Experimental Dynamic Analysis of a Breathing Cracked Rotor

The recently emerged conception “Industry 4.0” is one of the most popular manufacturing topics among the industry and academia in the world which was first announced at the 2013 Hannover Fair [1]. Similar strategies have also been proposed by other main industrial countries, such as “Industrial Internet” by US and “Made in China 2025” by China [2]. Focusing on cyber-physical systems (CPS), Industry 4.0 is regarded as the next-generation production framework for the fourth industrial revolution [3] and promises to create the smart factory [4]. As one of the main components of Industry 4.0, the smart factory will involve a new integrative system, where not only all manufacturing resources (sensors, actuators, machines, robots, etc.) are connected and exchange information automatically, but also the factory will become conscious and intelligent enough to predict and maintain the machines; and intelligent enough to predict and maintain the machines [5, 6]. Many new technologies and methodologies have been developed in the related fields to promote the revolution, such as the crowsdsourcing based new production development in manufacturing SMEs [7], Quality assurance system [8], standardization towards Industry 4.0 [9], wireless device connection [10]. Because of high connection, the health condition of a single machine has greater influence on the factory operation than ever before. Online fault diagnostics and prognostics provide critical health information for the self-aware building and decision making which will play an important role in the Industry 4.0 factory [11].

Rotating machines are extensively used in industry, such as the compressors, rotors in manufacturing machines, steam and gas turbines, generators, and pumps [12‐14]. Fatigue cracking of rotor shafts is an important phenomenon that can lead to severe damage and great economic loss if not detected in time, especially for the highly connected and automatic production system in the Industry 4.0 factory. The CPS provides great opportunity to perform online crack detection based on the broad implement of sensors, data acquisition systems, computer networks and cloud computing systems together with the rotor dynamic theory so that the sudden breakdown of production lines due to the cracked shafts can be avoided.

It has been shown in the literature that the presence of a crack introduces additional flexibility to the shaft, which reduces its overall stiffness and generates complex orbits and super-harmonic frequency components [15, 16]. The dynamic analysis of cracked rotor systems has been intensively studied by many researchers [17‐23]. Sinou, et al. [17] evaluated the dynamic response of the rotor with a breathing crack by expanding the changing stiffness of the crack in a truncated Fourier series and using the Harmonic Balance Method. The orbits during transient operation at the critical speed and at half of the critical speed were considered to be the unique characteristics of the cracked rotor system. Babu, et al. [18] used the Hilbert-Huang transform to study the transient response of a cracked rotor passing through its critical speed. A frequency fluctuation was observed at the sub-critical speed. Al-Shudeifat [19] and Silani, et al. [20] used finite element models to establish the dynamic equations of the cracked rotor system. The whirl orbit and the shifts in the critical and subcritical speeds were studied. Shravankumar, et al. [21] utilized a full-spectrum method obtained by complex Fast Fourier transform to estimate the force and displacement coefficients for crack identification. The typical orbits and the frequency spectrum at the sub-critical speed were investigated. Lu, et al. [22] studied the nonlinear response characteristics of a breathing transverse crack rotor. The results indicate that the transverse crack causes super-harmonic resonance peaks at the second, third and fourth subcritical speeds. In an earlier paper by a subset of the authors [23], a new breathing function was proposed and the empirical mode decomposition was used to study the high-order frequency variation of a Jeffcott rotor with a transvers breathing crack. The typical whirl orbits during passage through the 1/3 and 1/2 subcritical speeds were observed. Based on aforementioned literature and other references therein, it can be concluded that analyzing unique characteristics of the dynamic response is a feasible and widely used method for crack detection.

However, although many papers have been published in this area, only a few employ actual results from laboratory experiments [24]. Darpe, et al. [25] verified theoretical findings through experiments with a fatigue crack rotor. The orbits and FFT spectra during the rotor passage through the 1/3 and 1/2 critical speeds consistently matched the theoretical findings. Later, Zhou, et al. [26] and Ren, et al. [27] adopted a similar method to further examine fatigue in cracked rotors. Compared with real fatigue cracks, the open crack is easier to implement in the experiment. Dong, et al. [28], Lin, et al. [29], and Mohammed, et al. [30] used a wire cutter machine to generate slits with different depths in the rotor which were generally viewed as open cracks.

In this research, the dynamic response of a breathing cracked rotor was studied experimentally. A real fatigue crack was induced using a three-point bending machine. The unique orbit evolution was compared with the theoretical findings given in Ref. [19], and the frequency spectra obtained by FFT method were analyzed as well. This work presents an effective crack detection method based on the dynamic response for the online diagnosis of rotor systems in the future smart factory.

In Ref. [23], a Jeffcott rotor model was established, and a breathing function was synthesized using Fourier series to approximate the actual breathing process. The breathing of the crack during the shaft rotation can be described as shown Figure 1. When open, the crack causes a reduction in bending stiffness of the shaft, while when fully closed (see Figure 1(f), the bending stiffness is equal to that of the uncracked rotor. Therefore, the breathing phenomenon leads to a time-varying stiffness matrix in the governing equations of the cracked rotor system. The governing equations of the cracked rotor system are given bywhere k ₁(t), k ₂(t) are the instantaneous stiffnesses respectively in the horizontal and vertical directions, and k ₁₂(t), k ₂₁(t) are the cross-coupling stiffnesses. The definitions of other parameters can be found in Ref. [23].

The governing equations are solved for relative crack depth of μ = 0.2, and the whirl orbits during passage through the 1/3 and 1/2 subcritical speeds are shown in Figure 2. It can be seen that near the 1/3 subcritical speed two inner loops appear (see Figure 2(a)) and get larger as the rotating speed approaches the 1/3 subcritical speed in Figure 2(b). Then, as the speed further increases, the inner loops become smaller and finally disappear, Figure 2(d). Similarly, near the 1/2 subcritical speed, one inner loop appears and evolves similarly, shown in Figures 2(e)–2(h). In addition, in the 1/3 subcritical speed zone, the loops appear and disappear at about π/π2.2 rad, while in the 1/2 subcritical speed zone, the loops appear at about π rad. These results are quite consistent with the results of Refs. [19, 25], which leads us to consider the orbits as a reasonable feature for crack identification.

An experiment is set up on a rotor test rig which consisted of a real fatigue shaft supported by a pair of identical ball bearings, a disk, two eddy current sensors and a DC motor as shown in Figure 3. The mass of the disk is 500 g. The diameter of the shaft is 10 mm, and the span between the two bearings is 400 mm.

A fatigue crack is generated on the shaft transversely by using a three-point-bending machine. Firstly, a slot is made by a wire-electrode cutting machine near the middle of the effective supported span as the initial fault. Then the shaft is placed in the three-point-bending machine and subjected to cyclic loading in a sinusoidal form at the nearby of the precut slot. After about 5000 cycles, the crack propagates to a depth of about 3.2 mm. The displacement of the center of the cracked section is measured by the eddy current sensors implemented in both the horizontal and vertical directions. A speed controller is used to adjust the rotation speed. The vibration signal is collected by a PXI data acquisition box produced by the National Instruments Company.

In order to verify the typical whirl orbits during passage through the subcritical speeds, a coast up and rundown process was performed. The first critical speed of the cracked rotor system was found at about 3300 r/min. The orbits around 1660 r/min, which is the 1/2 sub-critical speed zone, are plotted in Figure 4. It can be seen that the experimental results agree well with the theoretical analysis. The evolution process of the typical loop shown here is clearer and more complete than similar results shown in the prior Refs. [25‐27]. In Ref. [25], only two whirl orbits were shown which was incomplete to display the evaluation process. In Ref. [27] only the frequency spectra were studied while orbits were not examined. In Ref. [26], the whirl orbits at the subcritical speeds were not quite consistent with the theoretical results. The reason may lie in that in Ref. [26] the oil film force generated by the journal bearings affected the rotor orbits, but in this research the high precision ball bearings are used which can help to reduce the additional force.

The orientation change of the loop during passage through the 1/2 subcritical speed zone is about π rad which verifies the modelling and simulation findings in our previous research [23]. The corresponding frequency spectra are shown in Figure 5. They indicate that when the rotation speed approaches the 1/2 sub-critical speed zone, the 2X component dominates, as shown in Figures 5(b) and (c). As the speed increases past the center of the subcritical zone, the 2X component weakens, as expected.

Similarly, the whirl orbits during passage through the 1/3 subcritical speed zone are shown in Figure 6. The evolution of the inner loops and their orientation agrees well with simulation results. The frequency spectra in Figure 7 show that in this region, in addition to the basic frequency a high order (3X) component exists, indicated by the two inner loops in Figure 6, and we observe that the 2X component is relatively smaller in the 1/3 subcritical speed zone.

During the experiment, the unique orbits near the 1/4 and 1/5 subcritical speeds were also observed as shown in Figure 8 and Figure 10. To our knowledge, these subcritical speed zones have not been observed experimentally and reported in the literature. The whirl orbits including the three inner loops shown in Figure 8 agreed well with simulation results given in Ref. [19]. The frequency spectra of the horizontal response in the 1/4 subcritical speed zone are shown in Figure 9. It indicates that in this zone the 4X component exists and shows a similar variation pattern as the high-order frequency components in the 1/2 and 1/3 subcritical speed zones.

In Figure 10, four inner loops appear in the orbit when the rotating speed passes through the 1/5 subcritical speed zone. However, compared to Figure 4, Figure 6 and Figure 8, the size of the inner loop is smaller and the evolution process is not as obvious as in previous cases. The Fourier spectra shown in Figure 11 indicate that the high frequency 5X component does exists but is relatively weak which leads to the small inner loop.

From Figure 5, Figure 7, Figure 9 and Figure 11, it can be seen that near the subcritical speed, besides the basic frequency, the high frequency harmonic of the first critical speed is obvious which leads to the appearance of the typical orbits. When the rotating speed is in the lower subcritical speed zone, the corresponding high resonance frequency component is weaker. From Figures 4–11, we believe that the unique dynamic responses in the sub-critical speed zones have been systematically investigated and documented by the current set of experiments.

In future work, the experiment can be designed with multiple faults, such as the crack with bearing fatigue, oil-film force, or rub-impact fault to study the influence of other faults on the dynamics of cracked rotor systems and the crack detection method in multi-fault cases.