Research on Dynamic Balance of Spindle Rotor System Based on Particle Swarm Optimization

/e dynamic balance is a significant issue for the nonlinear dynamic characteristics of the spindle rotor system. However, there is a problem that the dynamic balance is lacking detailed study on optimization method. In the paper, a modal dynamic balance optimization model of spindle rotor system is proposed, which can intend to improve the accuracy of spindle rotor system modal dynamic balance. Because the multiorder unbalance components are the main spindle rotor system mode shapes, the particle swarm optimization (PSO) method is adopted. /e sum of squares of residual vibration after balancing is taken as the optimization objective, and the correction is presented as the optimization variable in the optimization model./e optimal correction weight of every unbalance component is calculated through a modal matrix equation of PSO. /e vibration amplitude that is greatly reduced after optimization balance is presented under different conditions. /e balancing effect shows a better dynamic characteristic than that of traditional methods. And the fluctuation range of the axis track of the rotor system also shows reductive phenomenon. /e proposed optimization spindle rotor system model is well verified through experiments. It can contribute a theoretical optimization foundation for available dynamic balance in spindle rotor system.


Introduction
Rotor system dynamic output characteristics determine the precision machining of aerospace, petrochemical, high speed railway, and other fields. In the study of rotor system dynamic characteristics, the dynamic unbalance is one of the most important subjects that can influence the stability problem [1][2][3]. When the spindle unit is running for a long time, the spindle will produce unbalanced force and vibration due to wear and deformation [4]. e instability of rotor system is prominent at high speed. In particular, when the speed of spindle is close to the critical speed, the deflection deformation of the spindle rotor system will aggravate the influence of unbalanced vibration and may seriously result in the damage of the spindle.
Many efforts have been made to study the efficiency and method of the spindle rotor system dynamic balance, aiming to solve the stability of the dynamic output problem. e key issue in spindle rotor system can improve the dynamic balance effect through some optimization method. Zhang and Zhang [5] proposed a total phase difference maximizing method which can select the actual axial position in the rigid rotor system. Huang et al. [6] presented a novel double-plane balancing method to balance the rotor system through transient amplitudes; the balancing efficiency can be improved greater than traditional steady-state modal method. Wen et al. [7] developed a rotor transient method of modal balance based on empirical mode decomposition theory, and the rotor system could pass the critical resonance region smoothly through adding reasonable trial weight. Chen et al. [8] gave a specific explanation of the periodic solution and quasi-periodic solution of the system through combining multiple harmonic balance method with Runge-Kutta method.
e nonlinear dynamic characteristics of rotor system were revealed under double excitation. Deepthikumar et al. [9] demonstrated the analysis of the modeling rotor system unbalances whose eccentricity polynomial function was considered, and the correction balance mass was calculated at critical speed. Besides, it has been showed that transient force of balance disc can be predicted directly by the vibration characteristics of the rotor system based on the Newmark method [10]. Bin et al. [11] investigated unbalance excitation effect on the rotor system dynamic balance. Reasonable balancing plane number and places of rotors were adjusted through the least squares method. e results indicated that the novel balancing method of flexible rotor system could improve efficiency.
In fact, it is far from enough to just analyze the dynamic balance of traditional method in spindle rotor system. Due to the nonlinear dynamic characteristics in high speed condition, some algorithm methods need to be used in the performance of rapidly suppressing vibration. Some relevant optimization and suppression vibration phenomena methods were also widely observed in rotor system. Tao et al. [12] adapted a particle swarm optimization algorithm based on multiscale adaptive cooperative mutation strategy to improve the accuracy of final calculation, and the global solution has also been analyzed. Yun et al. [13] established the optimization variables and individual fitness function based particle swarm optimization and modeled the optimization finite element model of rotor system which can suppress vibration effectively. Max et al. [14] proposed a modal weighted optimization method for evaluating residual modal unbalance. ey found that the residual modal unbalances have an obvious effect on rotor system balancing facilities. Li et al. [15] developed a modal dynamic balance method for high speed flexible rotor without trial weight, and the unbalance amount and azimuth of rotor system were rapidly obtained by the optimized method. Díaz et al. [16] proposed a novel method which could find the real modes of the rotor system through the coordinate transformation, which resulted in that the optimum extraction position of the balancing parameters can be determined. Besides, it has been demonstrated that the stability and efficiency of rotor system dynamic balancing could be improved through PSO algorithm [17][18][19].
However, as can be seen from the knowledge of the previous references, less research is related to the multiorder unbalance components. In order to analyze the dynamic balance effect on the spindle rotor system vibration, in the paper, the modal dynamic balance optimization model is adapted. Since this paper takes the sum of squares of residual vibration after balancing as the optimization objective, considering multiorder unbalance components, the correction parameters of each order after modal balance of spindle rotor system are optimized through particle swarm optimization algorithm. en, the optimal compensation amount of each order of unbalance components is achieved, which is employed to suppress unbalanced vibration effectively. A specific study is performed on the influence of the rotor system nonlinear dynamic behavior, which offers a theoretical optimization foundation for available dynamic balance in spindle rotor system.

Modal Balance Method.
Combined with the dynamics theory of spindle rotor system, the rotor system can be divided into several unbalanced components, and each component corresponds to respective main mode. e modal balance method can balance the unbalanced components separately. Spindle needs dynamic balance to keep rotor system in balance. us, the resonance field can be avoided when the rotation speed reaches critical speed. e force diagram of spindle rotor system is shown in Figure 1. k 1 and k 2 are the stiffness of the front and rear bearings, and c 1 and c 2 are the damping of the front and rear bearings, respectively.
Assuming that the unbalanced force on the spindle rotor system is F(z), the vibration differential equation of the motorized spindle is shown in the following equation [20]: where M is the mass matrix, C is the damping matrix, K is the stiffness matrix, x(z) is the vibration vector of the spindle rotor system, and X is the amplitude of vibration. e natural frequency of the spindle is multiorder in the process of rotation, and every vibration mode is orthogonal to the others. e orthogonal expression is shown in the following equation: where ξ is the mass matrix of characteristic function, N j is the modal mass the j th mode, and m is mass of the rotor system. e unbalance force of spindle rotor system is directly related to characteristic function, mass, and other parameters; the unbalanced force is shown in the following equation: where c j is the j th mode component contained in the eccentricity distribution, a j is the azimuth of the component, and Ω is the speed of the spindle rotor system. e vibration curve of the spindle rotor system can be regarded as the superposition of the main vibration modes of each order generated, which is shown in the following equation: where A j (Ω) is the dynamic method coefficient of spindle rotor system. Assuming that the spindle reaches balance, the support reaction force of the rotor system is shown in the following equation: where Q is the corrected mass of the spindle rotor system, F A and F B are the supporting reaction force of the rotor system, and φ is the vibration of the spindle rotor system. e relationship of the unbalance of the spindle rotor system and the correction quality is shown in the following equation:

Modal Balance Method Based on Particle Swarm
Optimization. e PSO algorithm is a global random search algorithm based on swarm intelligence, which is proposed by simulating the migration and clustering behavior of bird swarms during foraging. e PSO treats a counterweight block as a particle and all counterweight blocks as a particle swarm.
e position of each counterweight in the N-dimensional space can represent its weight, which can be regarded as a feasible solution.
e flight process of the counterweight in the N-dimensional space is the search process. e counterweight changes the flight speed continuously, and then the position changes continuously until the iteration conditions are satisfied or the global optimal solution is obtained. e relationship between the speed of the counterweight block and the changed position is shown in the following equation: where ω is an inertial factor, its value is less than 0, C 1 is the individual learning factor, C 2 is the population learning factor, C 1 , C 2 are constant, usually defined as C 1 � C 2 � 2, random(0, 1) is a random number on [0, 1], p id is the optimal position of each particle in N-dimensional space, and p gd is the global optimal position. e square sum of the residual vibration δ of the modal balance method is used as the fitness function in the particle swarm calculation process, and the correction mass during balancing cannot exceed the maximum mass allowed by the correction plane, and the fitness function of the algorithm is shown in the following equation: where Q is the maximum mass allowed for the correction plane. e operation process of the particle swarm algorithm is as follows, and the flowchart of particle swarm algorithm is shown in Figure 2.
(1) N sets of counterweight masses are randomly generated as the initial solution, which is the initial population of the particle swarm algorithm. (2) 2 random numbers are randomly generated as the flying speed and distance of the weight mass. (3) e fitness function corresponding to the weight of each group is calculated. (4) e calculated fitness function values are compared, and the optimal quality of the counterweight itself and the global optimal quality are recorded. (5) Determining whether the global optimal weight quality within the allowed range is achieved: if it is, the result is output; if not, continue to the next step. (6) Updating the weight mass according to the initial flight speed and distance set, and the next flight speed and distance of the weight are changed; return to step (3) which can perform the next iteration until the optimal weight is obtained.

e Calculation of Modal Simulation.
According to the self-balancing spindle rotor system independently developed, the rotor system model is established. e rotor system is supported through the front and rear bearing. e front bearing and rear bearing are 7012 and 7009 angular contact ball bearings, respectively. e specific parameters of rotor system are shown in Table 1.
Before the modal analysis of the spindle rotor system, it is necessary to discretize the bearing rotor model unit, through meshing method. It is significant to select a reasonable meshing method, which can affect the analysis process and results of modal analysis. In the paper, 6-hedral division method is used in the front bearing, and 4-hedral division method is adopted in the rear bearing. e shaft is also divided according to the size of each step. e mesh division effect diagram of the spindle rotor system is shown in Figure 3. e dynamic balance head is installed in the cavity of the front end in the spindle rotor system, which can realize the online dynamic balance. e rotor system model is Due to the increasing speed, the centrifugal inertia force and flexible deformation of the rotor obviously affect the vibration. Compared with the first-order vibration mode, the second-order vibration mode of the rotor system has bending deformation, and the deformation degree increases by 33.15%.
e Campbell diagram of rotor system can be obtained by modal analysis. e critical speed of rotor system can be received from Campbell diagram. e first-order speed and second-order speed of rotor system are 6006.4 r/min and 22060.6 r/min, respectively. Because rotor system will vibrate strongly near the critical speed, it is necessary to avoid the critical speed in the experiment. 6000 r/min is close to the critical speed which is selected as the balance speed. e experimental speed starts from 2000 r/min, and the experimental speed is recorded every 2000 r/min until 24000 r/min. e dynamic balance of the rotor system is studied from different speed.

e Calculation of Dynamic Balance.
It is assumed that the established rotor model has no unbalance under ideal conditions; an unbalance mass block is added to the front end of the rotor system to simulate the unbalance effect. e proposed particle swarm optimization method is applied to balance the spindle rotor system in the balance simulation, and the process can be used to check the rationality of the    Advances in Materials Science and Engineering counterweight block which is obtained by the optimization method. e front and rear end of the rotor system can be used as a balance correction surface. e method of adding unbalance amount block in the end of the rotor system is adapted. e three kinds of unbalance, 5 g·mm, 10 g·mm, and 15 g·mm, are added, and the phase is 0°, 90°, and 180°, respectively. en the first two modes of the rotor system are obtained by modal analysis. According to the balance conditions of the modal balance method, the correction amount needed to be added on the balance correction surface can be calculated. After that the optimized balance of the rotor system needs to be carried out. e optimized balance is to calculate the weight of the balanced counterweight block through the particle swarm optimization. e correction and phase of unbalance mass of the spindle rotor system in 5 g·mm, 10 g·mm, and 15 g·mm can be obtained, as shown in Tables 2-4, respectively. From the three tables, the weight mass and phase required for balancing the rotor system at different unbalance levels can be seen. e vibration amplitudes of rotor system can be obtained through the above tables, which is shown in Figures 5-7. e vibration amplitude of the rotor system without balance, which fluctuates greatly at 6000 r/min and 22000 r/min, is demonstrated in Figure 5. e dynamic balance is a very important vibration factor of rotor system, so this section will mainly study the influence of dynamic balance on the dynamic behavior. From Figure 6, it can be exhibited that the average dynamic balance rate is 64.87% through rotor system balancing. And the maximum balance rate is 71.27% at the condition that the speed is 20000 r/min and the unbalance is 5 g·mm. e amplitude of the rotor system through optimized balance is shown in Figure 7. It can be found that the effect of optimized balancing on rotor system is significant. erefore, it is very necessary to study the influence of PSO algorithm on the balance of rotor system. e average balance rate is 72.38% through optimized balance. When the speed is 6000 r/min and the unbalance is 10 g·mm, the maximum balance rate of the optimized rotor system amplitude is 75.88%. What is more, compared with the modal balance method, the maximum vibration amplitude decreased by 34.75%, and the average amplitude decreased by 21.23%.
When the unbalance amount is 10 g·mm and the speed is, respectively, at 6000 r/min and 22000 r/min, the axis movement trajectories of the rotor system in three cases are shown in Figure 8.
us, in Figure 8(a), the axis movement trajectories without balance, modal balance, and balanced modal based on particle swarm optimization can be seen corresponding to trajectories radius of 24.41 μm, 9.07 μm, and 5.93 μm, respectively. e results of trajectories diagrams show that the optimized balance method effect on the rotor system is obvious. From Figure 8(b), the speed has a great influence on the balance of the rotor system. With the increase in rotational speed, the influence of movement trajectories on the dynamic characteristics of spindle rotor system began to be large. In the high speed range, compared with the low speed, that of the trajectories radius is 30.68 μm, 10.52 μm, and 8.48 μm; the response of rotor system evolves from strong vibration and centrifugal effect. e frequency domain is also a good way to observe in cover low-rising periodic signal; the fundamental frequency signal represents the state of unbalance vibration of spindle rotor system. e frequency domain of the spindle rotor system is shown in Figure 9. e fundamental frequency value of the rotor system decreased obviously through optimized balance. When the speed is 6000 r/min, through PSO balance method, the amplitude of the frequency domain compared with balance modal method and without balance decreased by 39.68% and 44.66%. e results show that the rotor system balancing method based on particle swarm optimization is effective.

Setting Up Experimental Platform.
e dynamic balance experimental platform consists of spindle (HT-170-11), data collector (MRBB47), and laser vibrometer (OFV-505/5000), which is shown in Figure 10. e front and rear ends of the spindle can be added mass blocks; the specific parameters of the spindle are shown in Table 5. e vibration of the spindle is measured through laser vibrometer under different conditions, which illuminates the front end of the spindle based on Doppler effect. e speed selection range of spindle is 4000-24000 rpm, and every speed interval is 2000 r/min. Due to the high speed of motorized spindle, the protective device is adopted in the experimental platform.
Unbalance mass of 5 g·mm, 10 g·mm, and 15 g·mm is added at the front end of spindle, with initial phases of 0°, 90°, and 180°, respectively. And the first two order modes of the spindle rotor system are [0.742, 0.742; 0.459, 0.170]. e unbalance correction and phase of the spindle rotor system at 5 g·mm, 10 g·mm, and 15 g·mm can be obtained, as shown in Tables 6-8. e experiment vibration amplitude comparison diagram of spindle rotor system under different conditions is Advances in Materials Science and Engineering 5 shown in Figures 11-13. It can be seen that the vibration amplitude fluctuates greatly at 6000 r/min and 22000 r/min. is is because the speed of spindle is close to the critical speed. Figure 11 shows that the maximum vibration of the rotor system is emerged in 22000 r/min, which means that it is a synchronous response with the natural frequency. In

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addition, this phenomenon indicates that the influence of nonlinear vibration caused by unbalance mass and speed begins to increase gradually.
In Figure 12, the results show that the modal balance method has an obvious influence on the rotor system vibration. It can be seen that the vibration of the rotor system causes decreasing phenomenon especially at high speed. And the decreasing average value of vibration is 64.3% at the condition of 5 g·mm unbalance mass. Besides, spindle rotor system has a marked improvement of the dynamic behavior. Figure 13 depicts a diagram for experiment vibration amplitude of spindle rotor system with optimized balance.  Compared with Figures 11 and 12, it indicates that the change trend of the vibration curve is basically the same with them. However, it is found that the vibration curve is relatively small through PSO balance, which can effectively suppress the vibration caused by rotor imbalance.
At the condition of unbalance mass of 15 g·mm, a comprehensive view of the effect of the PSO balance on the spindle rotor system is given in Figure 14.
As can be seen, the vibration of the rotor system without balance is much larger than other conditions, in which the       maximum amplitude exceeds 41 μm. e good news is that the dynamic behavior of the rotor system is improved through dynamic balance. Besides, the PSO optimization algorithm is applied in the modal balance. Note that the simulation and experimental average error is 4% through optimized balance. e results can give a better explanation to the PSO optimization algorithm existence of improving the spindle rotor system dynamic characteristics.

Conclusion
e PSO dynamic modal balance has been applied in the nonlinear dynamic behavior of spindle rotor system which have been presented in this paper. e PSO dynamic modal balance model is established to suppress vibration. e spindle rotor system before or after dynamic balance is obtained through dynamic model. e unbalance response of different unbalance mass was studied. e results reveal that, through PSO dynamic modal balance, the vibration amplitude is smaller than that without balance or dynamic modal balance. As the speed increases, the PSO dynamic modal balance method has an obvious effect on improving the dynamic characteristics of rotor system. And the stability and accuracy of dynamic balance model were verified through different experiments, and the average error is 4%. erefore, to avoid the strong vibration in the spindle rotor system, the investigation on the dynamic balance based on the PSO method is of great significance during the operation stage.

Data Availability
e data used to support the findings of this study are available from the corresponding author upon request.

Conflicts of Interest
e authors declare that they have no conflicts of interest.