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

Authors: Zhan Wang; Dongzheng Li; Zinan Wang; Aoxiang Liu; Ruiyao Tao
Journal: Advances in Materials Science and Engineering
 (2021)

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## Abstract

The 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. The 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. The optimal correction weight of every unbalance component is calculated through a modal matrix equation of PSO. The vibration amplitude that is greatly reduced after optimization balance is presented under different conditions. The 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. The 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.


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## Body

## 1. 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 [1–3]. When the spindle unit is running for a long time, the spindle will produce unbalanced force and vibration due to wear and deformation [4]. The 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. The 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. The 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. The 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. They 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 [17–19].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. Then, 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.


## 2. Modal Balance Method Based on Particle Swarm Optimization

### 2.1. 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. The modal balance method can balance the unbalanced components separately. Spindle needs dynamic balance to keep rotor system in balance. Thus, the resonance field can be avoided when the rotation speed reaches critical speed. The force diagram of spindle rotor system is shown in Figure1. k1 and k2 are the stiffness of the front and rear bearings, and c1 and c2 are the damping of the front and rear bearings, respectively.Figure 1
The force diagram of spindle rotor system.Assuming that the unbalanced force on the spindle rotor system isF(z), the vibration differential equation of the motorized spindle is shown in the following equation [20]:(1)Mx¨z+Cx˙z+Kxz=Fz,xz=Xesz,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.The natural frequency of the spindle is multiorder in the process of rotation, and every vibration mode is orthogonal to the others. The orthogonal expression is shown in the following equation:(2)∫0lmξizξjzdz=0,i≠j,Nj,i=j,where ξ is the mass matrix of characteristic function, Nj is the modal mass the jth mode, and m is mass of the rotor system.The 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:(3)Fz=Ω2∑j=1∞cjmzξjz,cj=cjeiaj,where cj is the jth mode component contained in the eccentricity distribution, aj is the azimuth of the component, and Ω is the speed of the spindle rotor system.The 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:(4)aj=AjΩcj,AjΩ=Ω2λj2−Ω2,where Aj(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:(5)FA=Ω2l∫0lzmzφdz+∫0lzFzdz+∑k=1KzkQk,FB=Ω2l∫0ll−zmzφdz+∫0ll−zFzdz+∑k=1Kl−zkQkFA+FB=Ω2∫0lmzφdz+∫0lFzdz+∑k=1KQk,,where Q is the corrected mass of the spindle rotor system, FA and FB are the supporting reaction force of the rotor system, and φ is the vibration of the spindle rotor system.The relationship of the unbalance of the spindle rotor system and the correction quality is shown in the following equation:(6)ξ1ξ1⋯ξ1ξ2ξ2⋯ξ2⋮⋮⋱⋮ξmξm⋯ξmQ1Q2⋯QnQ1Q2⋯Qn⋮⋮⋱⋮Q1Q2⋯Qn=F1zF2z⋮Fmz.


### 2.2. Modal Balance Method Based on Particle Swarm Optimization

The 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. The PSO treats a counterweight block as a particle and all counterweight blocks as a particle swarm. The position of each counterweight in theN-dimensional space can represent its weight, which can be regarded as a feasible solution. The flight process of the counterweight in the N-dimensional space is the search process. The 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. The relationship between the speed of the counterweight block and the changed position is shown in the following equation:(7)Vid=ωVid+C1random0,1pid−Xid,+C2random0,1pgd−Xid,Xid=Xid+Vid,where ω is an inertial factor, its value is less than 0, C1 is the individual learning factor, C2 is the population learning factor, C1, C2 are constant, usually defined as C1 = C2 = 2, random(0, 1) is a random number on [0, 1], pid is the optimal position of each particle in N-dimensional space, and pgd is the global optimal position.The square sum of the residual vibrationδ 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:(8)fx=δ2,δ=ξQ+F,where Q is the maximum mass allowed for the correction plane.The operation process of the particle swarm algorithm is as follows, and the flowchart of particle swarm algorithm is shown in Figure2.(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)
The fitness function corresponding to the weight of each group is calculated.(4)
The 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.Figure 2
The chart of particle swarm algorithm.


## 2.1. 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. The modal balance method can balance the unbalanced components separately. Spindle needs dynamic balance to keep rotor system in balance. Thus, the resonance field can be avoided when the rotation speed reaches critical speed. The force diagram of spindle rotor system is shown in Figure1. k1 and k2 are the stiffness of the front and rear bearings, and c1 and c2 are the damping of the front and rear bearings, respectively.Figure 1
The force diagram of spindle rotor system.Assuming that the unbalanced force on the spindle rotor system isF(z), the vibration differential equation of the motorized spindle is shown in the following equation [20]:(1)Mx¨z+Cx˙z+Kxz=Fz,xz=Xesz,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.The natural frequency of the spindle is multiorder in the process of rotation, and every vibration mode is orthogonal to the others. The orthogonal expression is shown in the following equation:(2)∫0lmξizξjzdz=0,i≠j,Nj,i=j,where ξ is the mass matrix of characteristic function, Nj is the modal mass the jth mode, and m is mass of the rotor system.The 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:(3)Fz=Ω2∑j=1∞cjmzξjz,cj=cjeiaj,where cj is the jth mode component contained in the eccentricity distribution, aj is the azimuth of the component, and Ω is the speed of the spindle rotor system.The 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:(4)aj=AjΩcj,AjΩ=Ω2λj2−Ω2,where Aj(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:(5)FA=Ω2l∫0lzmzφdz+∫0lzFzdz+∑k=1KzkQk,FB=Ω2l∫0ll−zmzφdz+∫0ll−zFzdz+∑k=1Kl−zkQkFA+FB=Ω2∫0lmzφdz+∫0lFzdz+∑k=1KQk,,where Q is the corrected mass of the spindle rotor system, FA and FB are the supporting reaction force of the rotor system, and φ is the vibration of the spindle rotor system.The relationship of the unbalance of the spindle rotor system and the correction quality is shown in the following equation:(6)ξ1ξ1⋯ξ1ξ2ξ2⋯ξ2⋮⋮⋱⋮ξmξm⋯ξmQ1Q2⋯QnQ1Q2⋯Qn⋮⋮⋱⋮Q1Q2⋯Qn=F1zF2z⋮Fmz.


## 2.2. Modal Balance Method Based on Particle Swarm Optimization

The 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. The PSO treats a counterweight block as a particle and all counterweight blocks as a particle swarm. The position of each counterweight in theN-dimensional space can represent its weight, which can be regarded as a feasible solution. The flight process of the counterweight in the N-dimensional space is the search process. The 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. The relationship between the speed of the counterweight block and the changed position is shown in the following equation:(7)Vid=ωVid+C1random0,1pid−Xid,+C2random0,1pgd−Xid,Xid=Xid+Vid,where ω is an inertial factor, its value is less than 0, C1 is the individual learning factor, C2 is the population learning factor, C1, C2 are constant, usually defined as C1 = C2 = 2, random(0, 1) is a random number on [0, 1], pid is the optimal position of each particle in N-dimensional space, and pgd is the global optimal position.The square sum of the residual vibrationδ 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:(8)fx=δ2,δ=ξQ+F,where Q is the maximum mass allowed for the correction plane.The operation process of the particle swarm algorithm is as follows, and the flowchart of particle swarm algorithm is shown in Figure2.(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)
The fitness function corresponding to the weight of each group is calculated.(4)
The 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.Figure 2
The chart of particle swarm algorithm.


## 3. Simulation Analysis of the Spindle Rotor System

### 3.1. The Calculation of Modal Simulation

According to the self-balancing spindle rotor system independently developed, the rotor system model is established. The rotor system is supported through the front and rear bearing. The front bearing and rear bearing are 7012 and 7009 angular contact ball bearings, respectively. The specific parameters of rotor system are shown in Table1.Table 1
The specific parameters of rotor system.
ParameterSizeLength of rotor400 mmDiameter of rotor57 mmInner diameter of rotor24 mmDiameter of disk100 mmThickness of disk150 mmMass of disk9.24 kgElastic modulusE = 2.1 × 1011Before 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. The shaft is also divided according to the size of each step. The mesh division effect diagram of the spindle rotor system is shown in Figure3.Figure 3
The mesh division effect diagram of the spindle rotor system.The dynamic balance head is installed in the cavity of the front end in the spindle rotor system, which can realize the online dynamic balance. The rotor system model is calculated and analyzed through finite element software. The first- and second-order vibration mode of the rotor system are obtained, as shown in Figure4. It can be seen that the rotor system has the largest deformation near the two bearings, so the front and rear contacting end area are taken as the correcting area of the unbalance amount. The first two main modes of the rotor system are [0.742, 0.742; 0.459, 0.170].Figure 4
Vibration mode of bearing rotor. (a) First-order vibration mode. (b) Second-order vibration mode.
(a)(b)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%.The Campbell diagram of rotor system can be obtained by modal analysis. The critical speed of rotor system can be received from Campbell diagram. The first-order speed and second-order speed of rotor system are 6006.4r/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. The experimental speed starts from 2000 r/min, and the experimental speed is recorded every 2000 r/min until 24000 r/min. The dynamic balance of the rotor system is studied from different speed.


### 3.2. The 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. The 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 counterweight block which is obtained by the optimization method. The front and rear end of the rotor system can be used as a balance correction surface. The method of adding unbalance amount block in the end of the rotor system is adapted. The 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. Then 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. The optimized balance is to calculate the weight of the balanced counterweight block through the particle swarm optimization. The 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 Tables2–4, respectively. From the three tables, the weight mass and phase required for balancing the rotor system at different unbalance levels can be seen.Table 2
Simulation data of 5 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)16.7618.0224.4120.1822.5024.2326.3228.0030.1532.6936.7433.48Correction value (g·mm)Front end3.96∠180°Rear end10.70∠0°Amplitude after balance (μm)4.815.759.076.627.188.308.919.5710.0511.5014.5212.45Optimize correction amount (g·mm)Front end3.81∠180°Rear end10.55∠0°Amplitude after optimized balance (μm)4.044.365.935.195.966.446.887.608.068.6511.439.64Table 3
Simulation data of 10 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)17.6219.4025.1921.2223.2825.1527.3929.4231.1333.2739.1035.79Correction value (g·mm)Front end7.93∠270°Rear end21.40∠90°Amplitude after balance (μm)5.476.419.586.887.899.009.489.8410.9013.8717.1514.45Optimize correction amount (g·mm)Front end5.47∠270°Rear end18.95∠90°Amplitude after optimized balance (μm)4.364.856.255.426.367.337.328.469.079.9212.6310.36Table 4
Simulation data of 15 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)18.9920.8226.8222.7324.3726.7729.3230.3632.6435.3940.8136.52Correction value (g·mm)Front end11.89∠0°Rear end32.12∠180°Amplitude after balance (μm)6.246.789.997.228.519.399.8710.6011.7313.8717.1514.45Optimize correction amount (g·mm)Front end9.71∠0°Rear end29.93∠180°Amplitude after optimized balance (μm)4.755.377.016.026.847.928.129.029.6710.5614.1311.64The vibration amplitudes of rotor system can be obtained through the above tables, which is shown in Figures5–7. The vibration amplitude of the rotor system without balance, which fluctuates greatly at 6000 r/min and 22000 r/min, is demonstrated in Figure 5. The 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.Figure 5
Amplitude of spindle rotor system without balance.Figure 6
Amplitude of spindle rotor system with balance.Figure 7
Amplitude of spindle rotor system with optimized balance.The amplitude of the rotor system through optimized balance is shown in Figure7. It can be found that the effect of optimized balancing on rotor system is significant. Therefore, it is very necessary to study the influence of PSO algorithm on the balance of rotor system. The 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 Figure8.Figure 8
The axis movement trajectories of spindle rotor system. (a) The speed is 6000r/min. (b) The speed is 22000 r/min.
(a)(b)Thus, in Figure8(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. The 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.The 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. The frequency domain of the spindle rotor system is shown in Figure9. The 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%. The results show that the rotor system balancing method based on particle swarm optimization is effective.Figure 9
The frequency domain of the spindle rotor system.


## 3.1. The Calculation of Modal Simulation

According to the self-balancing spindle rotor system independently developed, the rotor system model is established. The rotor system is supported through the front and rear bearing. The front bearing and rear bearing are 7012 and 7009 angular contact ball bearings, respectively. The specific parameters of rotor system are shown in Table1.Table 1
The specific parameters of rotor system.
ParameterSizeLength of rotor400 mmDiameter of rotor57 mmInner diameter of rotor24 mmDiameter of disk100 mmThickness of disk150 mmMass of disk9.24 kgElastic modulusE = 2.1 × 1011Before 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. The shaft is also divided according to the size of each step. The mesh division effect diagram of the spindle rotor system is shown in Figure3.Figure 3
The mesh division effect diagram of the spindle rotor system.The dynamic balance head is installed in the cavity of the front end in the spindle rotor system, which can realize the online dynamic balance. The rotor system model is calculated and analyzed through finite element software. The first- and second-order vibration mode of the rotor system are obtained, as shown in Figure4. It can be seen that the rotor system has the largest deformation near the two bearings, so the front and rear contacting end area are taken as the correcting area of the unbalance amount. The first two main modes of the rotor system are [0.742, 0.742; 0.459, 0.170].Figure 4
Vibration mode of bearing rotor. (a) First-order vibration mode. (b) Second-order vibration mode.
(a)(b)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%.The Campbell diagram of rotor system can be obtained by modal analysis. The critical speed of rotor system can be received from Campbell diagram. The first-order speed and second-order speed of rotor system are 6006.4r/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. The experimental speed starts from 2000 r/min, and the experimental speed is recorded every 2000 r/min until 24000 r/min. The dynamic balance of the rotor system is studied from different speed.


## 3.2. The 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. The 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 counterweight block which is obtained by the optimization method. The front and rear end of the rotor system can be used as a balance correction surface. The method of adding unbalance amount block in the end of the rotor system is adapted. The 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. Then 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. The optimized balance is to calculate the weight of the balanced counterweight block through the particle swarm optimization. The 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 Tables2–4, respectively. From the three tables, the weight mass and phase required for balancing the rotor system at different unbalance levels can be seen.Table 2
Simulation data of 5 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)16.7618.0224.4120.1822.5024.2326.3228.0030.1532.6936.7433.48Correction value (g·mm)Front end3.96∠180°Rear end10.70∠0°Amplitude after balance (μm)4.815.759.076.627.188.308.919.5710.0511.5014.5212.45Optimize correction amount (g·mm)Front end3.81∠180°Rear end10.55∠0°Amplitude after optimized balance (μm)4.044.365.935.195.966.446.887.608.068.6511.439.64Table 3
Simulation data of 10 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)17.6219.4025.1921.2223.2825.1527.3929.4231.1333.2739.1035.79Correction value (g·mm)Front end7.93∠270°Rear end21.40∠90°Amplitude after balance (μm)5.476.419.586.887.899.009.489.8410.9013.8717.1514.45Optimize correction amount (g·mm)Front end5.47∠270°Rear end18.95∠90°Amplitude after optimized balance (μm)4.364.856.255.426.367.337.328.469.079.9212.6310.36Table 4
Simulation data of 15 g·mm unbalanced mass.
Speed (r/min)20004000600080001000012000140001600018000200002200024000Initial amplitude (μm)18.9920.8226.8222.7324.3726.7729.3230.3632.6435.3940.8136.52Correction value (g·mm)Front end11.89∠0°Rear end32.12∠180°Amplitude after balance (μm)6.246.789.997.228.519.399.8710.6011.7313.8717.1514.45Optimize correction amount (g·mm)Front end9.71∠0°Rear end29.93∠180°Amplitude after optimized balance (μm)4.755.377.016.026.847.928.129.029.6710.5614.1311.64The vibration amplitudes of rotor system can be obtained through the above tables, which is shown in Figures5–7. The vibration amplitude of the rotor system without balance, which fluctuates greatly at 6000 r/min and 22000 r/min, is demonstrated in Figure 5. The 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.Figure 5
Amplitude of spindle rotor system without balance.Figure 6
Amplitude of spindle rotor system with balance.Figure 7
Amplitude of spindle rotor system with optimized balance.The amplitude of the rotor system through optimized balance is shown in Figure7. It can be found that the effect of optimized balancing on rotor system is significant. Therefore, it is very necessary to study the influence of PSO algorithm on the balance of rotor system. The 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 Figure8.Figure 8
The axis movement trajectories of spindle rotor system. (a) The speed is 6000r/min. (b) The speed is 22000 r/min.
(a)(b)Thus, in Figure8(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. The 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.The 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. The frequency domain of the spindle rotor system is shown in Figure9. The 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%. The results show that the rotor system balancing method based on particle swarm optimization is effective.Figure 9
The frequency domain of the spindle rotor system.


## 4. Experimental Verification

### 4.1. Setting Up Experimental Platform

The dynamic balance experimental platform consists of spindle (HT-170-11), data collector (MRBB47), and laser vibrometer (OFV-505/5000), which is shown in Figure10. The front and rear ends of the spindle can be added mass blocks; the specific parameters of the spindle are shown in Table 5. The vibration of the spindle is measured through laser vibrometer under different conditions, which illuminates the front end of the spindle based on Doppler effect. The 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.Figure 10
The dynamic balance experimental platform.Table 5
The specific parameters of spindle.
ParameterSizeAxial length400 mmRadius of the rotor50 mmModulus of elasticityE = 2.1 × 1011Frequency500 HzCurrent22.3 AFront bearing7012 angular contact ball bearingsRear bearing7009 angular contact ball bearingsCoolingWater coolingLubricationOil and gas lubricationLogarithm of motor poles2Power11 kWUnbalance 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]. The 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 Tables6–8.Table 6
Experimental data of 5 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude /μm18.525.92023.123.625.828.730.632.237.134.5Correction value (g·mm)Front end8.32∠180°Rear end22.48∠0°Amplitude after balance (μm)4.956.535.536.557.578.238.939.310.112.810.6Optimize correction amount (g·mm)Front end6.81∠180°Rear end19.96∠0°Amplitude after optimization/μm4.866.445.396.296.747.267.768.568.7411.69.95Table 7
Experimental data of 10 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude/μm19.626.520.62425.627.530.131.433.738.236.2Correction value/g·mmFront end16.64∠270°Rear end44.95∠90°Amplitude after balance/μm6.9210.597.058.279.439.610.3211.112.716.414.3Optimize correction amount/g·mmFront end14.08∠270°Rear end42.38∠90°Amplitude after optimization/μm4.956.535.536.557.578.238.939.310.112.810.6Table 8
Experimental data of 15 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude/μm2127.323.424.626.630.631.43336.341.436.8Correction value/g·mmFront end24.97∠0°Rear end67.43∠180°Amplitude after balance/μm7.3410.847.38.569.610.110.812.514.31814.7Optimize correction amount/g·mmFront end22.44∠0°Rear end64.89∠180°Amplitude after optimization/μm6.037.436.237.098.228.679.1510.110.714.611.9The experiment vibration amplitude comparison diagram of spindle rotor system under different conditions is shown in Figures11–13. It can be seen that the vibration amplitude fluctuates greatly at 6000 r/min and 22000 r/min. This 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 addition, this phenomenon indicates that the influence of nonlinear vibration caused by unbalance mass and speed begins to increase gradually.Figure 11
Experiment vibration amplitude of spindle rotor system without balance.Figure 12
Experiment vibration amplitude of spindle rotor system with balance.Figure 13
Experiment amplitude of spindle rotor system with optimized balance.In Figure12, 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.Figure13 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 Figure14.Figure 14
Simulation and experiment of rotor system vibration amplitude.As can be seen, the vibration of the rotor system without balance is much larger than other conditions, in which the maximum amplitude exceeds 41μm. The 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. The results can give a better explanation to the PSO optimization algorithm existence of improving the spindle rotor system dynamic characteristics.


## 4.1. Setting Up Experimental Platform

The dynamic balance experimental platform consists of spindle (HT-170-11), data collector (MRBB47), and laser vibrometer (OFV-505/5000), which is shown in Figure10. The front and rear ends of the spindle can be added mass blocks; the specific parameters of the spindle are shown in Table 5. The vibration of the spindle is measured through laser vibrometer under different conditions, which illuminates the front end of the spindle based on Doppler effect. The 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.Figure 10
The dynamic balance experimental platform.Table 5
The specific parameters of spindle.
ParameterSizeAxial length400 mmRadius of the rotor50 mmModulus of elasticityE = 2.1 × 1011Frequency500 HzCurrent22.3 AFront bearing7012 angular contact ball bearingsRear bearing7009 angular contact ball bearingsCoolingWater coolingLubricationOil and gas lubricationLogarithm of motor poles2Power11 kWUnbalance 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]. The 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 Tables6–8.Table 6
Experimental data of 5 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude /μm18.525.92023.123.625.828.730.632.237.134.5Correction value (g·mm)Front end8.32∠180°Rear end22.48∠0°Amplitude after balance (μm)4.956.535.536.557.578.238.939.310.112.810.6Optimize correction amount (g·mm)Front end6.81∠180°Rear end19.96∠0°Amplitude after optimization/μm4.866.445.396.296.747.267.768.568.7411.69.95Table 7
Experimental data of 10 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude/μm19.626.520.62425.627.530.131.433.738.236.2Correction value/g·mmFront end16.64∠270°Rear end44.95∠90°Amplitude after balance/μm6.9210.597.058.279.439.610.3211.112.716.414.3Optimize correction amount/g·mmFront end14.08∠270°Rear end42.38∠90°Amplitude after optimization/μm4.956.535.536.557.578.238.939.310.112.810.6Table 8
Experimental data of 15 g·mm unbalanced mass.
Rotating speed/r/min4000600080001000012000140001600018000200002200024000Initial amplitude/μm2127.323.424.626.630.631.43336.341.436.8Correction value/g·mmFront end24.97∠0°Rear end67.43∠180°Amplitude after balance/μm7.3410.847.38.569.610.110.812.514.31814.7Optimize correction amount/g·mmFront end22.44∠0°Rear end64.89∠180°Amplitude after optimization/μm6.037.436.237.098.228.679.1510.110.714.611.9The experiment vibration amplitude comparison diagram of spindle rotor system under different conditions is shown in Figures11–13. It can be seen that the vibration amplitude fluctuates greatly at 6000 r/min and 22000 r/min. This 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 addition, this phenomenon indicates that the influence of nonlinear vibration caused by unbalance mass and speed begins to increase gradually.Figure 11
Experiment vibration amplitude of spindle rotor system without balance.Figure 12
Experiment vibration amplitude of spindle rotor system with balance.Figure 13
Experiment amplitude of spindle rotor system with optimized balance.In Figure12, 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.Figure13 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 Figure14.Figure 14
Simulation and experiment of rotor system vibration amplitude.As can be seen, the vibration of the rotor system without balance is much larger than other conditions, in which the maximum amplitude exceeds 41μm. The 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. The results can give a better explanation to the PSO optimization algorithm existence of improving the spindle rotor system dynamic characteristics.


## 5. Conclusion

The PSO dynamic modal balance has been applied in the nonlinear dynamic behavior of spindle rotor system which have been presented in this paper. The PSO dynamic modal balance model is established to suppress vibration. The spindle rotor system before or after dynamic balance is obtained through dynamic model. The unbalance response of different unbalance mass was studied. The 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%. Therefore, 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.



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*Source: 9728248-2021-12-20.xml*