Method for simulating bearing inner and outer raceway fault vibration signals of a rotor-bearing system

Abstract

This invention discloses a method for simulating the vibration signals of internal and external raceway faults in a rotor-bearing system. The vibration signals obtained by this method can accurately reflect the influence of rotor imbalance centrifugal force on the vibration behavior of bearings with raceway defects in a high-speed rotor-bearing system. Consequently, it can accurately simulate the vibration signals and sideband characteristics of the envelope spectrum of bearings with raceway defects in a high-speed rotor-bearing system. This method can replace the traditional method of obtaining bearing fault vibration signals as training input for intelligent bearing diagnosis, thereby obtaining fault labels corresponding to the simulated internal and external raceway defects of the bearing. This method is time-saving, cost-effective, and has a short experimental cycle.

Description

Technical Field

[0001] This invention relates to the field of bearing fault diagnosis, and more specifically to a method for simulating the vibration signals of faults in the inner and outer raceways of a rotor-bearing system. Background Technology

[0002] As a key component of rotating machinery systems, the health of rolling bearings directly affects the performance of these systems. Local defects on the bearing contact surfaces, such as pits, scratches, or chips, can cause abnormal vibrations in the mechanical system. If these damages are not identified, they may ultimately lead to serious accidents.

[0003] Intelligent bearing diagnosis based on bearing vibration signals is a widely adopted and effective method. This method includes three stages: bearing vibration signal acquisition, feature extraction, and state recognition. State recognition involves comparing the state labels obtained from the bearing vibration signals with fault labels to determine whether the bearing has a fault corresponding to the label. Therefore, fault labels need to be obtained before intelligent bearing diagnosis, and these labels are obtained based on the bearing fault vibration signals. Traditionally, bearing fault vibration signals are obtained by building a bearing test bench and running an artificially induced faulty bearing on the bench. However, this method is time-consuming, costly, and has a long experimental cycle.

[0004] Subsequently, some researchers proposed modeling bearing fault vibration signals using digital simulation. For example, PDMcfadden et al. established a vibration demodulation signal model for bearings with raceway defects, clarifying the time-domain characteristics and spectral features of the demodulated vibration signal of bearings with raceway defects under directional loads; YTSu et al. studied the influence of raceway waviness on the modulation sideband of the vibration envelope spectrum of faulty bearings under different loads, improving the analytical model of the vibration envelope spectrum of faulty bearings; F. Cong et al. considered the influence of rotor unbalance force on bearing load and established a rotor-bearing system fault vibration signal model, but Cong et al. believed that the load applied to the bearing by rotor unbalance force and system self-weight was independent, without considering the influence of the coupling effect of rotor unbalance centrifugal force and rotor self-weight on the vibration of bearings with inner raceway defects.

[0005] However, rotor imbalance is a common fault in high-speed rotating rotor mechanical systems such as aero-engines and gas turbines. Rotor-main bearing systems in aero-engines and gas turbines typically operate at high speeds over a wide range. The centrifugal force load from rotor imbalance on the main bearings in such systems is not negligible, and the load in the bearing raceway defect area is one of the main factors affecting the impact vibration intensity of bearings with raceway damage. Therefore, under high-speed conditions, the coupling effect of directional loads such as rotor self-weight and rotor imbalance centrifugal force will inevitably change the load in the bearing raceway defect area, thus affecting the impact vibration behavior of bearings with raceway defects. However, existing technologies do not fully consider the impact of the coupling effect of large rotor imbalance centrifugal force and rotor self-weight at high speeds on the load in the bearing load-bearing area. Therefore, existing bearing fault vibration signal models cannot accurately describe the bearing fault vibration characteristics of high-speed rotor-bearing systems, making it difficult to obtain corresponding fault labels. Summary of the Invention

[0006] The purpose of this invention is to overcome the aforementioned defects or problems in the prior art and to provide a method for simulating the vibration signals of faults in the inner and outer raceways of a rotor-bearing system.

[0007] To achieve the above objectives, the present invention adopts the following technical solution:

[0008] The first technical solution relates to a method for simulating vibration signals of bearing inner raceway faults in a rotor-bearing system. The method includes the steps of obtaining the bearing inner raceway fault vibration signal based on the load equation of the bearing inner raceway defect region, through an inner raceway impact function, a transmission path modulation function of the inner raceway defect impact, and a unit pulse high-frequency resonance attenuation response function. The load equation for the bearing inner raceway defect region is as follows:

[0009]

[0010] Where φ(t) is the phase of the rotor unbalanced centrifugal force, Δφ0 is the phase difference between the location of the inner raceway defect and the rotor unbalanced centrifugal force, φ(t) + Δφ0 is the phase of the inner raceway defect at time t, ε is the load distribution factor, n is the bearing parameter, and θ max The maximum phase angle (θ) in the load-bearing area of ​​the clearance bearing max <),|F r ()| represents the magnitude of the combined load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as,

[0011]

[0012] Where, m r ,e,ω r These are the rotor's equivalent mass, equivalent eccentricity, and rotor speed, respectively, where g is the acceleration due to gravity.

[0013] β(t) is the phase angle of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as follows:

[0014]

[0015] The second technical solution is based on the first technical solution, wherein the inner raceway impact function is,

[0016]

[0017] Where, p i0 T represents the amplitude of the inner raceway impact function. bPFI Let δ be the period of the inner raceway impact function, k be an integer, and δ be the pulse function.

[0018] The third technical solution is based on the second technical solution, wherein the transmission path modulation function of the inner raceway defect impact is,

[0019] a i (t)= i cos(φ(t)+Δφ0)+ i0

[0020] Among them, A i Let a be the transmission coefficient of the inner raceway impact. i0 The transmitted DC component.

[0021] The fourth technical solution is based on the third technical solution, wherein the unit pulse high-frequency resonant attenuation response function is,

[0022]

[0023] Where ρ is the initial amplitude, B is the attenuation parameter, and f n This is the resonant frequency of the rotor-bearing system.

[0024] The fifth technical solution is based on the fourth technical solution, wherein the vibration signal of the bearing inner raceway fault is,

[0025]

[0026] The sixth technical solution relates to a method for simulating the vibration signal of a bearing outer raceway fault in a rotor-bearing system. This method includes the steps of obtaining the bearing outer raceway fault vibration signal based on the load equation of the bearing outer raceway defect region, through the outer raceway impact function, the outer raceway defect vibration transmission path effect function, and the unit pulse high-frequency resonance attenuation response function. The load equation for the bearing outer raceway defect region is...

[0027]

[0028] Where, γ o The phase of a single-point defect in the outer raceway, ε is the load distribution factor, n is the bearing parameter, and θ max The maximum phase angle (θ) in the load-bearing area of ​​the clearance bearing max <),|F r ()| represents the magnitude of the combined load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as,

[0029]

[0030] Where, m r ,e,ω r These are the rotor's equivalent mass, equivalent eccentricity, and rotor speed, respectively, where g is the acceleration due to gravity.

[0031] β(t) is the phase angle of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as follows:

[0032]

[0033] The seventh technical solution is based on the sixth technical solution, wherein the outer raceway impact function is,

[0034]

[0035] Where, p o0 T represents the amplitude of the outer raceway impact function. BPFO Let δ be the period of the outer raceway impact function, k be an integer, and δ be the pulse function.

[0036] The eighth technical solution is based on the seventh technical solution, wherein the vibration transmission path effect function of the outer raceway defect is,

[0037] a o (t)= O

[0038] Among them, A O It is the transmission coefficient of the impact on the outer raceway.

[0039] The ninth technical solution is based on the eighth technical solution, wherein the unit pulse high-frequency resonant attenuation response function is,

[0040]

[0041] Where ρ is the initial amplitude, B is the attenuation parameter, and f n This is the resonant frequency of the rotor-bearing system.

[0042] The tenth technical solution is based on the ninth technical solution, wherein the vibration signal of the bearing outer raceway fault is,

[0043]

[0044] As can be seen from the above description of the present invention, compared with the prior art, the present invention has the following beneficial effects:

[0045] This invention provides two methods for acquiring the vibration signals of the inner and outer raceways of a rotor-bearing system using digital simulation. The vibration signals obtained by these two methods can accurately reflect the influence of rotor imbalance centrifugal force on the vibration behavior of bearings with raceway defects in high-speed rotor-bearing systems. Consequently, they can accurately simulate the vibration signals and sideband characteristics of the envelope spectrum of bearings with raceway defects in high-speed rotor-bearing systems. This can replace the bearing fault vibration signals obtained by traditional methods as training input for intelligent bearing diagnosis to obtain corresponding fault labels, saving time, reducing costs, and shortening the experimental cycle.

[0046] Another technical contribution of this invention to the prior art is that, in the method for obtaining the vibration signal of the bearing inner raceway fault, the phase difference Δφ0 between the location of the bearing inner raceway defect and the rotor's unbalanced centrifugal force is also considered. This allows for the simulation of the bearing inner raceway fault vibration signal of the rotor-bearing system under a "false health state." A "false health state" refers to a condition where, under the action of the rotor's unbalanced centrifugal force, the impact vibration of the bearing inner raceway defect weakens accordingly. The bearing inner raceway fault vibration signal under this state is similar to the vibration signal of the inner raceway of the rotor-bearing system under a true health state. The simulated bearing inner raceway fault vibration signal of the rotor-bearing system under a false health state obtained by this invention can be used as training input for intelligent bearing diagnosis to obtain fault labels corresponding to the false health state. Then, when the actually measured bearing vibration signal is used for intelligent bearing diagnosis, if a state label with the same fault label appears, it can be determined that the bearing is not in a true health state but in a false health state.

[0047] Furthermore, since the method for obtaining bearing fault vibration signals provided by this invention is performed through digital simulation, the locations of defects in the inner and outer raceways of the bearing can be set independently to obtain different bearing inner and outer raceway fault vibration signals. Similarly, since it is performed through digital simulation, bearing inner and outer raceway fault vibration signals at different speeds can be obtained. Attached Figure Description

[0048] To more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings used in the following description of the embodiments are briefly introduced. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0049] Figure 1 This is a schematic diagram of the rotor-bearing system in this embodiment.

[0050] Figure 2 This is a schematic diagram of the rotor-bearing experimental testing device in this embodiment.

[0051] Figure 3 This is a schematic diagram of the turntable and mass block in this embodiment.

[0052] Figure 4 This is a schematic diagram of a bearing with an internal raceway defect in this embodiment.

[0053] Figure 5 This is a schematic diagram of the bearing with an outer raceway defect in this embodiment.

[0054] Figure 6 This is the simulated impact vibration signal and its envelope spectrum of the inner ring defect in this embodiment.

[0055] Figure 7 This example shows the simulated impact vibration signal and its envelope spectrum of the inner ring defect under different phase differences Δ'0 in this embodiment.

[0056] Figure 8 This is the simulated impact vibration signal and its envelope spectrum of the bearing with an outer ring defect in this embodiment.

[0057] Figure 9 This is the measured impact vibration signal and its envelope spectrum of the inner ring defect in this embodiment.

[0058] Figure 10 The measured signals and envelope spectra of the impact vibration of the inner ring defect under different phase differences Δφ0 in this embodiment are shown.

[0059] Figure 11 This is the measured impact vibration signal and its envelope spectrum of the bearing with an outer ring defect in this embodiment. Detailed Implementation

[0060] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are preferred embodiments of the present invention and should not be considered as excluding other embodiments. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without creative effort are within the scope of protection of the present invention.

[0061] Unless otherwise expressly defined, the use of terms such as "first," "second," or "third" in the claims, description, and accompanying drawings of this invention is for distinguishing different objects and not for describing a specific order.

[0062] Unless otherwise expressly defined, in the claims, description, and accompanying drawings of this invention, the use of directional terms such as "center," "lateral," "longitudinal," "horizontal," "vertical," "top," "bottom," "inner," "outer," "upper," "lower," "front," "rear," "left," "right," "clockwise," and "counterclockwise" to indicate orientation or positional relationships is based on the orientation and positional relationships shown in the accompanying drawings and is only for the convenience of describing the invention and simplifying the description, and is not intended to indicate or imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation, and therefore should not be construed as limiting the specific scope of protection of this invention.

[0063] Unless otherwise expressly defined, the terms "fixed connection" or "fixed connection" used in the claims, description and drawings of this invention should be interpreted broadly to refer to any connection in which there is no displacement or relative rotation relationship between the two parties, including non-removable fixed connection, detachable fixed connection, integral connection and fixed connection by other means or components.

[0064] In the claims, description and accompanying drawings of this invention, the terms "comprising," "having," and variations thereof are used to mean "including but not limited to."

[0065] In the accompanying drawings of this invention, the term "Amplitude" is used to refer to amplitude.

[0066] In the accompanying drawings of this invention, the term "Order" is used to refer to a grade or order.

[0067] In the accompanying drawings of this invention, the term "Side bands" as used refers to modulation side bands.

[0068] In the accompanying drawings of this invention, the term "Cycles" as used refers to the number of revolutions.

[0069] In the accompanying drawings of this invention, the term "Load" is used to refer to a load.

[0070] In the accompanying drawings of this invention, the term "f" is used as follows: bpfi ", which is "f" in the claims and specification of this invention. BPFI ".

[0071] In the accompanying drawings of this invention, the term "f" is used as follows: bpfo ", which is "f" in the claims and specification of this invention. BPFO ".

[0072] In the accompanying drawings of this invention, the term "f" is used as follows: s ", which is "f" in the claims and specification of this invention. r"" refers to the rotor speed, and its unit is RPM.

[0073] See Figure 1 , Figure 1 The rotor-bearing system in this embodiment is shown, with a rigid rotor symmetrically supported by bearings at both ends. The bearings at both ends are ball bearings and are mounted on bearing housings.

[0074] This embodiment provides a method for simulating vibration signals from internal raceway faults in a rotor-bearing system and a method for simulating vibration signals from external raceway faults in a rotor-bearing system. Both methods are based on the following assumptions.

[0075] 1) The target bearing is a ball bearing, which is connected to the rotor via a rigid shaft.

[0076] 2) The inner raceway of the bearing is fixed to a rigid shaft, and there is no relative rotation between the inner raceway of the bearing and the shaft.

[0077] 3) The rollers roll purely on the bearing raceway, without considering the possibility of roller slippage.

[0078] 4) The bearing cage is rigid, the bearing clearance is greater than zero, and it is constant.

[0079] 5) Ignore the influence of gravity on the shaft and bearings; the bearing gravity load mainly comes from the rotor.

[0080] 6) The rotor is unbalanced, which will generate an unbalanced centrifugal force load on the bearing during operation.

[0081] The method for obtaining vibration signals from bearing inner raceway faults in a rotor-bearing system includes the following steps: based on the load equation of the bearing inner raceway defect region, the vibration signals are obtained through the inner raceway impact function, the transmission path modulation function of the inner raceway defect impact, and the unit pulse high-frequency resonance attenuation response function. The load equation for the bearing inner raceway defect region is as follows:

[0082]

[0083] Where φ(t) is the phase of the rotor's unbalanced centrifugal force. φ0 is the initial phase of the rotor's unbalanced centrifugal force, Δφ0 is the phase difference between the location of the inner raceway defect and the rotor's unbalanced centrifugal force, φ(t)+Δφ0 is the phase of the inner raceway defect at time t, ε is the load distribution factor (ε<0.5 for positive clearance), and n is the bearing parameter; for ball bearings... Roller bearings θ max The maximum phase angle (θ) in the load-bearing area of ​​the clearance bearing max <), at phase angle θ max Within the range, the load on the raceway is greater than zero; at phase angle θmax Outside the range, the raceway load is zero, |F r ()| represents the magnitude of the combined load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as,

[0084]

[0085] Where, m r ,e,ω r These are the rotor's equivalent mass, equivalent eccentricity, and rotor speed, ω, respectively. r The unit is rad / s, and g is the acceleration due to gravity;

[0086] β(t) is the phase angle of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at time t, expressed as follows:

[0087]

[0088] The inner raceway impact function is expressed as follows:

[0089]

[0090] Where, p i0 The amplitude of the inner raceway impact function can be set to 1, T. BPFI Let δ be the period of the inner raceway impact function, k be an integer, and δ be the pulse function.

[0091] The period T of the inner raceway impact function BPFI Represented as,

[0092] T BPFI =1 / f BPFI

[0093] f BPFI The characteristic frequency of defects in the bearing's inner raceway is the frequency at which the roller passes through the defect area of ​​the inner raceway per revolution of the shaft, expressed as:

[0094]

[0095] Where, N b Here, d is the number of rollers, d is the roller diameter, D is the bearing pitch diameter, α is the bearing contact angle, and f is the bearing diameter. r This represents the rotor speed.

[0096] The transmission path modulation function for the impact of the inner raceway defect is:

[0097] a i (t)= i cos(φ(t)+Δφ0)+ i0

[0098] Among them, A iLet a be the transmission coefficient of the inner raceway impact. i0 This refers to the transmitted DC component. Typically, ||a i (t)‖≤1, we can let a i0 =0.5,A i =0.3.

[0099] The high-frequency resonant decay response function of a unit pulse is:

[0100]

[0101] Where ρ is the initial amplitude, B is the attenuation parameter, which is usually related to the system damping; the larger B is, the faster the high-frequency vibration attenuates. n This is the resonant frequency of the rotor-bearing system, which can be set to 6000Hz.

[0102] Therefore, the vibration signal of the bearing inner raceway fault can be obtained as follows:

[0103]

[0104] The method for obtaining the vibration signal of a bearing outer raceway fault in a rotor-bearing system includes the steps of obtaining the vibration signal of the bearing outer raceway fault based on the load equation of the bearing outer raceway defect region, through the outer raceway impact function, the outer raceway defect vibration transmission path effect function, and the unit pulse high-frequency resonance attenuation response function. The load equation for the bearing outer raceway defect region is as follows:

[0105]

[0106] Where, γ o This refers to the phase of a single-point defect in the outer raceway.

[0107] The outer raceway impact function is,

[0108]

[0109] Where, p o0 T represents the amplitude of the outer raceway impact function. BPFO Let δ be the period of the outer raceway impact function, k be an integer, and δ be the pulse function.

[0110] The period T of the outer raceway impact function BPFO It can be represented as,

[0111] T BPFO =1 / f BPFO

[0112] f BPFO The characteristic frequency of defects in the outer raceway of a bearing is the frequency at which the roller passes through the defect area of ​​the outer raceway per revolution of the shaft, expressed as:

[0113]

[0114] The vibration transmission path effect function of the outer raceway defect is:

[0115] a o (t)= o

[0116] Among them, A O It is the transmission coefficient of the outer raceway impact, usually A o <1.

[0117] Therefore, the vibration signal of the bearing outer raceway fault can be obtained as follows:

[0118]

[0119] The following section will verify the method provided by the invention for obtaining vibration signals of bearing inner and outer raceway faults.

[0120] First, the two methods provided by this invention are simulated.

[0121] The parameter selection is as follows, m r =10kg, e=10 -5 f BPFI =6.81, f BPFo =5.52, i =0.3,a i0 =0.51, A o =0.71, ρ=0.07, f n =6000, B=-80.

[0122] For vibration signals from bearing inner raceway faults, such as Figure 6 As shown, when the phase difference Δφ0 between the inner raceway defect location and the rotor's unbalanced centrifugal force is 0, envelope analysis is performed on the signal after simulations at low speed, medium speed, and high speed. The low-speed state is... Medium speed state High-speed state is In addition, such as Figure 7 As shown, while still at high speed, let Δφ0 be respectively and The simulation was performed under the specified conditions, followed by envelope analysis of the signal. In this embodiment, the low-speed, medium-speed, and high-speed states during the simulation were 1000 RPM, 6000 RPM, and 12000 RPM, respectively.

[0123] For vibration signals from bearing outer raceway faults, such as Figure 8 As shown, simulations were performed at low speed, medium speed, and high speed, respectively. Then, envelope analysis was performed on the signal. The definitions and values ​​of the low speed, medium speed, and high speed states are as described above.

[0124] Then, the vibration signals of the bearing's inner and outer raceways were obtained through experimental measurements.

[0125] like Figure 2 As shown, a rotor-bearing experimental test setup was constructed. A motor directly drives the shaft to rotate via a coupling. A disk is fixedly mounted in the middle of the shaft, and the rotor-shaft is supported on bearing housings at both ends by bearings. The driving end bearing is a healthy bearing, while the faulty bearing is installed at the driven end. Acceleration sensors are installed horizontally and vertically on the driven end bearing housing, and a tachometer is used to measure the shaft speed. Speed ​​pulse signals and vibration acceleration signals are acquired using a National Instruments (NI) acquisition module. The sampling frequency is set to 51.2 kHz, and the sampling duration for each data set is uniformly 10 seconds.

[0126] like Figure 3 As shown, the turntable has a mass of 1.82 kg and a diameter of 0.156 m. The turntable is circumferentially dotted with mounting holes, allowing for the addition of mass blocks via bolts to alter its imbalance. After assembling the turntable into the rotor-bearing experimental testing device, the initial imbalance was calculated to be 2.57 g / -110° (phase referenced to the reflective strip of the speed sensor). Adding a 2.57 g mass block in the opposite phase eliminated the initial imbalance, achieving dynamic balance for the rotor-bearing testing device.

[0127] The faulty bearings were respectively treated as follows Figure 4 The bearing with internal raceway defects shown and such Figure 5 The bearing shown has an outer raceway defect. The specific parameters of the rotor-bearing system are shown in the table below:

[0128]

[0129] For the vibration signal of a bearing inner raceway fault, a mass block with u = 5g is installed in the direction Δφ0 = 0 to simulate the unbalanced centrifugal force exerted by the turntable on the rotor-bearing system. The equivalent eccentricity is e = 4.28 × 10⁻⁶. -4 Based on the relationship between the rotor's self-weight and the unbalanced centrifugal force, the critical speed at which the unbalanced centrifugal force exceeds the rotor's self-weight can be calculated to be f0 ≈ 1500 RPM. Figure 9As shown, the vibration signals of the inner raceway fault were tested at three speeds: low speed (300 RPM), medium speed (1200 RPM), and high speed (2400 RPM). Then, the vibration signal measured by the vertical accelerometer of the bearing housing was bandpass filtered (3000 Hz to 7000 Hz) and synchronous envelope analysis was performed to obtain the envelope order spectrum of the bearing vibration at the corresponding speed.

[0130] For vibration signals from bearing inner raceway faults, such as Figure 10 As shown, the phase difference Δφ0 between the defects on the turntable and the inner raceway is respectively... and A mass block with u = 5g was installed in the direction of the bearing to test the fault vibration signal of the inner raceway at high speed (2400RPM), and then envelope analysis was performed.

[0131] For vibration signals from bearing outer raceway faults, such as Figure 11 As shown, a mass block with u = 5g is installed on the turntable, and the vibration signal of the outer raceway fault is tested under three conditions: low speed (300RPM), medium speed (1200RPM), and high speed (2400RPM). Envelope analysis is also performed after bandpass filtering.

[0132] By comparing the envelope spectrum of the bearing inner raceway fault vibration signal obtained from simulation, it can be found that the envelope spectrum of the bearing inner raceway fault vibration signal obtained from experimental measurement exhibits consistent characteristics. This indicates that the method for obtaining bearing inner raceway fault vibration signals provided by this invention can realistically simulate the experimentally measured bearing inner raceway fault vibration signals. Furthermore, it was found that the larger the phase difference Δφ0 between the rotor unbalance centrifugal force and the inner raceway defect region, the significantly reduced the number of time-domain impacts during bearing vibration due to the inner raceway defect, the lower the vibration amplitude, and the less significant the characteristic order on the envelope spectrum, indicating a "false healthy state."

[0133] In this embodiment, the bearing inner and outer raceway fault vibration signals obtained by the two methods in this embodiment can accurately reflect the influence of rotor imbalance centrifugal force on the vibration behavior of bearings with raceway defects in the high-speed rotor-bearing system. In turn, it can accurately simulate the vibration signal and sideband characteristics of the envelope spectrum of the bearing with raceway defects in the high-speed rotor-bearing system. Thus, it can replace the bearing fault vibration signal obtained by the traditional method of obtaining bearing fault vibration signal as the training input for intelligent bearing diagnosis to obtain the corresponding fault label, which is time-saving, cost-effective and has a short experimental cycle.

[0134] In this embodiment, the method for obtaining the bearing inner raceway fault vibration signal also considers the phase difference Δφ0 between the bearing inner raceway defect location and the rotor unbalanced centrifugal force. This allows for the simulation of the bearing inner raceway fault vibration signal in a "false health state" of the rotor-bearing system. This signal can then be used as training input for bearing intelligent diagnosis to obtain the corresponding fault label for the false health state. If a state label with the same fault label appears when the actual measured bearing vibration signal is used for bearing intelligent diagnosis, it can be determined that the bearing is not in a true health state but in a false health state.

[0135] In this embodiment, the locations of defects in the inner and outer raceways of the bearing can be set manually to obtain different vibration signals from these defects. Similarly, since the process is performed through digital simulation, vibration signals from the inner and outer raceways of the bearing at different speeds can be obtained.

[0136] The foregoing description of the specifications and embodiments is intended to explain the scope of protection of this invention, but does not constitute a limitation on the scope of protection of this invention. Modifications, equivalent substitutions, or other improvements to the embodiments of this invention or a portion thereof that can be obtained by those skilled in the art through logical analysis, reasoning, or limited experimentation, based on the teachings of this invention or the foregoing embodiments, in conjunction with common knowledge, general technical knowledge, and / or existing technology, should all be included within the scope of protection of this invention.

Claims

1. A method of simulating a bearing inner race fault vibration signal of a rotor-bearing system, characterized by, The method includes the following steps: obtaining the bearing inner raceway fault vibration signal based on the load equation of the bearing inner raceway defect region, through the inner raceway impact function, the transmission path modulation function of the inner raceway defect impact, and the unit pulse high-frequency resonance attenuation response function. The load equation for the bearing inner raceway defect region is as follows: in, This refers to the phase of the rotor's unbalanced centrifugal force. The phase difference between the location of the inner raceway defect and the unbalanced centrifugal force of the rotor. For internal raceway defects Phase of time, For load distribution factor, For bearing parameters, ball bearings are... Roller bearings , The maximum phase angle of the bearing load-bearing area. , for The magnitude of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at any given time is expressed as follows: in, , , These are the rotor's equivalent mass, equivalent eccentricity, and rotor speed, respectively. It is the acceleration due to gravity; for The phase angle of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at any given moment is expressed as follows: 。 2. The method for simulating vibration signals of bearing inner raceway faults in a rotor-bearing system as described in claim 1, characterized in that, The inner raceway impact function is: in, The amplitude of the inner raceway impact function. Let be the period of the inner raceway impact function. It is an integer. It is an impulse function.

3. The method for simulating vibration signals of bearing inner raceway faults in a rotor-bearing system as described in claim 2, characterized in that, The transmission path modulation function of the impact from the inner raceway defect is as follows: in, The transmission coefficient of the impact on the inner raceway is denoted as . The transmitted DC component.

4. The method for simulating vibration signals of bearing inner raceway faults in a rotor-bearing system as described in claim 3, characterized in that, The unit pulse high-frequency resonant attenuation response function is: in The initial amplitude, For attenuation parameters, This is the resonant frequency of the rotor-bearing system.

5. The method for simulating vibration signals of bearing inner raceway faults in a rotor-bearing system as described in claim 4, characterized in that, The vibration signal of the bearing inner raceway fault is as follows: 。 6. A method for simulating vibration signals from a fault in the outer raceway of a rotor-bearing system, characterized in that, The method includes the steps of obtaining the bearing outer raceway fault vibration signal through the outer raceway impact function, the outer raceway defect vibration transmission path effect function, and the unit pulse high-frequency resonance attenuation response function, based on the load equation of the bearing outer raceway defect region. The load equation for the bearing outer raceway defect region is as follows: in, For the phase of a single-point defect in the outer raceway, For load distribution factor, For bearing parameters, ball bearings are... Roller bearings , The maximum phase angle of the bearing load-bearing area. , for The magnitude of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at any given time is expressed as follows: in, , , These are the rotor's equivalent mass, equivalent eccentricity, and rotor speed, respectively. It is the acceleration due to gravity; for The phase angle of the resultant load of the rotor's unbalanced centrifugal force and its own weight on the bearing at any given moment is expressed as follows: 。 7. The method for simulating vibration signals of bearing outer raceway faults in a rotor-bearing system as described in claim 6, characterized in that, The outer raceway impact function is: in, The amplitude of the outer raceway impact function. Let be the period of the outer raceway impact function. It is an integer. It is an impulse function.

8. The method for simulating vibration signals of bearing outer raceway faults in a rotor-bearing system as described in claim 7, characterized in that, The vibration transmission path effect function of the outer raceway defect is: in, It is the transmission coefficient of the impact on the outer raceway.

9. The method for simulating vibration signals of bearing outer raceway faults in a rotor-bearing system as described in claim 8, characterized in that, The unit pulse high-frequency resonant attenuation response function is: in The initial amplitude, For attenuation parameters, This is the resonant frequency of the rotor-bearing system.

10. The method for simulating vibration signals of bearing outer raceway faults in a rotor-bearing system as described in claim 9, characterized in that, The vibration signal of the bearing outer raceway fault is as follows: 。

Images