Research Article  Open Access
Feng Li, Xinyu Pang, Zhaojian Yang, "Joint Amplitude and Frequency Demodulation Analysis Based on Variational Mode Decomposition for Multifault Diagnosis of a Multistage Reducer", Shock and Vibration, vol. 2018, Article ID 9869561, 19 pages, 2018. https://doi.org/10.1155/2018/9869561
Joint Amplitude and Frequency Demodulation Analysis Based on Variational Mode Decomposition for Multifault Diagnosis of a Multistage Reducer
Abstract
Multistage reducer vibration signals have complicated spectral structures owing to the amplitude and frequency modulations of gear damageinduced vibrations and the multiplicative amplitude modulation effect caused by timevarying vibration transfer paths (in the case of local gear damage) when the multistage reducer contains both planetary and spur gears. Moreover, the difference between the vibration energies of these gears increases the difficulty of fault feature extraction when multiple failures occur in the reducer. As the meshing frequency of each gear group often varies significantly, variational mode decomposition can be performed to decompose the vibration signal according to frequency, enabling separation of the vibration signals of the spur and planetary gears. The common fault features of these gears can be extracted from the spectrum of the amplitude demodulation envelope. To verify the effectiveness of this method, we first analyzed a simulation signal, and then utilized the experimental signals from a laboratory multistage reducer for verification. In the multistage reducer simulation, we considered the amplitude and frequency modulation of the gear damage and transfer paths. In the experimental verification, we processed local faults (broken teeth) and uniform faults (uniform wear) on the sun gear and the spur gear of the planetary gear separately.
1. Introduction
Multistage reducers are used extensively as key components in industry because of their compact structures, large transmission ratios, strong carrying capacities, stable operation, and high efficiencies [1, 2]. Further, as singlestage reducers can no longer meet the requirements of many types of engineering machinery, automobiles, aircraft, ships, and other equipment, multistage gear drives with multistage reducers are now essential. However, because multispeed reducers often contain multiple spur, planetary gears, or a combination thereof, the housing vibration signals of the gearbox are more complex than that of singlestage reducers, especially when planetary gears are involved [3]. Further, as reducer failure may lead to mechanical failure or even accidents, reducer fault diagnosis is very important.
The structure of a spur gear is simple, and the vibration signal mainly includes the rotation frequency, meshing frequency, and harmonic component. A planetary gear usually consists of a sun gear, several planet wheels, a ring gear, and a planet carrier. Usually, the ring gear is stationary, the sun gear rotates, and the planet gears not only revolve with the planet carrier, but also spin around their own centers. Because of the complicated internal dynamics and external environmental excitation, the vibration signals of planetary gears exhibit complex timevarying modulation, which leads to fault feature extraction difficulty [1]. In practice, to achieve more effective transmission, a planetary gear is often used with a spur gear, which makes the multistage reducer vibration signal more complex. When many gear faults occur in a multistage reducer, modulation of the gear faults and transmission paths to the vibration signal and the difference between the vibration energies of the gear groups increase the difficulty of diagnosing multiple simultaneous failures.
Many scholars have conducted extensive research on single reducer fault diagnosis. In particular, spur gear fault diagnosis has been studied extensively, and many related methods have been proposed. The proposed methods include timefrequency analysis, a wavelet method, ensemble empirical mode decomposition (EEMD), and a particle swarm optimization algorithm [4–7]. The fault types investigated include tooth surface damage, tooth breaking, wear, pitting, and cracking. In recent years, the amount of planetary gear fault diagnosis research has gradually increased. Lei et al. [8] proposed an adaptive stochastic resonance method that extracts the weak fault features of planetary gearboxes and detects sun gear faults, including chipped and missing teeth, successfully. Bartelmus and Zimroz [9] presented an indicator for monitoring planetary gearboxes under timevariable operating conditions, which is the linear dependence between the meshing frequency amplitude and operating conditions. McFadden [10, 11] and Samuel and Pines [12] generalized the timedomain averaging method, and respectively proposed planet and sun gear vibration separation methods. Barszcz and Randall [13] detected gear cracks in wind turbine planetary gearboxes by spectral kurtosis. Zhang et al. [14, 15] proposed a novel denoising structure and applied it to vibration signals collected from a seededfault testbed of the main gearbox of a helicopter. The proposed structure integrates a denoising algorithm, feature extraction, failure prognosis, and vibration modeling into a synergistic system. Chen and Feng [16] used reassigned wavelet scalograms to extract fault features from wind turbine planetary gearbox vibration signals. Feng et al. [17–20] summarized the amplitude modulation (AM) and frequency modulation (FM) characteristics in planetary gearbox vibration signals and diagnosed planetary gear faults through a variety of demodulation methods.
There are also a few studies on multiple gearbox faults. Lin and Chen [21] applied the EEMDbased method to diagnose multiple gearbox faults and successfully extracted multiple faults information from the collected signal. Teng et al. [22] proposed a complex wavelet transformbased method that can provide multiscale enveloping spectrograms (MuSEnSs) to decompose and demodulate signals simultaneously. Using this method, the weak bearing fault features buried in intensive energies can be detected readily by analyzing MuSEnSs at different scales. Zhang and Yu [23] proposed a novel resonancebased signal sparse decomposition (RSSD) with comb filter (CF) method in which the collected signal is firstly separated into high and low resonance components by using the RSSD method with optimal decomposition parameters. Then, both the high and low resonance components are demodulated by performing Hilbert transforms, and the fault information can be found in the Hilbert envelope spectra. Finally, a CF is constructed to extract the weaker fault feature signal from the resonance components and exclude the interference components. The studies cited above primarily focused on bearing and gear faults; there are only a few studies on simultaneous planetary and spur gear failure in reducers.
Usually, when a reducer gear fails, sensors are fixed near the planetary or spur gear, so that the vibration signal can be acquired more effectively [24]. When faults occur in a multistage reducer, the sensor should be fixed in the middle of the reducer box to collect the vibration signal of each gear. In particular, when there are planetary gears, the meshing positions of the sun and planet gears and that of the planet and ring gears are time varying with respect to the sensor, which results in vibration signal AM and makes the vibration signal more complex [25].
Some scholars have performed reducer vibration signal simulation research. Chaari et al. [26] studied the AM and FM characteristics of the vibration signal of a fixedshaft gearbox by constructing a timevarying meshing stiffness. Omar et al. [27] built a nine degreeoffreedom model of one stage of a gear system. The model considers varying meshing stiffness, gear size, errors, and faults. Wang and McFadden [5] built a nonlinear vibration model of spur gears considering nonlinear factors such as stiffness excitation, tooth wear, and gap variation. In all these methods, vibration signals are obtained by constructing differential equations. However, it is difficult to solve the equations, and the effects of the transmission path are not considered.
Regarding planetary gears, McFadden and Smith [28], McNames [29], and Mosher [30] studied the spectral structure of planetary gearbox vibration signals and found that the vibration signal spectrum is typically asymmetric, but they did not consider factors such as the FM effect in the signal modeling. Inalpolat and Kahraman [31] proposed a mathematical model to describe the vibration signal sidebands of planetary gearboxes. Inalpolat and Kahraman [32] found that vibration signals have very complicated sidebands by studying the spectral characteristics of planetary gearbox vibration signals considering the AM caused by the planet carrier rotation and AMFM resulting from manufacturing errors. Mark and Hines [33] studied the effects of nonuniform planet loading due to gear imperfections in the sidebands of the vibration response, as well as the effects of planet carrier torque modulation. Feng and Zuo [25] developed gear damageinduced vibration signal models for planetary gearbox fault diagnosis, considering the AMFM nature of locally and diffusely damaged gear vibrations and the AM effect of timevarying vibration transfer paths, derived their Fourier spectra in closed form, and provided explicit equations for calculating the characteristic frequency of each gear in a planetary gearbox. However, the influences of the spur gear and transmission path on the vibration signal when the sensor positions are different were not considered.
Recently, some scholars have studied multistage reducer vibration signal modeling. Raclot and Velex [34] introduced a mathematical model for simulating the contributions of shape deviations and mounting errors to the dynamic behaviors of single and multimesh geared systems. Walha et al. [35] analyzed the nonlinear dynamic system response by developing a 12 degreeoffreedom gear dynamic model that takes into account the meshing stiffness and gap changes with time. Yassine et al. [36] calculated the dynamic response of vibrations by using the Newmark method, which involves stepbystep time integration, and considers the periodic fluctuations of the mesh stiffness, eccentricity defects, profile errors, and cracked teeth. These vibration signals are obtained by solving kinetic equations, but the calculations are complex. Furthermore, the effect of the transmission path on the reducer vibration signal was not considered. Only a single fault was analyzed, which is different from the actual situation.
In this study, we generated the vibration signal of a multistage reducer with AM and FM caused by a timevarying transmission path, rotation frequency, and fault frequency. An explicit equation was developed to simulate the vibration signal of a multispeed reducer, and the structure of the vibration signal spectrum was obtained from the corresponding Fourier transform. In a multistage reducer, the meshing frequencies of each gear group change significantly because of rotation speed variations. Thus, the AM and FM of the gears at each level occur in different frequency bands. Based on this vibration signal property, this paper proposes a method of frequency and amplitude demodulation with combined variational mode decomposition (VMD) and envelope demodulation. The proposed method is significantly different from the demodulation methods used in the previous studies. When multiple failures occur, if empirical mode decomposition (EMD), EEMD, or local mean decomposition (LMD) is used to demodulate the reducer vibration signal, it cannot be ensured that the obtained separation signal contains the desired fault features. Furthermore, the number of signal demodulation layers cannot be determined if EMD, EEMD, or LMD is used, which makes it difficult to select a useful decomposition signal. In contrast, the reducer vibration signal can be decomposed according to the required frequency band because of the advantages of VMD. In this way, decomposition signals containing fault features can easily be acquired. Then, the fault features can be clearly obtained by analyzing the decomposition signal envelope. Notably, when the multistage reducer contains planetary and spur gears, their meshing frequencies often differ, which makes the method proposed in this paper widely applicable.
The remainder of this paper is organized as follows: The second section explains the principles of the VMD algorithm and the related algorithmic program. The third section describes the multistage reducer vibration signal model. The fourth section describes the application of the proposed method to a simulation signal. The fifth section discusses the verification conducted of the proposed method by presenting the analysis of experimental signals obtained when local damage (broken teeth) or distributed damage (uniform wear) occurred in the planetary and spur gears simultaneously. The sixth section presents concluding remarks.
2. Principles and Methods
2.1. VMD Principle
VMD is a multicomponent signal adaptive decomposition method proposed by Dragomiretskiy and Zosso [37]. To date, it has been used in areas such as bearing fault diagnosis, rotor rubbing, and speech signal detection. VMD can be employed to decompose a realvalued signal into a discrete number of subsignals based on the specific sparsity properties of its bandwidth in the spectral domain. The bandwidth of a mode can be assessed via a constrained variational optimization problem with the following scheme:(1)The real signal is transformed into an analytical signal by performing a Hilbert transform to form a onesided frequency spectrum of the signal.(2)The frequency spectrum of each mode is shifted to the baseband by mixing with an exponential function tuned to the relevant estimated center frequency.(3)The bandwidth of a mode is estimated based on the Gaussian smoothness of the demodulated signal, i.e., the squared norm of the gradient.
The constrained variational problem can be written as
In Equation (1), is the mode of the signal, is the set of modes is the center frequency of the mode, is the set of center frequencies of the modes is the signal to be decomposed, and is the Dirac function.
Equation (1) can be expressed as an unconstrained optimization problem by introducing a quadratic penalty and Lagrangian multipliers. The modified equation with the augmented Lagrangian can be written aswhere represents the balancing parameter of the datafidelity constraint.
Equation (2) is solved using the alternate direction method of multipliers. All the estimated modes in the frequency domain are expressed aswhere , , , and are the Fourier transforms of , and , respectively. Note that Equation (3) is a Wiener filtering structure. The mode in the time domain can be obtained from the real part of the inverse Fourier transform of this filtered analytic signal.
The complete VMD algorithm can be summarized as follows:(1)Initialization: let , , , and be zero and predefine a convergence threshold and the number of intrinsic mode functions (IMFs) K to be separated.(2)Update each IMF and its associated center frequency , for and :(3)Update the Lagrangian multiplier for all :where is the Lagrangian multiplier update parameter.(4)Check the convergence condition:
If it is met, let and and terminate the decomposition. Otherwise, let and return to Step 2.
2.2. Procedure
The basic steps of the signal processing algorithm proposed in this paper are as follows: Firstly, to avoid the influence of highfrequency harmonics, a lowpass filter is used to filter the vibration signal. Then, VMD is performed to decompose the filtered vibration signal to obtain three VIMFs (the IMFs acquired by VMD) ranging from low frequency to high frequency. Finally, the envelope spectrum is employed to analyze VIMF1 and VIMF3, which, respectively, include the spur gear and planetary gear vibration information. Multiple multistage reducer faults can be diagnosed by observing the characteristic frequency changes of the gear fault envelope spectrum.
3. Vibration Signal Model
The sensor is usually fixed onto the multistage reducer box when measuring vibrations. Vibration signals are transmitted to the sensor through multiple paths when the gears mesh. The vibration signals of each gear group are addressed in this section.
3.1. Gear Vibration Signal Model
The vibration signals of each gear group (with no distinction between planetary and spur gears) in a fault reducer can be modeled by the AM and FM process. The meshing frequency of the gears or their multiple frequencies is the carrier frequency of the signal, and the characteristic frequency of the damaged gear or its multiple frequencies is the modulation frequency.
The model of normal gear meshing vibration is as follows:where is the influence of the transmission path on the vibration signal, is the meshing vibration of the normal gear, is the highest order, is the meshing frequency, and is the initial phase.
When the gear is damaged,where is the AM function caused by the fault, is the meshing vibration of the faulty gear, and is the FM function caused by the fault:where is a dimensionless constant dependent on the signal amplitude; are the AM and FM coefficients, respectively ; are the initial phases; is the characteristic frequency of the fault; and and are the highest orders of modulation.
3.2. Influence of the Transmission Path
In a multistage reducer, the vibration signal generated by each gear group is transmitted to the sensor along multiple paths. We analyzed the influence of the transmission path on the vibration signal by using an example of a threestage gear transmission system (including a planetary gear and two spur gears, as shown in Figure 1). We discuss the planetary and spur gears separately as their transmission paths are different. For simplicity, we only consider the case of order 1 ().
3.2.1. Planetary Gear Vibration Signal
A planetary gear is typically composed of a sun gear, several planet gears, and a ring gear. Usually, the ring gear is stationary, and the sun and planet gears as well as the planet and ring gears mesh simultaneously. Owing to the revolution of the planet gears, the transmission path between the meshing point and sensor varies periodically. Figure 1 shows six transmission paths according to planetary gear. Taking a planet gear as the object of analysis, the transmission of a vibration signal from the meshing point of the planetary and sun gears to the sensor occurs along paths 1–3 in Figure 1, and that from the meshing point of the planetary and ring gears to the sensor occurs along paths 4–6. In addition to these six transmission paths, the vibrations will be transmitted to the sensor through the oil, box, etc. However, these vibrations are weak and therefore are not addressed in this article.
The transmission paths of the planetary gear are as follows: Path 1: sun gear ⟶ sun gear shaft ⟶ reducer box ⟶ sensor Path 2: sun gear ⟶ planet gear ⟶ ring gear ⟶ reducer box ⟶ sensor Path 3: sun gear ⟶ planetary gear ⟶ planet gear shaft ⟶ planet carrier ⟶ reducer box ⟶ sensor Path 4: planet gear ⟶ sun gear ⟶ sun gear shift ⟶ reducer box ⟶ sensor Path 5: planet gear ⟶ planet gear shift ⟶ planet carrier ⟶ reducer box ⟶ sensor Path 6: planet gear ⟶ ring gear ⟶ reducer box ⟶ sensor
For transmission paths 2 and 6, the position of the meshing point of each gear pair changes constantly. The time variation of the meshing point location makes the distance between the vibration source and sensor change periodically. The vibration signal amplitude measured by the sensor is large when the planet gear is rotated just below the sensor. Conversely, this amplitude is small when the planet wheel is rotated away from the sensor. Therefore, transmission paths 2 and 6 modulate the vibration signal amplitude. The modulation frequency is the planet gear revolution frequency, that is, the planet carrier rotation frequency. The remaining four transmission paths will not change owing to the planet gear revolution. They will change the vibration signal amplitude but will not introduce a new modulation frequency. The signals of these four paths are considered as a whole when simulating the vibration signal. Transmission paths 2 and 6 can be represented by Hanning windows, and they are synchronous. The lengths of transmission paths 2 and 6 are different; thus, the attenuation is different. is the function of transmission path 6 where the first planet gear and ring gear mesh, and is the function of transmission path 2 where the first planet gear and sun gear mesh:where is an attenuation coefficient and , and is the planet carrier rotation frequency.
For transmission path 6, the transmission paths of the other planet gears arewhere is the planet gear revolution period.
For transfer path 2, the transmission paths of the other planet gears are
The transfer functions of the remaining four paths can be considered to be constants, where paths 1 and 3 are expressed in , and paths 4 and 5 are expressed in .
Therefore, considering the influence of all the paths, the vibration signal of the planetary gear can be represented as follows:where and are the meshing vibrations of planet gear with the ring gear and sun gear, respectively, and is the number of planet gears:
When the sun gear has a fault,
Further, when the planet gear has a fault (assuming the failure of planet gear j),
The form of is similar to that of .
3.2.2. Spur Gear Vibration Signal
The spur gear transmission path is simple. When the normal gear is meshing, the vibration signal is mainly derived from the meshing position of the gear. The transmission path of the signal to the sensor is mainly along the two gear shafts (paths 7–10 in Figure 1). As these paths are not time varying, they only affect the vibration signal amplitude. These four transfer path functions are regarded as a constant :
The vibration signals of a spur gear fault can be expressed as
3.3. Characteristic Frequency of Faulty Gear
3.3.1. Characteristic Frequency of Faulty Planetary Gear
(1) Characteristic Frequency of Local Gear Damage. Sun Gear
In each relative rotating cycle, a damaged sun gear tooth comes into contact with all of the planet gears. Thus, the characteristic frequency of a locally damaged sun gear is equal to the number of planet gears times the relative rotation frequency of the sun gear with respect to the planet carrier: Planet Gear
A locally damaged planet gear has two characteristic frequencies because it contacts the ring and sun gears simultaneously. One of those frequencies is
If the damage exists on one side of the planet gear tooth, the damaged area contacts mating gears (either the sun or ring gear) only once in each relative rotating cycle. Meanwhile, if the damage occurs on both sides of the planet gear tooth, the damaged area contacts mating gears (both the sun and ring gears) twice in each relative rotating cycle, and the frequency is twice that of Equation (20): Ring Gear
Similarly, the characteristic frequency of a locally damaged ring gear is
(2) Characteristic Frequency of Distributed Gear Damage. In the case of distributed gear damage, the characteristic frequency of a faulty gear is defined as its rotation frequency relative to the planet carrier (in the cases of sun and ring gear damage) or to the ring gear (in the case of planet gear damage), because distributed gear damage modulates the gear meshing vibrations with a period equal to the damaged gear rotating cycle relative to the planet carrier or ring gear. In this sense, the characteristic frequencies of planet, sun, and ring gears with distributed damage can be calculated using
3.3.2. Characteristic Frequency of Faulty Spur Gear
The characteristic frequencies of a faulty spur gear with local and distributed damage arerespectively.
4. Simulated Signal Analysis
To illustrate the effectiveness of the proposed method, we simulated the vibration signal of a threestage reducer (including one planetary gear and two spur gears). The firststage planetary gear and thirdstage spur gear were equipped with gear faults separately. Without loss of generality, we ignored the influence of the initial phase and focused on analyzing the meshing and characteristic frequencies of the faults. To simulate the background noise interference, we added Gaussian noise , and the signaltonoise ratio was 20 dB. The simulation signal model was as follows:where
The relevant parameters in these formulas are listed in Table 1. The parameters of the related frequencies were obtained based on the experimental data (the simulation signal corresponds to the actual fault type Sun Gear WearSpur Gear Broken Teeth). The coefficients were obtained based on the amplitude of the actual vibration signal and rounded off. We tried to make the amplitude of the simulation signal similar to that of the actual vibration signal by adjusting the coefficients. This ensures that the ratio of the vibrational energy of the spur gear to the planetary gear is similar to that of the actual vibration signal. It further ensures that the fault feature signal of the spur gear is submerged in the simulation signal like the reality. The sampling frequency was set to 2000 Hz.

We analyzed the simulation signals in accordance with the program described in Section 2.2. The results are shown in Figure 2.
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Figure 2(b) shows the Fourier spectrum of the simulation signal. In the frequency domain, virtually all of the prominent spectral peaks appear at the expected characteristic frequencies—such as the meshing frequencies of spur gears 1 () and 2 (), their product frequencies (, ), and the planetary gear meshing frequency (). There is a sideband () associated with the spur gear failure frequency near the meshing frequency of spur gear 2. Complex sidebands appear near the planetary gear meshing frequency, including peaks such as those at , , , , and . Because the spur gear vibration energy is less than that of the planetary gear, and the planetary gear spectrum is complex, it is difficult to diagnose the gear faults via traditional Fourier spectrum analysis when the spur and sun gears fail simultaneously.
Figure 2(c) depicts the simulation signal envelope spectrum and clearly reveals the carrier frequency (), sun gear fault characteristic frequency (), and modulation frequency between them (). However, the spur gear fault features do not appear in the envelope spectrum. Therefore, to extract the fault information of each gear effectively, we used the method proposed in this paper. We employed VMD to decompose the simulation signal and obtain VIMFs (Figure 2(d)). The instantaneous frequency spectrogram shows that the frequency of VIMF1 is mainly concentrated in the 0–300 Hz range, which mainly contains the vibration information of spur gear 2, and the frequency of VIMF3 is mainly focused in the 600–800 Hz range, which mainly contains the vibration information of the sun wheel. Envelope spectra were acquired separately for VIMF1 and VIMF3.
Figure 2(e) clearly shows the fault feature frequency of the spur gears (), its modulation frequency, and the meshing frequency of spur gear 2 (). Figure 2(f) clearly provides the fault feature frequencies of the sun gear () and the planet carrier (). Compared with the traditional Fourier transform, Figures 2(e) and 2(f) more clearly show the gears corresponding to the fault characteristics. Thus, the proposed method not only enables effective diagnosis of spur gear faults, but also facilitates planetary gear fault diagnosis. The above simulation signal analysis illustrates the effectiveness of the proposed method for extracting multiple faults in a multistage reducer.
5. Experimental Signal Analysis
In this section, we verify the effectiveness of the proposed method by presenting experimental data. To obtain these data, we fabricated local faults (broken teeth) and distributed faults (uniform wear) on the planetary and spur gears of the reducer.
5.1. Experimental Specifications
Figure 3 shows the multistage reducer test rig. The reducer included three gear transmission stages: a firststage planetary gear, secondstage spur gear, and thirdstage spur gear. A magnetic powder brake was used to provide the entire system load. Table 2 lists the parameters of the multistage reducer test rig.

We processed the local faults (broken teeth) and distributed faults (uniform wear) on the sun gear of the firststage planetary gear and the secondstage spur gear. Figure 4 shows the different fault types of the sun and spur gears. We artificially destroyed about 20% of one sun gear tooth to represent a local fault (broken tooth) and cut about 0.3 mm off each sun gear tooth to represent a distributed fault (uniform wear). The same fault types were also processed on the thirdstage spur gear artificially. The other gears were normal in each experiment. In the experiment, we set the rotation frequency of the motor to 1800 rpm/min and the output torque of the magnetic brake to 1 N·m.
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The acceleration sensor was fixed in the middle of the reducer box so that the vibration information of the reducer at each gear stage could be collected. The vibration signal sampling frequency was 10 kHz.
According to the structure and rotation speed of the planetary and spur gears, the rotation frequency of the gears at each stage and the characteristic frequency of the faulty gear were calculated; the results are presented in Table 3.

5.2. Multifault Experiment Signal Analysis
In this section, we outline the experimental signal analysis performed using the program proposed in Section 2.2. We analyzed the experimental signals of the reducer box when the planet and spur gears experienced local faults (broken teeth) or distributed faults (uniform wear) to demonstrate the effectiveness of the method. In all the following figures, the blue line indicates the baseline signal and the red line indicates the fault signal.
5.2.1. Baseline: All of the Gears Are Perfect
Figures 5(a) and 5(b) depict the timedomain waveforms of the original and filtered vibration signals, respectively. From the spectrum of the filtered vibration signal (Figure 5(c)), the motor rotation frequency (), planetary gear meshing frequency (), spur gear meshing frequencies (, ), and multiples of the spur gear meshing frequencies (, ) can be identified. Sidebands appear near the spur gear meshing frequency, which is mainly caused by the gear shaft rotation frequency. There are also sidebands near the planetary gear meshing frequency, but the form is relatively complex, mainly because of the planet gear and planet carrier rotation frequencies and their combined frequency. Comparison of the amplitudes of the planetary and spur gear spectra shows that the spur gear vibration amplitude is smaller than that of planetary gear, especially for the thirdstage spur gear. Thus, the planetary gear vibration energy is greater than that of the spur gear. Therefore, only the characteristic frequency of the planetary gear can be seen in the vibration signal envelope spectrum. In the envelope spectrum, the rotation frequencies of the planet gear and planet carrier, multiples of their frequencies, and their combined frequency can be seen. The meshing frequency of the secondstage spur gear is observable, but the rotation frequency associated with the spur gear is not visible.
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After VMD decomposition, we obtained three VIMFs. Figure 5(e) presents the timedomain and timefrequency images for each VIMF, revealing that the three VIMFs are in different frequency bands. VIMF1 and VIMF3 mainly contain the vibration information of the spur and planetary gears, respectively. Then, the envelope spectra of VIMF1 and VIMF3 were obtained separately. Figure 5(f) shows the envelope spectrum of VIMF1, revealing the multiples of the rotating frequencies of the second spur gear () and the third spur gear (), the meshing frequency of the third spur gear (), and the modulation frequencies between them (, ) which are related to the characteristic frequency of the spur gears. Figure 5(g) depicts the envelope spectrum of VIMF3, revealing the rotation frequency of the planet carrier (), characteristic frequency of the planet gear (), characteristic frequency of the sun gear (), their multiples (, , ), and the modulation frequencies between them (), which are related to the characteristic frequency of the planetary gear. In an actual reducer, manufacturing and assembly error is inevitable, leading to the occurrence of these frequency components in the FM spectrum.
5.2.2. Sun Gear Broken TeethSpur Gear Broken Teeth
Figure 6 presents the vibration signal analysis results obtained when both the sun gear of the planetary gear and the driving thirdstage spur gear had broken teeth simultaneously. The fault characteristic frequency of the sun gear is and that of the spur gear is .
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The spectrogram of the vibration signal (Figure 6(b)) shows that some continuous peaks occur between the meshing frequency of the thirdstage spur gear () and four times that frequency (), because of the broken teeth of the spur gear. However, these peaks are not prominent. Some sidebands appear near the meshing frequency () of the planetary gear, including at the combinatorial frequency between the meshing frequency of the planetary gear and the sun gear fault characteristic frequency. In addition, there are the combinatorial frequencies (, , , , ) between the meshing frequency of the planetary gear () and 1/4 times the fault characteristic frequency (). Most likely, because manufacturing and assembly errors are inevitable in a real reducer, the four planet gears that meshed with the sun gear could not have been exactly the same; thus, the impacts of the sun and four planet gears differed. Some frequencies appear in the vibration signal envelope spectrum (Figure 6(c)), such as the sun gear fault characteristic frequency () and the frequencies associated with it (). However, there is no significant change in the spur gear fault characteristic frequency ().
After VMD decomposition, we obtained three VIMFs. Figure 6(d) shows the timedomain and timefrequency results for each one. VIMF1 and VIMF3 mainly contain the vibration information of the spur and planetary gears, respectively. Figure 6(e) shows the envelope spectrum of VIMF1, revealing that the spur gear fault characteristic frequency () is obviously increased, and the fault characteristic frequencies multiplied times 11–27 are increased as well. Thus, a broken tooth fault occurred in the spur gear. Figure 6(f) shows the envelope spectrum of VIMF3, where it can be seen that the sun gear fault characteristic frequency () is obviously increased, and those related to the sun gear fault characteristic frequency (, , ) are increased as well. These results indicate that a broken tooth fault occurred in the sun gear.
5.2.3. Sun Gear WearSpur Gear Wear
Figure 7 shows the vibration signal analysis results obtained when both the sun gear of the planetary gear and the driving gear of the thirdstage spur gear were worn simultaneously. The fault characteristic frequencies of the sun and spur gears are and , respectively.
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The vibration signal spectrogram (Figure 7(b)) shows that the thirdstage spur gear meshing frequency (), as well as two and three times the meshing frequency ( and , respectively), is increased slightly. The planetary gear meshing frequency () has increased, as has the peak of the sideband near the meshing frequency according to the sun gear fault characteristic frequency (). Some frequencies appear in the vibration signal envelope spectrum, such as the sun gear fault characteristic frequency and its associated frequencies (, , ). These characteristics indicate that the sun gear wear failure was identified, but the spur gear fault diagnosis was not satisfactory.
After VMD decomposition, it can be concluded from Figure 7(d) that VIMF1 and VIMF3 mainly contain the vibration information of the spur and planetary gears, respectively. Figure 7(e) shows the envelope spectrum of VIMF1, revealing that the spur gear fault characteristic frequency () is obviously increased. This feature indicates that wear fault occurred in the spur gear. Figure 7(f) presents the envelope spectrum of VIMF3, showing that the sun gear fault characteristic frequency () is obviously increased, as are its related frequencies (, ). Thus, a wear fault occurred in the sun gear.
5.2.4. Sun Gear Broken TeethSpur Gear Wear
Figure 8 shows the vibration signal analysis results obtained when the sun gear of the planetary gear had broken teeth and the driving gear of the thirdstage spur gear was simultaneously worn. The fault characteristic frequencies for the sun and spur gears are and , respectively.
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The vibration signal spectrogram (Figure 8(b)) shows that the meshing frequency of the thirdstage spur gear (), as well as two and three times that frequency ( and , respectively), is increased slightly. There are some sidebands near the planet gear meshing frequency (). It is clear that there is a combination of the sun gear meshing frequency and fault characteristic frequency in the sidebands (). There are combined frequencies of the meshing frequency and 1/4 times the sun gear fault characteristic frequency () in the sidebands simultaneously (, , , , ).
Some frequencies appear in the vibration signal envelope spectrum (Figure 8(c)), such as the sun gear fault characteristic frequency () and its associated frequencies (). However, there is no significant change in the spur gear fault characteristic frequency.
After VMD decomposition, it can be concluded from Figure 8(d) that VIMF1 and VIMF3 mainly contain the vibration information of the spur and planetary gears, respectively. Figure 8(e) shows the envelope spectrum of VIMF1, revealing that the spur gear fault characteristic frequency () is obviously increased. Thus, a wear fault occurred in the spur gear. Figure 8(f) presents the envelope spectrum of VIMF3, showing that the sun gear fault characteristic frequency () and its related frequencies (, , ) are increased. Thus, a broken teeth fault occurred in the sun gear.
5.2.5. Sun Gear WearSpur Gear Broken Teeth
Figure 9 shows the vibration signal analysis results obtained when the sun gear of the planetary gear was worn and the driving gear of the thirdstage spur gear simultaneously had broken teeth. The fault characteristic frequencies of the sun and spur gears are and , respectively.
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(f)
The vibration signal spectrogram (Figure 9(b)) shows that some continuous peaks occur between the meshing frequency of the thirdstage spur gear () and four times that frequency (), because of the broken teeth of the spur gear. However, these peaks are not prominent. The planetary gear meshing frequency () exhibits a certain increase, and the peaks in the sideband associated with the sun gear fault characteristic frequency (, , , ) are increased as well. The vibration signal envelope spectrum (Figure 9(c)) clearly reveals that the fault characteristic frequency () and the frequencies associated with it (, , , ) are increased. These features indicate that wear failure occurred on the sun gear, but the spur gear fault diagnosis is not ideal.
After VMD decomposition, it can be concluded from Figure 9(d) that VIMF1 and VIMF3 mainly contain the vibration information of the spur and planetary gears, respectively. Figure 9(e) depicts the envelope spectrum of VIMF1, showing that the spur gear fault characteristic frequency () is obviously increased and 11–27 times that frequency are increased as well. Thus, a broken tooth fault occurred in the spur gear. Figure 9(f) presents the envelope spectrum of VIMF3, revealing that the sun gear fault characteristic frequency () is obviously increased, as are the frequencies related to it (, , , ). Thus, a wear fault occurred in the sun gear.
6. Discussion
In the analysis results of the simulation signal, we could effectively extract the desired fault characteristic frequencies of the gears. However, the frequencies distribution of the simulation signal is simpler than the actual vibration signal because our focus is only on the ideal situation. We only considered the meshing frequency of all gears, the rotation frequency of the planet carrier, and the fault characteristic frequencies of the sun and spur gears. Although these are somewhat different from the actual situation, they sufficiently demonstrate the effectiveness of the proposed method.
When the reducer is running normally, assembly and machining errors are unavoidable, the planet gears are not exactly the same, and there are many other transmission paths for the vibration signal. Further, the gear meshing transmission has periodic fluctuations that can trigger the related vibration. Thus, the actual vibration signal is complex, and it is therefore reasonable that there are some frequencies in the spectrum figures.
When multiple faults occur in a multistage reducer, peaks in the VIMF envelope spectra do not appear at the fault characteristic frequencies of the gears and their harmonics, most likely because of manufacturing and assembling errors that are inevitable in actual multistage reducers. Therefore, it is reasonable to see other peaks in VIMF envelope spectra. The desired fault characteristic frequency of the gear can be obtained based on the envelope spectra of VIMF1 and VIMF3. Therefore, it is possible to diagnose planetary and spur gear failures by employing the proposed method.
To diagnose multiple faults in a multistage reducer, we proposed a method based on amplitude and frequency demodulation. In multistage reducer box vibration signal analysis of the spectrum and envelope spectrum directly, the spur gear fault characteristics are not obvious because its vibration energy is smaller than the vibration energy of the planetary gear. To recognize a spur gear fault, it is necessary to separate the spur gear vibration signal from that of the multistage reducer box. In a multistage reducer, the meshing frequencies of the gear stages are often in different frequency bands because of deceleration or acceleration. Therefore, the vibration signal of a multistage reducer box can be decomposed by frequency band, such that each frequency band contains the vibration information of different levels of gears. The VMD method can facilitate signal decomposition according to the expected frequency band, and the number of layers decomposed is manageable. To validate fully the effectiveness of the proposed method, we analyzed four different laboratory signals in a multistage reducer, where the sun gear of the planetary gear and the spur gear experienced local faults (broken teeth) or distributed faults (uniform wear). The experimental multistage reducer vibration signals were composed of various components generated by the planetary gear, spur gear, bearings, input/output shafts, and connected devices such as motors. They have the same multicomponent nature as those of a real industrial multistage reducer. Thus, they were sufficient to test the performance of the VMD demodulation method. The analysis results obtained using the four different datasets were all in line with our expectations.
We used VMD to decompose the vibration signals according to frequency band. The spur and planetary gear vibration information was included in VIMF1 and VIMF3, respectively, so their gear fault characteristic frequencies could clearly be seen in the corresponding envelope spectra. The experimental validation demonstrates the effectiveness of the proposed method and its potential for use in insitu applications.
7. Conclusions
To address fault characteristic frequency extraction when multiple faults occur simultaneously in a multistage reducer, we proposed a joint amplitude and frequency demodulation method to identify the characteristic frequencies of faulty gears in multistage reducer systems more effectively. In this technique, VMD is employed to decompose the signal into VIMFs such that each VIMF contains the vibration information of a gear stage. Then, the envelope spectrum of the VIMF of interest is calculated, and the gear faults are identified by the fault characteristic frequency peaks in the envelope spectra. The method was demonstrated by conducting simulated signal analysis, and its performance was validated experimentally using four experimental signals. In future work, we will collect industrial multistage reducer vibration datasets to validate the proposed method further. Throughout this study, we assumed that the multistage reducer rotation speed was constant. We are currently doing research to address this issue when the rotation speed fluctuates.
Data Availability
We cannot share the data because our project has not yet been completed.
Conflicts of Interest
The authors declare that they have no conflicts of interest.
Acknowledgments
This paper is supported by the National Natural Science Foundation of China (no. 51475318) and the Innovation Project in Postgraduate Education of Shanxi Province (no. 2016BY058). The authors are grateful to the anonymous reviewers for their valuable and detailed comments and suggestions, which have helped to improve this paper.
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