Shock and Vibration
Volume 2015 (2015), Article ID 542472, 12 pages
http://dx.doi.org/10.1155/2015/542472

Research Article

Cyclostationary Analysis for Gearbox and Bearing Fault Diagnosis

Zhipeng Feng¹ and Fulei Chu²

¹School of Mechanical Engineering, University of Science and Technology Beijing, Beijing 100083, China
²Department of Mechanical Engineering, Tsinghua University, Beijing 100084, China

Received 5 May 2015; Revised 24 July 2015; Accepted 27 July 2015

Academic Editor: Dong Wang

Copyright © 2015 Zhipeng Feng and Fulei Chu. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.

Abstract.

Gearbox and rolling element bearing vibration signals feature modulation, thus being cyclostationary. Therefore, the cyclic correlation and cyclic spectrum are suited to analyze their modulation characteristics and thereby extract gearbox and bearing fault symptoms. In order to thoroughly understand the cyclostationarity of gearbox and bearing vibrations, the explicit expressions of cyclic correlation and cyclic spectrum for amplitude modulation and frequency modulation (AM-FM) signals are derived, and their properties are summarized. The theoretical derivations are illustrated and validated by gearbox and bearing experimental signal analyses. The modulation characteristics caused by gearbox and bearing faults are extracted. In faulty gearbox and bearing cases, more peaks appear in cyclic correlation slice of 0 lag and cyclic spectrum, than in healthy cases. The gear and bearing faults are detected by checking the presence or monitoring the magnitude change of peaks in cyclic correlation and cyclic spectrum and are located according to the peak cyclic frequency locations or sideband frequency spacing.

1. Introduction

Gearboxes and rolling element bearings are critical mechanical components and widely used in many types of machinery [1–3]. Gear and bearing faults will result in deficiency of transmission or even shut-down of the entire machinery. Therefore, gearbox and bearing fault diagnosis play an important role.

The vibration signals of gearboxes and rolling element bearings are usually cyclostationary, since their statistics (in terms of ensemble average) change periodically with time due to their rotation. Hence, cyclostationary analysis is suitable to process gearbox and bearing vibration signals. Dalpiaz et al. [4] made a comparison study between various vibration signal analysis methods (including cepstrum, time-synchronous average, wavelet transform, and cyclostationary analysis) for gear localized fault detection, and they found spectral correlation density is effective in monitoring gear crack development. Sidahmed et al. [5, 6] showed that time-synchronous average can be considered as a first order cyclostationarity and spectral correlation as a second order cyclostationarity, found that gear vibration signals have second order cyclostationarity, and early detected gear tooth spalling using spectral correlation analysis. Zhu et al. [7] investigated the effectiveness of cyclostationarity from the first order to the third order, that is, spectrum of time-synchronous average, cyclic spectrum and cyclic bispectrum, in gearbox condition monitoring. Bi et al. [8] proposed to extract the amplitude modulation and phase modulation information from gear vibration signals using slice spectral correlation density, so as to detect gear defects. Li and Qu [9] deduced the cyclic correlation and cyclic spectrum of amplitude modulation signals and applied them to rolling element bearing fault diagnosis. Recently, Antoni et al. [10–15] conducted a series of researches on cyclostationary signal analysis and applied it to fault diagnosis of rotating machinery. To reduce the computational complexity of cyclic energy indicator based on cyclic spectral density, Wang and Shen [16] proposed an equivalent cyclic energy indicator for rolling element bearing degradation evaluation. These researches illustrate the effectiveness of cyclostationary analysis in gearbox and bearing fault diagnosis. However, the explicit relationship between the cyclostationary features of vibration signals and the gearbox and bearing dynamic nature still needs further investigation, in order for thoroughly understanding the vibration signal characteristics and thereby effectively diagnosing fault.

Gearbox and rolling element bearing vibration signals usually feature amplitude modulation and frequency modulation (AM-FM), and the modulation characteristics contain their health status information [17–21]. Cyclic correlation and cyclic spectrum are effective in extracting modulation features from amplitude modulation (AM), frequency modulation (FM), and AM-FM signals. Feng and his collaborators [22–24] derived the expressions of cyclic correlation and cyclic spectrum for gear AM-FM vibration signals and proposed indicators based on cyclic correlation and cyclic spectrum for detection and assessment of gearbox fault. Nevertheless, the carrier frequency of rolling element bearing vibration signals (resonance frequency) is completely different from that of gear vibration signals (gear meshing frequency and its harmonics). Therefore, it is important to investigate the cyclic correlation and cyclic spectrum of bearing vibration signals in depth, considering both the AM and the FM effects due to bearing fault. Meanwhile, how to explain the cyclostationary features displayed by the cyclic correlation and cyclic spectrum and to map the modulation characteristics to gear and bearing fault are still important issues for application of cyclostationary analysis in gearbox and bearing fault diagnosis. In this paper, we derive the explicit expressions of cyclic correlation and cyclic spectrum for general AM-FM signals, summarize their properties, and further extend the theoretical derivations to modulation analysis of both gear and rolling element bearing vibration signals, thus enabling cyclostationary analysis to detect and locate both gearbox and bearing fault.

2. Cyclic Correlation

2.1. Definition

The statistics of cyclostationary signals have periodicity or multiperiodicity with respect to time evolution. Cyclic statistics are suitable to process such signals. Among those, second order cyclic statistics, that is, cyclic correlation and cyclic spectrum, are effective in extracting the modulation features of cyclostationary signals.

For a signal , the cyclic autocorrelation function is defined as [25]

where is time lag and is cyclic frequency.

2.2. Cyclic Correlation of AM-FM Signal

During the constant speed running of gearboxes and rolling element bearings, the existence of fault, machining defect, and assembling error often leads to periodical changes in vibration signals. For gearboxes, such periodical changes modulate both the amplitude envelope and instantaneous frequency of gear meshing vibration. For bearings, such repeated changes excite resonance periodically. The excited resonance vanishes rapidly due to damping before next resonance comes, resulting in AM feature. Meanwhile, in one repeating cycle, the resonance exists in early period and the instantaneous frequency equals approximately the resonance frequency, while in later period, the resonance vanishes due to damping and the instantaneous frequency becomes 0. That means the instantaneous frequency changes periodically, resulting in frequency modulation (FM). Hence the vibration signals of both gearboxes and rolling element bearings can be modeled as an AM-FM process [17, 21] plus a random noise

where

are the AM and FM functions, respectively, and are the magnitude of AM and FM respectively, is the carrier frequency (for gearboxes, it is the gear meshing frequency or its th harmonics; for rolling element bearings, it is the resonance frequency of bearing system), is the modulating frequency equal to the gear or bearing fault characteristic frequency, , , and are the initial phase of AM and FM, respectively, and is a white Gaussian noise due to random background interferences.

Without loss of generality, consider only the fundamental frequency of the AM and FM terms; then (2) becomes

According to the identity [26]

where is Bessel function of the first kind with integer order and argument , the FM term in (5) can be expanded as a Bessel series, and then (5) becomes

For such a signal expressed as (7), the time-varying feature of its autocorrelation function is mainly determined by the AM-FM part, since the autocorrelation function of a white Gaussian noise (i.e., its Fourier transform has peak at 0 only, and therefore the noise does not affect identification of modulating frequency via cyclic correlation and cyclic spectrum analysis). In addition, it is the AM and FM effects on the carrier signal that leads to the cyclostationarity of bearing and gearbox vibration signals, and we rely on detection of the modulating frequency of such AM and FM effects to diagnose bearing and gearbox fault. Therefore, we neglect the noise and focus on the deterministic AM-FM part only in the following analysis. Then the cyclic autocorrelation function of (7) can be derived as [22]

in lower cyclic frequency domain, and

in higher cyclic frequency domain, where the intermediate functions

Set the time lag to 0, yielding the slice of cyclic autocorrelation function

in lower and higher cyclic frequency domains, respectively, where the intermediate functions

According to (10a) and (10b) and (11a) and (11b), the slice of cyclic autocorrelation function has two clusters of cyclic frequencies: one cluster concentrates around the cyclic frequency of 0 Hz separated by the modulating frequency , and the other cluster spreads around twice the carrier frequency with a spacing equal to the modulating frequency .

In lower cyclic frequency domain, the cyclic frequency locations of present peaks are dependent on the difference of the two Bessel function orders . For any peak at a specific cyclic frequency, . This leads to constant complex exponentials in (11a). Furthermore, according to the addition theorem of Bessel functions [26]

peaks appear in the slice of cyclic autocorrelation function in lower cyclic frequency domain, if and only if the orders of the two Bessel functions are equal to each other; that is, . Therefore, the cyclic autocorrelation slice in lower cyclic frequency domain can be further simplified as

According to (13), in lower cyclic frequency domain of the cyclic autocorrelation slice, peaks appear at the cyclic frequencies of 0 Hz, the modulating frequency , and its twice . If higher order harmonics of the modulating frequency are taken into account, then peaks also appear at the modulating frequency harmonics .

The addition theorem of Bessel functions does not apply to the slice of cyclic autocorrelation function in higher cyclic frequency domain. The cyclic frequency locations of present peaks are dependent on the sum of the two Bessel function orders . For any specific peak, . This does not mean . According to (10b) and (11b), in higher cyclic frequency domain of the cyclic autocorrelation slice, sidebands appear at both sides of twice the carrier frequency , with a spacing equal to the modulating frequency .

According to the above derivations, we can detect gearbox and bearing fault by monitoring the presence or magnitude change of sidebands around the cyclic frequency of 0 or twice the carrier frequency, that is, twice the meshing frequency for gearboxes and twice the resonance frequency for bearings, in the 0 lag slice of cyclic autocorrelation function. We can further locate the gearbox and bearing fault by matching the sideband spacing with the fault characteristic frequencies.

3. Cyclic Spectrum

3.1. Definition

For a signal , the cyclic spectral density is defined as the Fourier transform of the cyclic correlation function [25]

where is frequency.

3.2. Cyclic Spectrum of AM-FM Signal

Without loss of generality, we still consider the simplified gearbox and bearing vibration signal model, (5), by focusing on the fundamental frequency of the AM and FM terms. Its cyclic spectral density can be derived as [23, 24]

in lower and higher cyclic frequency domains, respectively, where the intermediate function

According to (15a) and (15b), peaks appear at specific locations only on the cyclic frequency−frequency plane. Their cyclic frequency locations in lower cyclic frequency domain, as well as their frequency locations in higher cyclic frequency domain, are dependent on the difference of the two Bessel function orders . For any specific peaks, . Then, the addition theorem of Bessel functions [26], (12), applies to the cyclic spectral density, (15a) and (15b). Hence, on the cyclic frequency−frequency plane of the cyclic spectral density, peaks appear if and only if the orders of the two Bessel functions are equal to each other; that is, . Then cyclic spectral density can be simplified as

in lower cyclic frequency domain and

in higher cyclic frequency domain.

According to (17a) and (17b), for any peak on the cyclic frequency−frequency plane, its frequency location in lower cyclic frequency domain, as well as its cyclic frequency location in higher cyclic frequency domain, is dependent on the Bessel function order . Meanwhile, the peak magnitude only involves a few Bessel functions. Thus (17a) and (17b) can be further simplified as

in lower and higher cyclic frequency domains, respectively.

According to (18a), in lower cyclic frequency domain, peaks appear at the cyclic frequencies of 0 Hz, modulating frequency , and its twice . If higher order harmonics of modulating frequency are taken into account, then peaks also appear at the cyclic frequencies of the modulating frequency harmonics . Along the frequency axis, these peaks center around the carrier frequency , with a spacing equal to the modulating frequency .

According to (18b), in higher cyclic frequency domain, peaks appear at the frequencies of 0 Hz, modulating frequency , and its half . If higher order harmonics of modulating frequency are taken into account, then peaks also appear at the modulating frequency harmonics and their half . Along the cyclic frequency axis, these peaks center around twice the carrier frequency , with a spacing equal to twice the modulating frequency .

Observing the peak locations in (18a) and (18b), the peaks in cyclic spectrum distribute along the lines

These lines form diamonds on the cyclic frequency−frequency plane, as illustrated by Figure 1, which is the cyclic spectrum of an AM-FM signal with a carrier frequency of 256 Hz and a modulating frequency of 16 Hz.

Figure 1: Cyclic spectrum distribution characteristics of an AM-FM signal.

According to the above derivations, we can detect gearbox and bearing fault by monitoring the presence or magnitude change of peaks in the cyclic spectrum. For example, in lower cyclic frequency band, focus on the points corresponding to the cyclic frequency locations of modulating frequency and its multiples and to the frequency locations of the carrier frequency plus the modulating frequency multiples . We can further locate the gearbox and bearing fault by matching the cyclic frequency spacing of peaks with the fault characteristic frequencies.

4. Gearbox Signal Analysis

4.1. Specification of Experiment

Figure 2 shows the experimental system. The gearbox has one gear pair. Table 1 lists the configuration and running condition of the gearbox. Two statuses of the gearbox are simulated. Under the healthy status, the gear pair is perfect. While under the faulty status, one of the pinion teeth is spalled, whereas the gear is perfect. During the experiment, accelerometer signals are collected at a sampling frequency of 20000 Hz and each record lasts for 3 s (i.e., 60000 samples) which covers more than 51 and 48 revolutions for the drive pinion and the driven gear, respectively, and is long enough to reveal the cyclostationarity.

Table 1: Gearbox configuration and running condition.

Drive pinion
Driven gear

Number of teeth
20
21

Rotating frequency (Hz)
17.285
16.462

Meshing frequency (Hz)
345.7

Brake torque (Nm)
—
200

Figure 2: Gearbox experimental setup.

4.2. Signal Analysis

Figure 3 shows the waveform, Fourier spectrum, cyclic correlation 0 lag slice, and cyclic spectrum (in lower cyclic frequency band) of the healthy gearbox. In the following analysis, the peak frequencies do not correspond exactly to those in Table 1. This is reasonable, because the actual speed is inevitably different from the set one in real experiments. In the cyclic correlation slice, Figure 3(c), most of the present peaks correspond to the driven gear rotating frequency harmonics. Although a few peaks appear at the pinion and gear characteristic frequencies and their harmonics, their magnitudes are not strong. In the cyclic spectrum (the colorbar on the right shows the magnitude, the same setting in the following cyclic spectra), Figure 3(d), along the frequency axis, the present peaks center around the gear meshing frequency 345.7 Hz, and its harmonics, and along the cyclic axis, they appear at the pinion and gear characteristic frequencies and their harmonics. The presence of these peaks is reasonable; since gear manufacturing errors and minor defects are inevitable, they will result in these peaks.

(a) Waveform

(b) Fourier spectrum

(c) Cyclic correlation 0 lag slice

(d) Cyclic spectrum

(e) Zoomed-in cyclic spectrum

Figure 3: Healthy gearbox signal.

Figure 4 shows the waveform, Fourier spectrum, cyclic correlation 0 lag slice, and cyclic spectrum (in lower cyclic frequency band) of the faulty gearbox. In the cyclic correlation slice, Figure 4(c), peaks appear at the pinion and gear characteristic frequencies and their harmonics. Except the first two peaks, nearly all the other peaks appear at the cyclic frequency locations of the drive pinion rotating frequency harmonics, and they are higher than those in that of the healthy gearbox. In the cyclic spectrum, Figure 4(d), more and stronger peaks appear than in that of the healthy gearbox. Figure 4(e) shows the zoomed-in cyclic spectrum, for revealing the peak distribution details. Along the cyclic frequency axis, peaks appear along lines corresponding to the pinion characteristic frequency and its multiples. While along the frequency axis, sidebands appear around 1400 Hz about four times the gear meshing frequency, with a spacing equal to the pinion characteristic frequency. Based on the theoretical derivations in Sections 2 and 3, the cyclic frequency locations of peaks in cyclic correlation slice and cyclic spectrum, as well as the sideband spacing along frequency axis in cyclic spectrum, relate to the modulating frequency of AM-FM signals. These features imply that more harmonics of the drive pinion rotating frequency get involved in modulating the gear meshing vibration and that the drive pinion has a stronger modulation effect than the driven gear, indicating the pinion fault. These findings are consistent with the actual condition of the faulty gearbox.

(a) Waveform

(b) Fourier spectrum

(c) Cyclic correlation 0 lag slice

(d) Cyclic spectrum

(e) Zoomed-in cyclic spectrum

Figure 4: Faulty gearbox signal.

5. Bearing Signal Analysis

5.1. Specification of Experiment

Figure 5 shows the experimental setup of the test [27]. A shaft is supported by four Rexnord ZA-2115 double row rolling element bearings and is driven by an AC motor through rub belts at a speed of 2000 rpm. A radial load of 6000 lbs is applied to the shaft and bearings by a spring mechanism. The bearing test was kept running for eight days until damage occurs to the outer race of bearing 1. In the normal case, all the four bearings are healthy. While in the faulty case, the outer race of bearing 1 has damage, as shown in Figure 6. Accelerometers are mounted on the bearing housings, and the vibration signals are collected at a sampling frequency of 20480 Hz, and 20480 data points are recorded for both the healthy and faulty cases. The main parameters of the four bearings are listed in Table 2. The characteristic frequency of each element fault is calculated and listed in Table 3.

Table 2: Parameters of bearing Rexnord ZA-2115.

Number of rollers
Roller diameter
Pitch diameter
Contact angle

16
0.331 [in]
2.815 [in]
15.17 [°]

Table 3: Characteristic frequency of bearing Rexnord ZA-2115 [Hz].

Outer race
Inner race
Roller

236.404
296.930
139.917
279.833

Figure 5: Bearing experimental setup [27].

Figure 6: Outer race damage of bearing 1 [27].

5.2. Signal Analysis

Figure 7 shows the waveform, Fourier spectrum, cyclic correlation 0 lag slice, and cyclic spectrum (in lower cyclic frequency band) of the normal case. In the cyclic correlation slice, Figure 7(c), a few small peaks appear, but they do not correspond to any bearing component fault characteristic frequency or its multiples. Although some peaks appear in the cyclic spectrum, Figure 7(d), they do not distribute along lines corresponding to the cyclic frequencies of any bearing component fault characteristic frequency or its multiples. These features imply that no significant modulation on the resonance vibration and the bearing is healthy.

(a) Waveform

(b) Fourier spectrum

(c) Cyclic correlation 0 lag slice

(d) Cyclic spectrum

Figure 7: Normal bearing signal.

Figure 8 shows the waveform, Fourier spectrum, cyclic correlation 0 lag slice, and cyclic spectrum (in lower cyclic frequency band) of the faulty case. In the close-up view of the Fourier spectrum, some sidebands appear, but the frequency spacing is not identically equal to the outer race fault characteristic frequency. In the cyclic correlation slice, Figure 8(d), more peaks appear and their magnitudes are higher than in the normal case. Moreover, their cyclic frequency locations correspond to the outer race fault characteristic frequency and multiples up to the 25th order. In the cyclic spectrum, Figure 8(e), many peaks are present. More importantly, they distribute along lines associated with the outer race fault characteristic frequency and multiples. At any cyclic frequency of the outer race fault characteristic frequency or its multiple, these peaks form sidebands along the frequency axis, with a spacing equal to the outer race fault characteristic frequency. For example, in the zoomed-in cyclic spectrum, Figure 8(f), the four peaks labeled by capitals A, B, C, and D distribute along a line at the cyclic frequency of 710 Hz (about three times the outer race fault characteristic frequency), and they have a spacing of 236 Hz (approximately equal to the outer race fault characteristic frequency) along the frequency axis. These findings imply that the outer race characteristics frequency has strong modulation effect on the resonance, indicating fault existence on the bearing outer race, in accordance with the actual settings.

(a) Waveform

(b) Fourier spectrum

(c) Zoomed-in Fourier spectrum

(d) Cyclic correlation 0 lag slice

(e) Cyclic spectrum

(f) Zoomed-in cyclic spectrum

Figure 8: Faulty bearing signal.

6. Discussion and Conclusions

Since gearbox and rolling element bearing vibration signals are characterized by AM-FM feature, their Fourier spectra have complex sideband structure due to the convolution between the Fourier spectra of AM and FM parts as well as the infinite Bessel series expansion of an FM term. Although gearbox and bearing fault can be identified via conventional Fourier spectrum, it involves complex sideband analysis and relies on the sideband spacing to extract the fault characteristic frequency.

Considering the cyclostationarity of gearbox and bearing vibration signals due to modulation and the suitability of cyclostationary analysis to extract modulation features of such signals, the explicit expressions of cyclic correlation and cyclic spectrum of general AM-FM signals are derived and validated via gearbox and bearing lab experimental signal analysis. According to the theoretical derivations, the cyclic frequency locations of peaks in cyclic correlation and cyclic spectrum directly correspond to the modulating frequency (i.e., the gear or bearing fault characteristic frequency) and harmonics. Therefore, cyclostationary analysis offers an effective approach to gearbox and bearing fault feature extraction.

Conflict of Interests

The authors declare that there is no conflict of interests regarding the publication of this paper.

Acknowledgments

This work is supported by National Natural Science Foundation of China (11272047, 51475038), Program for New Century Excellent Talents in University (NCET-12-0775), and CETIM (Centre des Etudes Techniques des Industries Mécaniques de Senlis), France. The authors would like to thank the reviewers for their valuable comments and suggestions.

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