Shock and Vibration
Volume 2021 (2021), Article ID 5536853, 12 pages
https://doi.org/10.1155/2021/5536853

Research Article

Study on the Unbalanced Fault Dynamic Characteristics of Eccentric Motorized Spindle considering the Effect of Magnetic Pull

Zhan Wang, Wenzhi He, Siyuan Du, and Zhe Yuan

School of Mechanical Engineering, Shenyang Jianzhu University, Shenyang, Liaoning 110168, China

Correspondence should be addressed to Zhe Yuan; yuanzhe@sjzu.edu.cn

Received 6 January 2021; Revised 21 February 2021; Accepted 11 March 2021; Published 26 April 2021

Academic Editor: Hui Ma

Copyright © 2021 Zhan Wang et al. 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.

Unbalanced fault is the most common fault of high-speed motorized spindle, which is the main factor affecting the machining accuracy of high-speed spindle. Due to the unbalanced magnetic pull produced by the air gap eccentricity of the stator and rotor, the unbalanced vibration of the motorized spindle will be further aggravated. In order to explore the dynamic behavior and motion law of the unbalanced fault motorized spindle under the eccentric state, a dynamic model of the unbalanced fault of the high-speed motorized spindle considering the unbalanced magnetic pull was established. Taking the eccentric motorized spindle customized by the research group as the research object, the dynamic model is established, simulated, and analyzed, and the response change law of motorized spindle under the effect of different speed, unbalance, and air gap is obtained. The simulation results show that the unbalanced magnetic pull caused by static eccentricity will increase the unbalanced vibration of motorized spindle, and the unbalanced vibration will also increase with the increase of static eccentricity. The vibration caused by unbalanced magnetic pull does not increase with the increase of rotating speed. In frequency-domain analysis, when there is unbalanced magnetic pull, the peak appears at 0 Hz, and the amplitude of fundamental frequency vibration will increase with the increase of eccentricity. The experimental results show that the greater the eccentricity is, the greater the unbalance vibration of the motorized spindle is. The experimental results are consistent with the simulation results, which further verify the accuracy of the model. The research results lay a theoretical basis for fault analysis and diagnosis of coupling fault motorized spindle.

1. Introduction

In recent years, with the development of high-end manufacturing and processing in the direction of high speed and high precision, higher processing requirements have been put forward for high-end CNC machine tool. As the core component of CNC machine tools, the operation accuracy and performance of the motorized spindle unit are the key to high-speed and high-precision machining. During the operation of the motorized spindle, it will be subject to the coupling effect of the structure and the electromagnetic field. Due to installation errors and machining accuracy, the geometric center of the stator and rotor will have position eccentricity. Thus, the air gap distribution inside the motorized spindle is not uniform, which will lead to the result that unbalanced magnetic pull is generated; and unbalanced mass of the rotating spindle itself will also cause unbalanced vibration of the motorized spindle during operation. These will affect the machining accuracy of the motorized spindle and more seriously may cause equipment failure. To solve the unbalanced fault caused by the eccentricity of the motorized spindle and the position eccentricity of the stator and rotor is the key issue to improve the machining quality of the machine tool. So it is vital to deeply study the dynamic behavior of the unbalanced fault of the motorized spindle under eccentricity.

In recent years, the vibration and fault dynamics of rotors similar to motorized spindle have always been a research hotspot in the field of rotor vibration, and a large number of scholars have carried out in-depth research. Liu proposed an improved dynamic model for unbalanced high-speed motorized spindle considering the internal clearance and air magnetic field energy [1]. Shi studied the orbit-spinning behaviors of the outer ring in a full ceramic ball bearing-steel pedestal system in wide temperature ranges [2, 3]. Shan et al. established a high-speed motorized spindle bearing-rotor dynamics model and analyzed the relationship between high speed and the transfer function of the milling cutter tip point [4]. Phadatare and Pratiher conducted a nonlinear dynamic analysis of a lightweight flexible rotor-disk-bearing system with geometric eccentricity and mass unbalance [5]. Wang and Jiang used Runge-Kutta method to successfully numerically solve the control equation of the dual-rotor system with unbalanced and unaligned coupling faults [6]. Qiao and Zhu studied the unbalanced vibration of the grinding wheel and provided a theoretical basis for dynamic balance [7]. Bab et al. studied the influence of mass eccentricity and surrounding medium damping on the steady-state response of the system [8]. Yue et al. found that mass eccentricity can increase the rotor vibration and weaken the influence of unbalanced magnetic pull and make the vibration tend to be regular [9]. Kong et al. studied the effect of mass eccentricity on the unbalanced response of induction motors through modeling [10]. Gao et al. studied the effect of unbalanced magnetic pull and mass eccentricity on the vibration of the motorized spindle but did not consider the influence of the gyro torque [11]. Faiz et al. proposed an analysis method that combines the concept of double penetration and superposition, which can predict the air gap magnetic field distribution of a surface-mounted permanent magnet motor with an eccentric air gap [12]. Xu et al. studied the nonlinear response of the rotor when the rotor is eccentric [13]. Tang et al. studied the stator vibration characteristics of the turbo generator under normal operating conditions and the combined fault of air gap eccentricity and rotor turn-to-turn short circuit [14]. Zuo et al. analyzed the excitation source using the finite element method and the effect of the unbalanced magnetic pull on the longitudinal dynamics evaluation index influences [15]. Liu et al. studied the mechanical coupling and magnetic coupling of permanent magnet synchronous motors [16]. Boy and Hetzler studied the lateral stability behavior and static torque characteristics of magnetic eccentricity [17]. Liu established a Jefferson rotor model considering the static radial eccentricity and studied the effect of unbalanced magnetic pull on the eddy of permanent magnet synchronous motors [18, 19]. Kumar and Kalita studied the causes and control methods of unbalanced magnetic pull [20]. Chen et al. studied the magnetic model of the motor [21]. Xiang et al. studied the influence of UMP on the nonlinear dynamic characteristics of permanent magnet synchronous motor rotor system [22]. Tang et al. analyzed the influence of radial air gap eccentricity on the radial unbalanced magnetic pull and vibration characteristics of the turbine generator rotor when the number of pole pairs is 1 [23]. Werner explained how to consider electromagnetic field damping when analyzing the forced vibration caused by eccentricity [24]. In summary, the research on rotor failure dynamics and vibration has formed a good theoretical basis. However, there are few studies on coupling faults mainly based on unbalanced magnetic pull between stator and rotor of motorized spindle. Therefore, it is of great significance to study the causes of unbalanced magnetic pull and its influence on rotor vibration.

In the above studies, most of the researches on air gap eccentricity to rotor bearing system are focused on motor. However, due to the complexity of the structure of motorized spindle, in particular the influence of unbalanced magnetic pull caused by eccentricity between stator and rotor on vibration cannot be ignored. With the increase of speed of motorized spindle, the operation stability of motorized spindle will be more affected, thus affecting the processing quality. In this paper, the expression of unbalanced magnetic pull of motorized spindle is derived first, and then a fault dynamic model of unbalanced magnetic pull coupling with mass eccentricity considering gyroscopic moment is established based on Lagrange method. The customized motorized spindle is taken as the research object to carry out simulation analysis. The influence of mass eccentricity, air gap eccentricity, and speed on the vibration characteristics of the spindle is discussed in detail. The research results of this paper provide certain theoretical reference for fault diagnosis, early prediction, and further dynamic balance regulation of coupled faulty motorized spindle.

2. Dynamic Modeling

2.1. The Mechanism of Unbalanced Magnetic Pull

The matching structure diagram of the motorized spindle stator and rotor is shown in Figure 1. There is a millimeter-level air gap between the rotor and stator. The main reason for unbalanced magnetic pull is the asymmetry of magnetic field between the stator and rotor, which leads to the asymmetry of magnetic pull force of rotor in radial direction, and unbalanced force produces force biased to one side. The uneven distribution of the air gap is the main reason for the uneven distribution of the magnetic field. When the geometric centers of the stator and rotor do not coincide, the uneven air gap around the rotor will occur; and because it is impossible to make the stator and rotor geometric center overlap even after rigorous testing and calibration, the unbalanced magnetic pull is inevitable.

Figure 1: Motorized spindle diagram.

2.2. Magnetic Pull Model of the Motorized Spindle

A brief diagram of static eccentricity of rotor section of motorized spindle is shown in Figure 2. The large circle represents the internal measurement of the stator, and the small circle represents the outside of the rotor. The air gap of the eccentric rotor can be approximately expressed as

where denotes the average air gap width of the motorized spindle, and denote the angle of any position and the static eccentric distance of the rotor, respectively, and denotes the static eccentric angle of the rotor.

Figure 2: Rotor static eccentricity diagram.

The expression to expand the air gap into a series is

where indicates relative eccentricity and indicates the air permeability coefficient.

Fourier Coefficient is as follows:

The air gap fundamental magnetomotive force can be calculated by

where denotes the number of pole pairs of the motor, denotes the fundamental magnetomotive force of the rotor exciting current, and denotes the electrical frequency.

The expression of the air gap distribution is

Ignoring the smaller magnetic close component, the Maxwell stress of the normal component is

The expression of the unbalanced magnetic pull can be derived by integrating the above formula on the rotor surface.

where represents the rotor radius, represents the axis length, represents the static eccentricity angle, and represent the magnetic pull in direction and in direction, respectively, , , , and represent the magnetic pull, respectively, and represents the unbalanced tension series.

2.3. Dynamic Model

Due to manufacturing and material reasons, even if the motorized spindle rotor is dynamically balanced, there will still be unbalanced mass. These unbalanced masses will cause unbalanced vibration when rotating at high speeds, so the impact of unbalanced masses cannot be ignored. The expression of the centrifugal force produced by the unbalanced mass is

where denotes the unbalanced mass and denotes the speed of the rotor.

Since the length of spindle is short and the stiffness is high, the influence of bearing stiffness on the operation of the motorized spindle can be ignored, and the four-degree-of-freedom rotor model shown in Figure 3 is used, where (, , , ) are the degrees of freedom, and are the lateral displacement and longitudinal displacement of the geometric center of the rotor, respectively, and (, ) are the corner of the disc. A rotor with a disc not in the middle of the spindle will generate gyroscopic torque when the rotor rotates. Therefore, the influence of gyro torque cannot be ignored. The angle between the axis of the disc and the connecting line AB at both ends of the rotor is , the rotational angular velocity of the rotor is , the rotor moment of inertia is , and the polar moment of inertia is . The momentum moment of the rotor is

Figure 3: Schematic diagram of a 4-DOF rotor.

Suppose that the plane formed by the axis of the disc and the connection AB has an angular velocity . Because the momentum moment of the precession disc will constantly change direction, there is a moment of inertia

The direction is perpendicular to , and the size is

This moment is called the gyro moment or turning moment. It is the moment of the disc acting on the spindle. Because is smaller, . The above formula can be written as

The dynamic differential equations of the motorized spindle rotor are derived based on Lagrange method. Lagrange’s equation is

Let the coordinates of the center of gravity be

where denotes the coordinate of the geometric center of the rotor.

The kinetic energy of the rotor can be calculated by

Let the generalized coordinates be , , and , and the generalized force can be calculated by

The dynamic differential equation of the rotor is obtained by substituting equations (14)–(16) in equation (13):

In the equation, denotes the mass of the disk, denotes the eccentricity distance of the mass, and denotes the force applied at point when the center of the disk has a unit displacement in the x direction. denotes the force applied at a point along direction when unit rotation angle is available on axis . refers to the force applied at a point along direction when there is a unit rotation angle around the axis . is the damping of point when it has a displacement in the direction, and is the damping of point when it has a turn around the -axis.

3. Analysis of Unbalanced Vibration Characteristics of the Eccentric Motorized Spindle

The dynamic model of eccentric mass and unbalanced magnetic pull coupling fault motorized spindle is established by Lagrange method and solved numerically by the fourth-order Runge-Kutta method based on MATLAB. In the established model system, the effects of relative eccentricity on unbalanced magnetic pull, mass eccentricity and static eccentricity on axis track, and unbalanced vibration are analyzed, respectively. Vibration response law is obtained by processing parameters such as rotating speed , mass eccentricity , and static eccentricity . Vibration characteristics of motorized spindle under mass eccentricity and air gap eccentricity are further understood through analysis results. The customized HT-170-20000-11 eccentric motorized spindle is used as the research object. Table 1 gives some parameters of the motorized spindle. For comparison, the static eccentric angle of the rotor is set to .

Table 1: Structural parameters of motorized spindle.

Parameter
Size

Spindle length

Material elastic modulus

Material density

Rotor disc thickness

Rotor radius

Air gap width

Number of motor pole pairs

3.1. Effect of Relative Eccentricity on Unbalanced Magnetic Pull

The relationship between relative eccentricity and air gap permeability coefficient is given in Figure 4. From the figure, it can be seen that the relative eccentricity and the air gap permeability coefficient are nonlinear. As the relative eccentricity increases, the air gap permeability coefficient also increases; and the increase rate is becoming faster and faster when the relative eccentricity is getting closer and closer to 1, because the air gap on one side of the rotor is close to infinity, which causes the magnetic pull on one side to rise sharply.

Figure 4: The relation between relative eccentricity and air gap permeability coefficient.

From Figure 5, it can be concluded that when the relative eccentricity is less than 0.7, the unbalanced magnetic pull and the relative eccentricity are roughly linear, but when the relative eccentricity is close to 1, the unbalanced magnetic pull rises sharply and appears infinite, which is related to the increase of air gap permeability coefficient. The air gap permeability coefficient increases sharply when the relative eccentricity is close to 1, which increases the unbalanced magnetic pull to infinity. It will cause serious vibration of the motorized spindle and affect the stable operation of the motorized spindle.

Figure 5: The relationship between relative eccentricity and magnetic force of gas unbalance.

3.2. Vibration Analysis in Time and Frequency Domains

Figures 6 and 7 are the frequency-domain and time-domain waveform diagrams of the motorized spindle at 6000 r/min and 12000 r/min, and the mass eccentricity is 5 μm. The static eccentricity is 0 μm, 30 μm, and 100 μm. When the static eccentricity in the frequency-domain diagram is 0 μm, the frequency-domain diagram has a peak at 100 Hz, and when the static eccentricity is added, a peak appears at about 0 Hz. This part of the peak value is caused by unbalanced magnetic pull, which is a manifestation of the effect of unbalanced magnetic pull on the vibration of motorized spindle. When the speed increases by 12000 r/min, the main peak position moves to about 200 Hz, and the peak value increases. To compare the two time-domain diagrams, it can be concluded that, with the appearance of static eccentricity, the initial phase of unbalanced vibration increases, and the amplitude of unbalanced vibration decreases in the positive direction and increases in the negative direction. This is consistent with the analysis results of the axis trajectory. With the increase of rotating speed, the time-domain diagrams coincide, and the effect of unbalanced magnetic pull weakens. Mass eccentricity becomes the main interfering factor.

(a)

(b)

Figure 6: Time-domain and frequency-domain waveforms with mass eccentricity of 5 µm at 6000 r/min and different air gap eccentricity. (a) Time domain. (b) Frequency domain.

(a)

(b)

Figure 7: Time-domain and frequency-domain waveforms with the rotating speed of 12000 r/min, mass eccentricity of 5 µm, and different air gap eccentricity. (a) Time domain. (b) Frequency domain.

3.3. Axis Track Analysis

Figure 8 shows the simulation axis track under the condition of rotating speed of 5000 r/min, mass eccentricity of 0.0001 m, and static eccentricity of 0.0001 m. Vibration occurred within a certain range, and the unbalanced magnetic pull changed the motion state of the motorized spindle rotor. By comparing Figure 8(b) with static eccentricity occurring at 45° and Figure 8(c) with static eccentricity occurring at 225°, it can be seen that when static eccentricity occurs at 45°, the axis trajectory shifts to the lower left. But when the eccentricity occurs at the position of 225°, the axis track shifts to the upper right, which shows that the unbalanced magnetic pull pushes the rotor to the side with larger air gap.

(a)

(b)

(c)

Figure 8: Orbit of spindle center. (a) No static eccentricity. (b) Static eccentricity at 45°. (c) Static eccentricity at 225°.

3.4. Vibration Analysis without Static Eccentricity

The rotor static eccentric distance r is set to zero. The amplitude along the X direction of the rotor is analyzed when the rotating speed increases under three unbalanced conditions: mass eccentricity is 5 micron, 10 micron, and 15 micron, respectively. It can be concluded from Figure 9 that when the mass eccentricity is constant, the amplitude of the motorized spindle rotor increases with the increase of the speed, and the higher the speed is, the greater the amplitude of the unbalanced amplitude is. At the same speed, as the mass eccentricity increases, amplitude also increases, and the higher the speed is, the greater the amplitude of unbalanced vibration is. This is because the unbalanced force produced by the unbalanced mass has a square relationship with the speed, and the slope will gradually increase.

Figure 9: Effect of mass eccentricity on amplitude without static eccentricity.

When the rotor static eccentric distance is zero and the rotating speed is 10000 r/min and 20000 r/min, the variation of the amplitude of unbalanced vibration of motorized spindle with the increase of mass eccentricity is obtained. Figure 10 shows that the amplitude of the unbalanced vibration increases linearly with the increase of the mass eccentricity at the same speed, and, under the same mass eccentricity, the amplitude increases with the increase of the speed, and the higher the speed is, the greater the amplitude of unbalanced vibration is. This is also consistent with the model: the mass eccentricity and the unbalanced force produced by the eccentric mass have a linear relationship.

Figure 10: Effect of mass eccentricity on vibration without static eccentricity.

3.5. Effect of Static Eccentricity on Unbalanced Vibration

Effect of different mass eccentricity and static eccentricity on unbalanced vibration of motorized spindle is analyzed. Figure 11 shows that the vibration of the motorized spindle increases with the increase of the speed under the same static and mass eccentricity, and the increase of unbalanced vibration shows an upward trend, and the higher the rotating speed is, the greater the amplitude increase is. With the increase of unbalanced magnetic pull and static eccentricity, the vibration also increases. The three figures show that the unbalanced vibration increases as the mass eccentricity increases.

(a)

(b)

(c)

Figure 11: Effect of different static eccentricity on vibration with mass eccentricity of (a) 10 µm, (b) 20 µm, and (c) 30 µm.

The change of unbalanced vibration with the increase of rotor static eccentricity under different mass eccentricity at speeds of 5000 r/min and 30000 r/min is analyzed. The vibration increases as the static eccentricity of the motorized spindle increases linearly, as shown in Figure 12. Under the same speed and static eccentricity, the amplitude of unbalanced vibration increases with the mass eccentricity.

(a)

(b)

Figure 12: Effect of static eccentricity on vibration under different mass eccentricity at (a) 5000 r/min and (b) 30000 r/min.

The increase of unbalanced vibration with mass eccentricity under the same static eccentricity is analyzed when the rotating speed is 5000 r/min and 10000 r/min. At the same speed and static eccentricity of the rotor, as the mass eccentricity increases, the unbalanced vibration increases and rises linearly, as shown in Figure 13. Under the same mass eccentricity and speed, the unbalanced vibration amplitude increases with static eccentricity.

(a)

(b)

Figure 13: Effect of mass eccentricity on vibration at the rotating speed of (a) 5000 r/min and (b) 30000 r/min.

The effect of unbalanced tension on the vibration of the motorized spindle rotor is calculated when there is no mass eccentricity in the motorized spindle. In Figure 14, is the static eccentricity of the rotor spindle, and the unbalanced magnetic pull is proportional to the static eccentricity. Figure 14 shows that the influence of unbalanced magnetic pull on unbalanced vibration has nothing to do with the speed and only depends on the size of the static eccentricity of the rotor spindle, which increases with the increase of the static eccentricity.

Figure 14: Effect of different static eccentricity on vibration with the increase of rotating speed.

4. Experimental Verification

The experiment uses the motorized spindle test platform shown in Figure 15 for experimental verification. The motorized spindle is two customized HT-170-20000-11 eccentric motorized spindles with air gap eccentricity of 0.1 mm and 0.15 mm. In the experiment, a laser vibrometer of Germany’s Polytec GmbH company model OFV-50555000 Xtra is used to measure the unbalanced vibration of the motorized spindle during operation. Because of the limitation of actual experimental conditions, the experiment mainly reflects the vibration of the rotor by monitoring the exposed rotating spindle at the end of the motorized spindle. The data display instrument is used to export the experimental data.

Figure 15: Motorized spindle test platform.

The experiment uses 0.1 mm and 0.15 mm static eccentric HT-170-20000-11 motorized spindles and carries out the vibration experiment of the motorized spindle with increasing speed. Through the experiment, it can be concluded that the vibration caused by the static eccentricity of the motorized spindle fluctuates in a certain small range with the increase of the speed, but it can be regarded as basically unchanged because of the more external influence. As the static eccentricity increases, the unbalanced vibration will increase. This matches the simulation result. Figure 16 shows the comparison between simulation and experiment under different static eccentricity. Through comparison, the experiment and simulation are roughly consistent within a small range, and the model has a high accuracy.

Figure 16: Comparison between simulation and experiment.

Figure 17 shows the time-domain waveform diagrams and frequency-domain diagrams of the motorized spindle at 12000 r/min obtained from the experiment. When the static eccentricity increases, the amplitude of the unbalanced vibration also increases with it. In the frequency-domain diagram, since the motorized spindle has a slight mass eccentricity, a peak appears in the fundamental frequency. When the static eccentricity increases, the amplitude of the unbalanced vibration also increases. Because of the static eccentricity, peak value appears at 0 Hz, which is consistent with the simulation results.

(a)

(b)

Figure 17: Time-domain and frequency-domain waveforms with the rotating speed of 12000 r/min. (a) Time domain. (b) Frequency domain.

5. Conclusions

The mechanism of unbalanced magnetic pull force is analyzed, and the influence of gyroscopic moment is considered. A dynamic model of eccentric mass and unbalanced magnetic pull coupling fault motorized spindle is established by Lagrange method. Through the simulation analysis of the model and the comparison with the experiment, the influence of unbalanced magnetic pull on unbalanced vibration of the spindle does not increase with the speed of the spindle but is only related to the eccentric distance. The larger the eccentric distance is, the greater the vibration will be. When the relative eccentricity approaches 1, an infinite unbalanced magnetic pull will occur, and the unbalanced vibration of the rotor will deviate to the direction of large air gap. When there is mass eccentricity, the amplitude of unbalanced vibration increases with the increase of speed. When the speed is constant, the amplitude increases linearly with the increase of mass eccentricity. Through the above analysis, the coupling dynamic behavior of eccentric faulted motorized spindle under the influence of unbalanced magnetic pull is revealed.

Data Availability

The data used to support the findings of this study are included within the article.

Conflicts of Interest

The authors declare that they have no conflicts of interest.

Acknowledgments

This work was supported by the National Natural Science Foundation of China (Grant no. 51805337), the Key Laboratory of Vibration and Control of Aero-Propulsion System, Ministry of Education, Northeastern University (Grant no. VCAME202008), and the Scientific Research Project of Liaoning Provincial Education Department (Grant no. lnjc202010).

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