to the vibration peak based on the relationship between the vibration amplitude and the frequency;

[0017] The lowest frequency point is selected from multiple frequency points as the bearing seat resonance frequency point.

[0018] Optionally, in one embodiment of the present invention, the parametric mass of the bearing seat under different amplitudes of additional mass is expressed as:

[0019] Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is the second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm;

[0020] The parametric mass of the bearing seat is determined based on the parametric mass of the bearing seat under different amplitudes of additional mass, including:

[0021] Based on the parametric mass of the bearing seat under different amplitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined;

[0022] The curve of the bearing seat parametric mass changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric mass when the added mass is 0 is obtained as the bearing seat parametric mass.

[0023] Optionally, in one embodiment of the present invention, the parametric damping factor is expressed as:

[0024] Among them, ξ is the parametric damping factor, δ is the logarithmic decay rate, and N is the number of cycles.

[0025] Optionally, in one embodiment of the present invention, determining the parametric damping factor of the bearing seat based on the parametric damping factors under different amplitudes of the added mass includes:

[0026] Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the added mass is determined;

[0027] The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric damping factor when the added mass is 0 is obtained as the bearing seat parametric damping factor.

[0028] Optionally, in one embodiment of the present invention, the bearing seat parametric damping coefficient is expressed as:

[0029] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat;

[0030] The parametric stiffness coefficient of the bearing seat is expressed as:

[0031] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat.

[0032] To achieve the above-mentioned purpose, the second embodiment of the present invention proposes a bearing seat parametric dynamic parameter additional mass test identification device, including a system construction module, a first measurement module, a second measurement module, a first calculation module, a second calculation module, and a third calculation module, wherein:

[0033] A system building module is used to simplify the bearing seat dynamic model into a single-degree-of-freedom system, where the single-degree-of-freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient, and the bearing seat parametric stiffness coefficient;

[0034] a first measuring module, configured to measure a first vibration response when a transient excitation force is applied to the bearing seat, and determine a first resonant frequency point based on the first vibration response;

[0035] a second measuring module, configured to measure a vibration response set and a vibration attenuation response set when additional masses of different magnitudes are applied above the bearing seat and a transient excitation force is applied to the bearing seat, and to determine a second resonant frequency point set and a logarithmic attenuation rate set based on the response set and the vibration attenuation response set, respectively;

[0036] A first calculation module is used to calculate the parametric mass of the bearing seat under different amplitudes of added mass based on the first resonant frequency point and the second resonant frequency point set, and determine the parametric mass of the bearing seat based on the parametric mass of the bearing seat under different amplitudes of added mass;

[0037] A second calculation module is used to calculate the parametric damping factor of the bearing seat under different amplitudes of added mass based on the logarithmic decay rate set, and determine the parametric damping factor of the bearing seat based on the parametric damping factor under different amplitudes of added mass;

[0038] The third calculation module is used to determine the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient based on the bearing seat parametric mass and the bearing seat parametric damping factor.

[0039] Optionally, in one embodiment of the present invention, determining the first resonant frequency point based on the first vibration response includes:

[0040] Determining the relationship between vibration amplitude and frequency based on the first resonance response;

[0041] Determine multiple frequency points corresponding to the vibration peak based on the relationship between the vibration amplitude and the frequency;

[0042] The lowest frequency point is selected from multiple frequency points as the bearing seat resonance frequency point.

[0043] Optionally, in one embodiment of the present invention, the parametric mass when the bearing seat applies additional mass is expressed as:

[0044] Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is the second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm;

[0045] The parametric mass of the bearing seat is determined based on the parametric mass of the bearing seat under different amplitudes of additional mass, including:

[0046] Based on the parametric mass of the bearing seat under different amplitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined;

[0047] The curve of the bearing seat parametric mass changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric mass when the added mass is 0 is obtained as the bearing seat parametric mass.

[0048] Optionally, in one embodiment of the present invention, determining the parametric damping factor of the bearing seat based on the parametric damping factors under different amplitudes of the added mass includes:

[0049] Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the added mass is determined;

[0050] The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric damping factor when the added mass is 0 is obtained as the bearing seat parametric damping factor.

[0051] Additional aspects and advantages of the present invention will be given in part in the following description and will become apparent from the following description or learned through practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0052] The above and / or additional aspects and advantages of the present invention will become apparent and readily understood from the following description of the embodiments in conjunction with the accompanying drawings, in which:

[0053] FIG1 is a flow chart of a method for identifying the parametric dynamic parameters of a bearing seat by an additional mass test according to a first embodiment of the present invention;

[0054] FIG2 is a flowchart illustrating a method for testing and identifying parametric vibration dynamic parameters of a bearing seat according to an embodiment of the present invention;

[0055] FIG3 is an example diagram of a simplified single-degree-of-freedom mass-spring-damper system model according to an embodiment of the present invention;

[0056] FIG4 is an example diagram of the variation of vibration amplitude with frequency under transient excitation of an embodiment of the present invention;

[0057] FIG5 is an example diagram of a rear bearing seat model with an additional mass block according to an embodiment of the present invention;

[0058] FIG6 is a vibration attenuation response curve under transient excitation of an embodiment of the present invention;

[0059] FIG7 is a schematic structural diagram of an additional mass test identification device for parametric dynamic parameters of a bearing seat provided in an embodiment of the present invention. DETAILED DESCRIPTION

[0060] The following describes in detail embodiments of the present invention, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to explain the present invention, and are not to be construed as limiting the present invention.

[0061] Bearing seats are crucial components of rotating machinery and a vital part of the rotor-bearing system, playing a crucial role in supporting the rotor. Their parametric dynamic parameters significantly influence the dynamic characteristics of the rotating machinery system and the safe and stable operation of the unit. These parameters include mass, stiffness coefficient, and damping coefficient. Obtaining these parameters through testing, experimental identification, modeling, and calculation is crucial for optimizing the design of rotating machinery dynamics, reducing vibration, and assisting in fault diagnosis and management.

[0062] The following describes the bearing seat parametric dynamic parameters additional mass test identification method and device of the embodiment of the present invention with reference to the accompanying drawings.

[0063] FIG1 is a flow chart of an additional mass test identification method for parametric dynamic parameters of a bearing seat provided in Example 1 of the present invention.

[0064] As shown in FIG1 , the bearing seat parametric dynamic parameter additional mass test identification method includes the following steps:

[0065] Step 101: simplifying the bearing seat dynamic model into a single degree of freedom system, wherein the single degree of freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient, and the bearing seat parametric stiffness coefficient;

[0066] Step 102: measuring a first vibration response when a transient excitation force is applied to the bearing seat, and determining a first resonant frequency point based on the first vibration response;

[0067] Step 103: measuring a vibration response set and a vibration attenuation response set when additional masses of different magnitudes are applied above the bearing seat and a transient excitation force is applied to the bearing seat, and determining a second resonant frequency point set and a logarithmic decay rate set based on the response set and the vibration attenuation response set, respectively;

[0068] Step 104, calculating the parametric mass of the bearing seat under different amplitudes of added mass based on the first resonant frequency point and the second resonant frequency point set, and determining the parametric mass of the bearing seat based on the parametric mass of the bearing seat under different amplitudes of added mass;

[0069] Step 105: calculating the parametric damping factors of the bearing seat under different magnitudes of added mass based on the logarithmic decay rate set, and determining the parametric damping factor of the bearing seat based on the parametric damping factors under different magnitudes of added mass;

[0070] Step 106: Determine the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient based on the bearing seat parametric mass and the bearing seat parametric damping factor.

[0071] The method for identifying the vibration-parametric dynamic parameters of a bearing seat by adding mass testing in an embodiment of the present invention is to obtain the change in the bearing seat's natural frequency and vibration attenuation by impact testing bearing seats with different masses attached. The vibration-parametric mass of the bearing seat is calculated based on the model of the influence of mass on the natural frequency of the system by vibration theory. The damping coefficient is calculated based on the vibration attenuation response curve, and then the stiffness coefficient is calculated. The identification method proposed in the present invention application has a clear physical meaning, the identification environment is consistent with the actual working state of the bearing seat, and identification can be performed based on the vibration response curve under transient excitation force, which is simple and convenient.

[0072] Optionally, in one embodiment of the present invention, determining the first resonant frequency point based on the first vibration response includes:

[0073] Determining the relationship between vibration amplitude and frequency based on the first resonance response;

[0074] Determine multiple frequency points corresponding to the vibration peak based on the relationship between the vibration amplitude and the frequency;

[0075] The lowest frequency point is selected from multiple frequency points as the bearing seat resonance frequency point.

[0076] Optionally, in one embodiment of the present invention, the parametric mass when the bearing seat applies additional mass is expressed as:

[0077] Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is the second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm;

[0078] The parametric mass of the bearing seat is determined based on the parametric mass of the bearing seat under different amplitudes of additional mass, including:

[0079] Based on the parametric mass of the bearing seat under different amplitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined;

[0080] The curve of the bearing seat parametric mass changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric mass when the added mass is 0 is obtained as the bearing seat parametric mass.

[0081] Optionally, in one embodiment of the present invention, the parametric damping factor is expressed as:

[0082] Where δ is the logarithmic decay rate, N is the number of cycles, and T is the cycle time.

[0083] Optionally, in one embodiment of the present invention, determining the parametric damping factor of the bearing seat based on the parametric damping factors under different amplitudes of the added mass includes:

[0084] Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the added mass is determined;

[0085] The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric damping factor when the added mass is 0 is obtained as the bearing seat parametric damping factor.

[0086] Optionally, in one embodiment of the present invention, the bearing seat parametric damping coefficient is expressed as:

[0087] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat;

[0088] The parametric stiffness coefficient of the bearing seat is expressed as:

[0089] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat.

[0090] FIG2 is a flowchart of a method for testing and identifying the parametric vibration dynamic parameters of a bearing seat according to this embodiment. In this embodiment, the transient excitation force applied is in the vertical direction. This embodiment is also applicable to the horizontal direction. As shown in FIG2 , this embodiment includes:

[0091] Step 1: Simplify the bearing seat model into a single degree of freedom system as shown in Figure 3, including: parametric mass, stiffness coefficient and damping coefficient;

[0092] Step 2: Arrange vibration measurement points in the vertical direction of the bearing seat, apply transient excitation force to the bearing seat in the vertical direction with a hammer, measure the vibration response under the hammer excitation, and plot the vibration amplitude versus frequency, as shown in Figure 4. In Figure 4, there are vibration peaks at several frequency points. The lowest frequency point is selected as the resonant frequency point of the bearing seat, which is recorded as

[0093] Step 3: Figure 5 shows an example of the bearing seat model after adding a mass block. As shown in Figure 5, add an additional mass Δm above the bearing seat. Let the mass of the bearing seat be m. To improve the accuracy of the identification results, the requirement is: 10% m ≤ Δm ≤ 60% m.

[0094] After adding the additional mass, a transient excitation force is applied to the bearing seat in the vertical direction again, and the vibration response under the hammer excitation is measured. The vibration amplitude is plotted against the frequency, and the lowest frequency point is selected as the resonant frequency point of the bearing seat, which is recorded as

[0095] Step 4: According to mechanical vibration theory, for a single degree of freedom vibration system:

[0096] Where ζ is the damping factor and k is the bearing seat stiffness.

[0097] The bearing seat vibration mass can be derived from the above formula:

[0098] Step 5: Within the range of 10%m≤Δm≤60%m, apply different amplitudes of additional mass Δm, calculate the bearing seat mass m under different added masses, and plot the bearing seat parametric mass versus added mass curve. Use the least squares method to fit the bearing seat parametric mass versus added mass curve, and extrapolate the bearing seat parametric mass when the added mass is 0. This is used as the final identified bearing seat parametric mass m.

[0099] Step 6: Experimentally identify the bearing seat parametric damping factor ξ. Using a hammer, apply an impact excitation force to the bearing seat with different added masses. Measure the vibration attenuation response under impact excitation, as shown in Figure 6. Select N cycles and calculate the logarithmic decay rate δ of the vibration amplitude during this period.

[0100] According to the mechanical vibration theory,

[0101] Where N is the number of cycles.

[0102] Step 7: Within the range of 10%m≤Δm≤60%m, apply different amplitudes of additional mass Δm, calculate the bearing seat parametric damping factor ζ under different added masses, and plot the bearing seat parametric damping factor versus added mass curve. Use the least squares method to fit the bearing seat parametric damping factor versus added mass curve, and extrapolate the bearing seat parametric damping factor when the added mass is 0. This is used as the final identified bearing seat parametric damping factor.

[0103] Step 8: Calculate the bearing seat parametric damping coefficient c from the bearing seat parametric damping factor ζ:

[0104] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat;

[0105] The parametric stiffness coefficient of the bearing seat is expressed as:

[0106] in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat.

[0107] In order to implement the above embodiment, the present invention application also proposes an additional mass test identification device for the parametric dynamic parameters of a bearing seat.

[0108] FIG7 is a schematic structural diagram of an additional mass test identification device for parametric dynamic parameters of a bearing seat provided in an embodiment of the present invention.

[0109] As shown in FIG7 , the bearing seat parametric dynamic parameter additional mass test identification device includes a system construction module, a first measurement module, a second measurement module, a first calculation module, a second calculation module, and a third calculation module, wherein:

[0110] A system building module is used to simplify the bearing seat dynamic model into a single-degree-of-freedom system, wherein the single-degree-of-freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient, and the bearing seat parametric stiffness coefficient;

[0111] a first measuring module, configured to measure a first vibration response when a transient excitation force is applied to the bearing seat, and determine a first resonant frequency point based on the first vibration response;

[0112] a second measuring module, configured to measure a vibration response set and a vibration attenuation response set when additional masses of different magnitudes are applied above the bearing seat and a transient excitation force is applied to the bearing seat, and to determine a second resonant frequency point set and a logarithmic attenuation rate set based on the response set and the vibration attenuation response set, respectively;

[0113] A first calculation module is used to calculate the parametric mass of the bearing seat under different amplitudes of added mass based on the first resonant frequency point and the second resonant frequency point set, and determine the parametric mass of the bearing seat based on the parametric mass of the bearing seat under different amplitudes of added mass;

[0114] A second calculation module is used to calculate the parametric damping factor of the bearing seat under different amplitudes of added mass based on the logarithmic decay rate set, and determine the parametric damping factor of the bearing seat based on the parametric damping factor under different amplitudes of added mass;

[0115] The third calculation module is used to determine the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient based on the bearing seat parametric mass and the bearing seat parametric damping factor.

[0116] Optionally, in one embodiment of the present invention, determining the first resonant frequency point based on the first vibration response includes:

[0117] Determining the relationship between vibration amplitude and frequency based on the first resonance response;

[0118] Determine multiple frequency points corresponding to the vibration peak based on the relationship between the vibration amplitude and the frequency;

[0119] The lowest frequency point is selected from multiple frequency points as the bearing seat resonance frequency point.

[0120] Optionally, in one embodiment of the present invention, the parametric mass when the bearing seat applies additional mass is expressed as:

[0121] Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is the second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm;

[0122] The parametric mass of the bearing seat is determined based on the parametric mass of the bearing seat under different amplitudes of additional mass, including:

[0123] Based on the parametric mass of the bearing seat under different amplitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined;

[0124] The curve of the bearing seat parametric mass changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric mass when the added mass is 0 is obtained as the bearing seat parametric mass.

[0125] Optionally, in one embodiment of the present invention, determining the parametric damping factor of the bearing seat based on the parametric damping factors under different amplitudes of the added mass includes:

[0126] Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the added mass is determined;

[0127] The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method, and the bearing seat parametric damping factor when the added mass is 0 is obtained as the bearing seat parametric damping factor.

[0128] It should be noted that the above explanation of the embodiment of the bearing seat parametric vibration dynamic parameters additional mass test identification method is also applicable to the bearing seat parametric vibration dynamic parameters additional mass test identification device of this embodiment, and will not be repeated here.

[0129] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example" or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0130] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of this application, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0131] Any process or method description in a flowchart or otherwise described herein may be understood to represent a module, segment or portion of code comprising one or more executable instructions for implementing the steps of a custom logical function or process, and the scope of the preferred embodiments of the present invention application includes alternative implementations in which functions may be performed in a sequence other than as shown or discussed, including performing functions in a substantially simultaneous manner or in a reverse order depending on the functions involved, which should be understood by those skilled in the art to which the embodiments of the present invention application belong.

[0132] The logic and / or steps represented in the flowcharts or otherwise described herein, for example, can be considered as a sequenced list of executable instructions for implementing the logical functions, and can be embodied in any computer-readable medium for use by, or in conjunction with, an instruction execution system, apparatus, or device (e.g., a computer-based system, a system including a processor, or other system that can fetch and execute instructions from an instruction execution system, apparatus, or device). For purposes of this specification, a "computer-readable medium" can be any device that can contain, store, communicate, propagate, or transport a program for use by, or in conjunction with, an instruction execution system, apparatus, or device. More specific examples (a non-exhaustive list) of computer-readable media include the following: an electrical connection with one or more wires (electronic devices), a portable computer disk cartridge (magnetic device), random access memory (RAM), read-only memory (ROM), erasable and programmable read-only memory (EPROM or flash memory), fiber optic devices, and a portable compact disc read-only memory (CDROM). Furthermore, the computer-readable medium may even be paper or other suitable medium on which the program is printed, since the program may be obtained electronically, for example, by optically scanning the paper or other medium and then editing, interpreting or processing it in another suitable manner if necessary, and then storing it in a computer memory.

[0133] It should be understood that the various parts of the present application can be implemented using hardware, software, firmware, or a combination thereof. In the above-described embodiments, multiple steps or methods can be implemented using software or firmware stored in a memory and executed by a suitable instruction execution system. For example, if implemented using hardware, as in another embodiment, any one of the following technologies known in the art or a combination thereof can be used to implement the hardware: a discrete logic circuit having a logic gate circuit for implementing a logic function on a data signal, an application-specific integrated circuit having a suitable combination of logic gate circuits, a programmable gate array (PGA), a field programmable gate array (FPGA), etc.

[0134] Those skilled in the art will understand that all or part of the steps in the method of the above embodiment can be completed by instructing related hardware through a program, and the program can be stored in a computer-readable storage medium. When the program is executed, it includes one or a combination of the steps of the method embodiment.

[0135] In addition, the functional units in the various embodiments of the present invention may be integrated into a single processing module, or each unit may exist physically separately, or two or more units may be integrated into a single module. The aforementioned integrated modules may be implemented in the form of hardware or in the form of software functional modules. If the integrated modules are implemented in the form of software functional modules and sold or used as independent products, they may also be stored in a computer-readable storage medium.

[0136] The storage medium mentioned above may be a read-only memory, a magnetic disk, or an optical disk, etc. Although the embodiments of the present invention have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting the present invention. Persons skilled in the art may make changes, modifications, substitutions, and variations to the above embodiments within the scope of the present invention.

Claims

1. A bearing seat parametric dynamics parameter additional mass test identification method, characterized in that: The following steps are involved: Simplifying the bearing seat dynamics model into a single degree of freedom system, wherein the single degree of freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient; measuring a first vibration response when a transient excitation force is applied to the bearing seat, and determining a first resonance frequency point based on the first vibration response; Measuring a vibration response set and a vibration attenuation response set when additional masses of different amplitudes are applied above the bearing seat and a transient excitation force is applied to the bearing seat, and determining a second resonance frequency point set and a logarithmic attenuation rate set based on the response set and the vibration attenuation response set respectively; Calculating the parametric mass of the bearing seat under different amplitudes of additional mass based on the first resonant frequency point and the second resonant frequency point set, and determining the parametric mass of the bearing seat based on the parametric mass of the bearing seat under different amplitudes of additional mass; Calculating the parametric damping factor of the bearing seat under different amplitudes of additional mass based on the logarithmic decay rate set, and determining the parametric damping factor of the bearing seat based on the parametric damping factor under different amplitudes of additional mass; The bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient are determined based on the bearing seat parametric mass and the bearing seat parametric damping factor.

2. The method according to claim 1, characterized in that The determining a first resonant frequency point based on the first vibration response comprises: Determining a relationship between vibration amplitude and frequency based on the first resonance response; Determine multiple frequency points corresponding to the vibration peak value based on the relationship between the vibration amplitude and the frequency; The lowest frequency point is selected from the multiple frequency points as the bearing seat resonance frequency point.

3. The method according to claim 1, characterized in that The parametric mass of the bearing seat with different magnitudes of additional mass is expressed as: Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is a second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm; the determining of the bearing seat parametric mass based on the parametric mass under the additional mass of different amplitudes of the bearing seat comprises: Based on the parametric mass of the bearing seat under different magnitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined; The curve of the bearing seat parametric mass changing with the additional mass is fitted and extrapolated by the least squares method to obtain the bearing seat parametric mass when the additional mass is 0 as the bearing seat parametric mass.

4. The method according to claim 1, characterized in that The parametric damping factor is expressed as: Among them, ξ is the parametric damping factor, N is the number of cycles, and δ is the logarithmic decay rate.

5. The method according to claim 1, characterized in that The determining of the bearing seat parametric damping factor based on the parametric damping factor under different amplitudes of the additional mass includes: Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the additional mass is determined; The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method to obtain the bearing seat parametric damping factor when the added mass is 0 as the bearing seat parametric damping factor.

6. The method according to claim 1, characterized in that The bearing seat parametric damping coefficient is expressed as: in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat; The bearing seat parametric stiffness coefficient is expressed as: in, is the first resonant frequency point, m is the parametric mass of the bearing seat, and ξ is the parametric damping factor of the bearing seat.

7. A bearing seat parametric dynamics parameter additional mass test identification device, characterized in that: It includes a system construction module, a first measurement module, a second measurement module, a first calculation module, a second calculation module, and a third calculation module, wherein: The system building module is used to simplify the bearing seat dynamics model into a single degree of freedom system, wherein the single degree of freedom system includes the bearing seat parametric mass, the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient; The first measuring module is used to measure a first vibration response when a transient excitation force is applied to the bearing seat, and determine a first resonance frequency point based on the first vibration response; The second measuring module is used to measure a vibration response set and a vibration attenuation response set when additional masses of different amplitudes are applied above the bearing seat and a transient excitation force is applied to the bearing seat, and determine a second resonance frequency point set and a logarithmic attenuation rate set based on the response set and the vibration attenuation response set respectively; The first calculation module is used to calculate the parametric mass of the bearing seat under different amplitudes of additional mass based on the first resonant frequency point and the second resonant frequency point set, and determine the parametric mass of the bearing seat based on the parametric mass of the bearing seat under different amplitudes of additional mass; The second calculation module is used to calculate the parametric damping factor of the bearing seat under different amplitudes of additional mass based on the logarithmic decay rate set, and determine the parametric damping factor of the bearing seat based on the parametric damping factor under different amplitudes of additional mass; The third calculation module is used to determine the bearing seat parametric damping coefficient and the bearing seat parametric stiffness coefficient based on the bearing seat parametric mass and the bearing seat parametric damping factor.

8. The device according to claim 7, characterized in that The determining a first resonant frequency point based on the first vibration response comprises: Determining a relationship between vibration amplitude and frequency based on the first resonance response; Determine multiple frequency points corresponding to the vibration peak value based on the relationship between the vibration amplitude and the frequency; The lowest frequency point is selected from the multiple frequency points as the bearing seat resonance frequency point.

9. The device according to claim 7, characterized in that The parametric mass of the bearing seat with different magnitudes of additional mass is expressed as: Where m is the parametric mass, Δm is the additional mass applied, is the first resonant frequency point, is a second resonance frequency point in the second resonance frequency point set corresponding to the applied additional mass Δm; The determining of the bearing seat parametric mass based on the parametric mass of the bearing seat under different amplitudes of the additional mass includes: Based on the parametric mass of the bearing seat under different magnitudes of additional mass, the curve of the parametric mass of the bearing seat changing with the additional mass is determined; The curve of the bearing seat parametric mass changing with the additional mass is fitted and extrapolated by the least squares method to obtain the bearing seat parametric mass when the additional mass is 0 as the bearing seat parametric mass.

10. The device according to claim 7, characterized in that The determining of the bearing seat parametric damping factor based on the parametric damping factor under different amplitudes of the additional mass includes: Based on the parametric damping factor under different amplitudes of additional mass, the curve of the parametric damping factor of the bearing seat changing with the additional mass is determined; The curve of the bearing seat parametric damping factor changing with the added mass is fitted and extrapolated by the least squares method to obtain the bearing seat parametric damping factor when the added mass is 0 as the bearing seat parametric damping factor.

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