# Theory of Frequency Captured of Eccentric Rotor by Vibration Environment with Same Direction

Authors: Su Ming; Li Rong; Xie Zhiping; Zheng Jiming
Journal: Shock and Vibration
 (2021)

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## Abstract

Aiming at the frequency synchronization phenomena of oscillating or rotating bodies, this paper proposes a novel solution to address the self-synchronization problem of vibration systems. An integral mean method with small parameters and periodic coefficient (IMM-SPPC) is proposed, which converts the relative motion of the electrically driven eccentric rotor and the vibration environment into a second-order periodic coefficient differential equation. Through the calculation of the equilibrium point of the second-order periodic coefficient differential equation and the study of its stability, the synchronization criterion and the stability criterion of the eccentric rotor and the vibration environment are deduced. The simulation results show the validity of the deduced synchronization criterion and stability criterion. The proposed IMM-SPPC provides a new way for studying vibration synchronization.


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## Body

## 1. Introduction

Beginning with the phenomenon discovered by Huijgens [1], vibration synchronizations have drawn researchers’ attention in wide fields of mathematics, physics, and biology as well as in industrial applications of mechanical and electrical engineering, such as large-scale vibrating screen [2], vibrating feeder [3], and so on. There are two types of synchronizations in a general definition. The synchronous regime achieved by introducing special actions or imposing special constraints is defined as forced or controlled synchronization. The synchronous regime arose due to natural properties, and interactions of the processes are defined as self-synchronization, e.g., frequency synchronization of oscillating or rotating bodies. This paper focuses on addressing the problem of vibration synchronizations.During the last decades, experts and scholars have made efforts on the vibration synchronization of mechanical systems and proposed three main methods such as the direct motion separation method, average torque difference method, and small parameter method [4–17]. The direct motion separation method was employed to address the vibration synchronization problem of objects with almost uniform rotations [9]. By using this method, the average speed and the phase difference of motors are formulated into fast motion component and slow motion component in the initial differential equation of the system motion. Then, the vibration synchronization problem is transformed into the solution existence of an integral stability criterion [7–9]. However, this method neglects the working conditions of the vibration systems [10] which results in certain limitations in practical engineering applications. In order to deal with this drawback, Wen proposed a principle of vibration synchronization of mechanical systems (vibratory synchronization transmission) by utilizing the average torque difference method, which transforms the vibratory motion into the phase difference of two eccentric rotors and introduces its corresponding working conditions [6, 11–13]. Moreover, this method was applied to a plane-motion dual-mass dual-machine offset self-synchronizing vibrator [6, 11], a plane single-mass dual-machine self-synchronizing vibrator with the same direction and reverse rotation [12], and a plane-motion single-mass dual-machine offset self-synchronizing vibrator [13]. However, the existing disturbances of average speed and phase difference of the two rotors are ignored. A modified average torque method with small parameters was introduced to convert the self-synchronization of two eccentric rotors into existence and stability of the zero solutions of the differential equations, including the disturbance parameters of phase difference and average rotational velocity [14–16]. Various mechanical systems are designed by employing this average torque method with small parameters, such as a dual-mass four-machine driven vibration system [14], an identical rotary two-machine driven vibration system with an unbalanced rotor [15], two nonidentical exciters driven nonresonant vibrating system [16], two cylindrical rollers in far resonance [17], the asymmetrically placed dual-machine drive rotation ultra-distant resonance vibration system [18], two exciters driven dual-mass vibrating system [19], and frequency doubling control synchronization systems with two rotors in reverse rotation [20]. Although the mentioned modified average method is able to address the self-synchronization and controlled synchronization of two or more motors, the synchronization and stability criteria deviate from the perspective of vibratory synchronization transmission. However, the self-synchronization phenomena, such as vibratory synchronization between the moon’s orbital motion and its rotational motion, have not been fully considered yet.Motivated by the above discussion, this paper proposes a novel solution to address the self-synchronization problem of vibration systems. Assuming that an electrically driven eccentric rotor rotates anti-clockwise in a vibration environment. The vibration environment is set as a vibration field that changes periodically inx-direction. By defining a small parameter integral mean variable, the rotation motion of electrically driven eccentric rotor is converted into a second-order periodic coefficient differential equation. Then, the synchronization and stability criteria for the eccentric rotor and vibration environment are derived.The contribution of this article is mainly reflected in the following aspects:(1)
An integral mean method with small parameters and periodic coefficient (IMM-SPPC) is proposed, which converts the relative motion of the eccentric rotor and the vibration environment into a second-order periodic coefficient differential equation.(2)
By solving the steady-state solution of the periodic coefficient differential equation at the equilibrium point, the synchronization criterion and the stability criterion of the eccentric rotor and the vibration environment are derived.(3)
The simulation results verify the validity of the synchronization criterion and the stability criterion and provide a novel way of studying vibration self-synchronization.This article gives a single-motor vibration model and establishes the differential equation of motion in the Section2. Section 3 gives the synchronization and stability criteria of the single motor and the vibration environment. Section 4 carries out a computer simulation and verification of the criterion. Finally, some conclusions and discussions are drawn.


## 2. Vibration System Modeling

The dynamic model of the vibration system is shown in Figure1. This system is composed of a motor and vibration environment. The motor has an eccentric rotor that rotates anti-clockwise. The vibration environment is the vibration field that changes periodically in x-direction. Assuming that there is a vibrating environment which exerts a vibration in the x-direction with Vx = −ω2Acosωt, a rotor with an eccentric mass of m, an eccentric radius of r, and rotational inertia of J rotates anti-clockwise around point O. Point O satisfies the law of vibration motion with amplitude A.Figure 1
Dynamic model of the vibration system with electrically driven eccentric rotor in the vibration environment.The equation of motion for a vibrating environment is given by(1)x=Acosφ,x′=−ωAsinφ,x″=−ω2Acosφ,where x, x′, and x″ are the displacement, velocity, and acceleration of the vibrating environment, respectively, φ is the angular displacement of the vibrating environment, ω is the rotating angular frequency of the vibrating environment, and A is the amplitude of the vibrating environment.


### 2.1. Dynamic Equations of the Vibration System

Through the force analysis of the vibration system, the torque balance equation of the motor with eccentric rotor rotating in vibrating environment is obtained as follows:(2)TJ+Tf+Td=TM+Tz.The dynamic equation of the eccentric rotor can be obtained as follows:(3)TJ+Tf+Td=TM−12mrω2Asinθ+φ+sinθ−φ,where TJ=Jθ″ is the inertia torque of the eccentric rotor; Tf is the moment of inertia of the vibration system; Td is the fan load of the excited motor; TM is the electromagnetic torque of the motor; Tz=mrx″sinθ=−mrω2Acosφsinθ is the vibration torque; and θ is the angular displacement of the eccentric rotor.


### 2.2. Differential Equations for the Relative Motion of the Vibration System

Since there is a rotational motion of the motor and the vibration of the vibration environment in a vibrating system, there is an interaction between the two motions, and this paper uses the vibration of the vibrating environment as a benchmark. Therefore, the mutual motion is studied within one cycle of the vibrating environment.When the electrically driven eccentric rotor is captured by the same frequency of the vibration environment, the following conclusions can be drawn.Assumption 1.
The angular velocity of the eccentric rotorθ′ is captured by the angular frequency of the vibrating environment ω, θ′=ω.Assumption 2.
The difference between the angular displacement of the eccentric rotorθ and the angular displacement of the vibration φ is Δα, ω/2π∫tt+2π/ωθ−φdt=Δα, where Δα is a constant and can be converted to the range of 0,2π.Assumption 3.
The angular velocity of the eccentric rotorθ′ and the angular velocity of the vibrating environment ω are equal in the integration period t,t+2π/ω, ω/2π∫tt+2π/ωθ′−φ′dt=0.
The small parameter integral mean variable of the angular displacement difference between the eccentric rotor and the vibrating environment is expressed as follows:(4)ε¯t=ω2π∫tt+2π/ωθ−φdt−Δα,and then(5)ε¯′t=ω2π∫tt+2π/ωθ′−φ′dt,(6)ε¯″t=ω2π∫tt+2π/ωθ″dt.
When the vibration system is in stable synchronization,ω/2π∫tt+2π/ωε¯tdt=0, ε¯t≪1.
At the torque balance point, we have(7)TM≈TM0+CMθ′−ω,Td≈Td0+mfdrωθ′−ω,Tf≈Tf0+fθ′−ω,and then(8)CM=2πdTMdθ′|ω,Tf0=fω,Td0=12mrfdω2,where CM is the mechanical characteristic slope when the electrically driven eccentric rotor is captured by the vibration environment, TM0 is the electromagnetic torque when the electrically driven eccentric rotor is captured by the vibration environment, Td0 is the fan load when the electrically driven eccentric rotor is captured by the vibration environment, Tf0 is the friction torque when the eccentric rotor is captured by the vibration environment, f is the friction coefficient of the vibration system, and d is the equivalent diameter of the fan load of the motor.
This paper usesε¯t as a variable and integrates equation (3) in t,t+2π/ω; we get(9)ε¯″t+f+mfdrω−CMJε¯′t+Tf0+Td0−TM0J+mrω2A2Jω2π∫tt+2π/ωsinθ+φdt+ω2π∫tt+2π/ωsinθ−φdt=0.
This section uses the torque balance equation to get the dynamic equation. Then, the dynamic differential equation is obtained by the differential mean method with small parameter periodic coefficients. Finally, a mathematical model of a single excited motor in a vibration environment is established, which provides a basis for the derivation of the synchronization and stability criterion of the vibration system.


## 2.1. Dynamic Equations of the Vibration System

Through the force analysis of the vibration system, the torque balance equation of the motor with eccentric rotor rotating in vibrating environment is obtained as follows:(2)TJ+Tf+Td=TM+Tz.The dynamic equation of the eccentric rotor can be obtained as follows:(3)TJ+Tf+Td=TM−12mrω2Asinθ+φ+sinθ−φ,where TJ=Jθ″ is the inertia torque of the eccentric rotor; Tf is the moment of inertia of the vibration system; Td is the fan load of the excited motor; TM is the electromagnetic torque of the motor; Tz=mrx″sinθ=−mrω2Acosφsinθ is the vibration torque; and θ is the angular displacement of the eccentric rotor.


## 2.2. Differential Equations for the Relative Motion of the Vibration System

Since there is a rotational motion of the motor and the vibration of the vibration environment in a vibrating system, there is an interaction between the two motions, and this paper uses the vibration of the vibrating environment as a benchmark. Therefore, the mutual motion is studied within one cycle of the vibrating environment.When the electrically driven eccentric rotor is captured by the same frequency of the vibration environment, the following conclusions can be drawn.Assumption 1.
The angular velocity of the eccentric rotorθ′ is captured by the angular frequency of the vibrating environment ω, θ′=ω.Assumption 2.
The difference between the angular displacement of the eccentric rotorθ and the angular displacement of the vibration φ is Δα, ω/2π∫tt+2π/ωθ−φdt=Δα, where Δα is a constant and can be converted to the range of 0,2π.Assumption 3.
The angular velocity of the eccentric rotorθ′ and the angular velocity of the vibrating environment ω are equal in the integration period t,t+2π/ω, ω/2π∫tt+2π/ωθ′−φ′dt=0.
The small parameter integral mean variable of the angular displacement difference between the eccentric rotor and the vibrating environment is expressed as follows:(4)ε¯t=ω2π∫tt+2π/ωθ−φdt−Δα,and then(5)ε¯′t=ω2π∫tt+2π/ωθ′−φ′dt,(6)ε¯″t=ω2π∫tt+2π/ωθ″dt.
When the vibration system is in stable synchronization,ω/2π∫tt+2π/ωε¯tdt=0, ε¯t≪1.
At the torque balance point, we have(7)TM≈TM0+CMθ′−ω,Td≈Td0+mfdrωθ′−ω,Tf≈Tf0+fθ′−ω,and then(8)CM=2πdTMdθ′|ω,Tf0=fω,Td0=12mrfdω2,where CM is the mechanical characteristic slope when the electrically driven eccentric rotor is captured by the vibration environment, TM0 is the electromagnetic torque when the electrically driven eccentric rotor is captured by the vibration environment, Td0 is the fan load when the electrically driven eccentric rotor is captured by the vibration environment, Tf0 is the friction torque when the eccentric rotor is captured by the vibration environment, f is the friction coefficient of the vibration system, and d is the equivalent diameter of the fan load of the motor.
This paper usesε¯t as a variable and integrates equation (3) in t,t+2π/ω; we get(9)ε¯″t+f+mfdrω−CMJε¯′t+Tf0+Td0−TM0J+mrω2A2Jω2π∫tt+2π/ωsinθ+φdt+ω2π∫tt+2π/ωsinθ−φdt=0.
This section uses the torque balance equation to get the dynamic equation. Then, the dynamic differential equation is obtained by the differential mean method with small parameter periodic coefficients. Finally, a mathematical model of a single excited motor in a vibration environment is established, which provides a basis for the derivation of the synchronization and stability criterion of the vibration system.


## 3. Synchronization Criterion and Stability Criterion of Vibration System

### 3.1. Linearization of the Equation

In this paper, we study the relationship betweenθ−φ=Δα, so we linearize the equation at this point.(1)
ω/2π∫tt+2π/ωsinθ−φdt of linearization.Expandingsinθ−φ at θ−φ=Δα by using Taylor formula and ignoring the higher term, it can be rewritten as(10)sinθ−φ=sinΔα+θ−φ−ΔαcosΔα.Integrating both sides of equation (10), we obtain(11)ω2π∫tt+2π/ωsinθ−φdt=ω2πcosΔα∫tt+2π/ωθ−φ−Δαdt+sinΔα.From equation (4),(12)ω2π∫tt+2π/ωθ−φ−Δαdt=ε¯t.Substituting equation (12) into equation (11), we can obtain(13)ω2π∫tt+2π/ωsinθ−φdt=sinΔα+ε¯tcosΔα.(2)
ω/2π∫tt+2π/ωsinθ+φdt of linearization.Expandingsinθ+φ at θ−φ=Δα by using Taylor formula and ignoring the higher term, it can be rewritten as(14)sinθ+φ=sinΔα+2φ+θ−φ−ΔαcosΔα+2φ.Integrating both sides of equation (14), we obtain(15)ω2π∫tt+2π/ωsinθ+φdt=12ωω2πθ−φ−ΔαsinΔα+2φ|tt+2π/ω−12ωω2π∫tt+2π/ωsinΔα+2φdθ−φ.From equation (5),(16)ω2πθ−φ−ΔαsinΔα+2φ|tt+2π/ω=ε¯′tsinΔα+2φ.Substituting equation (16) into equation (15), we can obtain(17)ω2π∫tt+2π/ωsinθ+φdt=12ωε¯′tsinΔα+2φ+12ω2ω2πθ′−ωcosΔα+2φ|tt+2π/ω−12ω2ω2π∫tt+2π/ωcosΔα+2φdθ′−φ′.From equation (6),(18)ω2πθ′−ωcosΔα+2φ|tt+2π/ω=ε¯″tcosΔα+2φ.Substituting equation (18) into equation (16), we can obtain(19)ω2π∫tt+2πωsinθ+φdt=12ωε¯′tsinΔα+2φ+12ω2ε¯″tcosΔα+2φ−12ω2ω2π∫tt+2πωcosΔα+2φdθ′−φ′.We can find thatω/2π∫tt+2π/ωsinθ+φdt is an infinite-order function of ε¯′t,ε¯″t,…… and ignoring the higher-order differential terms, we can obtain(20)ω2π∫tt+2π/ωsinθ+φdt≈12ωε¯′tsinΔα+2φ+12ω2ε¯″tcosΔα+2φ.The small parameter integral mean periodic coefficient differential equation of an eccentric rotor in vibration environment can be obtained as follows:(21)8J+mrAcosΔα+2φ8Jε¯″t+4f+mfdrω−CM+mrωAsinΔα+2φ4Jε¯′t+mrω2AcosΔα2Jε¯t+mrω2AsinΔα2J−TM0−Tf0−Td0J=0.Finally, we obtain differential equation (21), which makes it possible to better meet the synchronization and stability conditions.


### 3.2. Synchronization Criterion of Vibration System

When the eccentric rotor is synchronized with the vibration environment,(22)ε¯″t=ε¯′t=ε¯t=0.Substituting equation (22) into equation (21), we can obtain(23)−mrω2A2JsinΔα+TM0−Tf0−Td0J=0,and then(24)sinΔα=2TM0−Tf0−Td0mrω2A.The synchronization criterion can be obtained as follows:(25)2TM0−Tf0−Td0mrω2A<1.When the angular frequency of the vibration environment is less than the no-load angular velocity of motorω0, the motor is running in the electric working state.From equation (24),(26)TM0−Tf0−Td0>0sinΔα>0,T¯z0=mrω2A2sinΔα>0.The vibration torque is a motor load torque withT¯z0 as the average value. And the synchronization phase difference Δα can be located in the first or second quadrant.When the angular frequency of the vibration environment is greater than the no-load angular velocity of motorω0, the motor is running in the feedback state.(27)TM0−Tf0−Td0>0sinΔα>0,T¯z0=mrω2A2sinΔα>0.The vibration torque is an active torque withT¯z0 as the average value. The phase difference Δα can be located in the third or fourth quadrant.


### 3.3. Stability Criterion of Vibration System

The periodic coefficient differential equation of eccentric rotor frequency being captured by vibration environment can be transferred like this.(28)ε¯″t+8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φε¯′t+4mrω2AcosΔα8J+mrAcosΔα+2φε¯t=0.Equation (28) is a second-order periodic coefficient linear differential equation with a period of π/ω. According to the theory of second-order differential equations [21, 22], if equation (28) is to reach stable state, the two conditions must be met.(29)4mrω2A8J+mrAcosΔα+2φcosΔα>0,∫0π/ω8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φdt>0.Commonly, those conditions are stratified,J>mrA.From the first condition, we obtain(30)cosΔα>0.From the second condition, we obtain(31)∫0π/ω8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φdt=4πf+mfdrω−CMω64J2−m2r2A2>0.The stability criterion can be obtained as follows:(32)cosΔα>0.Remark 1.
The synchronization criterion and stability criterion can estimate the quadrant range of the synchronization phase differenceΔα.
When the angular frequency of the vibration environment is less than the no-load angular velocity of motorω0,(33)sinΔα>0,cosΔα>0.
The motor is running in the electric working state. The phase differenceΔα can be located in the first quadrant.
When the angular frequency of the vibration environment is greater than the no-load angular velocity of motorω0,(34)sinΔα<0,cosΔα>0.
The motor is running in the feedback state. The phase differenceΔα can be located in the fourth quadrant.


## 3.1. Linearization of the Equation

In this paper, we study the relationship betweenθ−φ=Δα, so we linearize the equation at this point.(1)
ω/2π∫tt+2π/ωsinθ−φdt of linearization.Expandingsinθ−φ at θ−φ=Δα by using Taylor formula and ignoring the higher term, it can be rewritten as(10)sinθ−φ=sinΔα+θ−φ−ΔαcosΔα.Integrating both sides of equation (10), we obtain(11)ω2π∫tt+2π/ωsinθ−φdt=ω2πcosΔα∫tt+2π/ωθ−φ−Δαdt+sinΔα.From equation (4),(12)ω2π∫tt+2π/ωθ−φ−Δαdt=ε¯t.Substituting equation (12) into equation (11), we can obtain(13)ω2π∫tt+2π/ωsinθ−φdt=sinΔα+ε¯tcosΔα.(2)
ω/2π∫tt+2π/ωsinθ+φdt of linearization.Expandingsinθ+φ at θ−φ=Δα by using Taylor formula and ignoring the higher term, it can be rewritten as(14)sinθ+φ=sinΔα+2φ+θ−φ−ΔαcosΔα+2φ.Integrating both sides of equation (14), we obtain(15)ω2π∫tt+2π/ωsinθ+φdt=12ωω2πθ−φ−ΔαsinΔα+2φ|tt+2π/ω−12ωω2π∫tt+2π/ωsinΔα+2φdθ−φ.From equation (5),(16)ω2πθ−φ−ΔαsinΔα+2φ|tt+2π/ω=ε¯′tsinΔα+2φ.Substituting equation (16) into equation (15), we can obtain(17)ω2π∫tt+2π/ωsinθ+φdt=12ωε¯′tsinΔα+2φ+12ω2ω2πθ′−ωcosΔα+2φ|tt+2π/ω−12ω2ω2π∫tt+2π/ωcosΔα+2φdθ′−φ′.From equation (6),(18)ω2πθ′−ωcosΔα+2φ|tt+2π/ω=ε¯″tcosΔα+2φ.Substituting equation (18) into equation (16), we can obtain(19)ω2π∫tt+2πωsinθ+φdt=12ωε¯′tsinΔα+2φ+12ω2ε¯″tcosΔα+2φ−12ω2ω2π∫tt+2πωcosΔα+2φdθ′−φ′.We can find thatω/2π∫tt+2π/ωsinθ+φdt is an infinite-order function of ε¯′t,ε¯″t,…… and ignoring the higher-order differential terms, we can obtain(20)ω2π∫tt+2π/ωsinθ+φdt≈12ωε¯′tsinΔα+2φ+12ω2ε¯″tcosΔα+2φ.The small parameter integral mean periodic coefficient differential equation of an eccentric rotor in vibration environment can be obtained as follows:(21)8J+mrAcosΔα+2φ8Jε¯″t+4f+mfdrω−CM+mrωAsinΔα+2φ4Jε¯′t+mrω2AcosΔα2Jε¯t+mrω2AsinΔα2J−TM0−Tf0−Td0J=0.Finally, we obtain differential equation (21), which makes it possible to better meet the synchronization and stability conditions.


## 3.2. Synchronization Criterion of Vibration System

When the eccentric rotor is synchronized with the vibration environment,(22)ε¯″t=ε¯′t=ε¯t=0.Substituting equation (22) into equation (21), we can obtain(23)−mrω2A2JsinΔα+TM0−Tf0−Td0J=0,and then(24)sinΔα=2TM0−Tf0−Td0mrω2A.The synchronization criterion can be obtained as follows:(25)2TM0−Tf0−Td0mrω2A<1.When the angular frequency of the vibration environment is less than the no-load angular velocity of motorω0, the motor is running in the electric working state.From equation (24),(26)TM0−Tf0−Td0>0sinΔα>0,T¯z0=mrω2A2sinΔα>0.The vibration torque is a motor load torque withT¯z0 as the average value. And the synchronization phase difference Δα can be located in the first or second quadrant.When the angular frequency of the vibration environment is greater than the no-load angular velocity of motorω0, the motor is running in the feedback state.(27)TM0−Tf0−Td0>0sinΔα>0,T¯z0=mrω2A2sinΔα>0.The vibration torque is an active torque withT¯z0 as the average value. The phase difference Δα can be located in the third or fourth quadrant.


## 3.3. Stability Criterion of Vibration System

The periodic coefficient differential equation of eccentric rotor frequency being captured by vibration environment can be transferred like this.(28)ε¯″t+8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φε¯′t+4mrω2AcosΔα8J+mrAcosΔα+2φε¯t=0.Equation (28) is a second-order periodic coefficient linear differential equation with a period of π/ω. According to the theory of second-order differential equations [21, 22], if equation (28) is to reach stable state, the two conditions must be met.(29)4mrω2A8J+mrAcosΔα+2φcosΔα>0,∫0π/ω8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φdt>0.Commonly, those conditions are stratified,J>mrA.From the first condition, we obtain(30)cosΔα>0.From the second condition, we obtain(31)∫0π/ω8f+mfdrω−CM+2mrωAsinΔα+2φ8J+mrAcosΔα+2φdt=4πf+mfdrω−CMω64J2−m2r2A2>0.The stability criterion can be obtained as follows:(32)cosΔα>0.Remark 1.
The synchronization criterion and stability criterion can estimate the quadrant range of the synchronization phase differenceΔα.
When the angular frequency of the vibration environment is less than the no-load angular velocity of motorω0,(33)sinΔα>0,cosΔα>0.
The motor is running in the electric working state. The phase differenceΔα can be located in the first quadrant.
When the angular frequency of the vibration environment is greater than the no-load angular velocity of motorω0,(34)sinΔα<0,cosΔα>0.
The motor is running in the feedback state. The phase differenceΔα can be located in the fourth quadrant.


## 4. Simulation Results and Discussion

In this section, some quantitative analyses are given to illustrate the effectiveness of the aforementioned theoretical results.


### 4.1. Setting Parameters

The motor model is established based on the practical expression of the mechanical characteristics of the asynchronous motor. The model parameters are listed in Table1.Table 1
Parameters of the vibration system.
ParametersValueMaximum torque of motorTM (N⋅m)50Maximum slip of motorSM0.05No-load angular velocity of exciterω0 (rad/s)25πAmplitude of simple harmonicA (m)0.003Rotation radius of eccentric rotorr (m)0.2Mass of eccentric rotorm (kg)10Load equivalent diameter of motor fand (m)0.1Coefficient of frictionf0.002Moment of inertia of eccentric rotorJ (kg⋅m2)0.02Simulation timeT (s)100


### 4.2. Simulation and Analysis

Based on the established mathematical model, a simulation model is established in MATLAB/Simulink.Simulation 1: the angular velocity isω=24.9πrad/s.Whenω=24.9πrad/s, we get slip rate s=0.004, TM0=7.949, Tf0=fω≈0.156, Td0=mrω2fd/2≈0.612, and mrω2A=18.358; substituting the above values into the synchronization criterion, we obtain(35)2TM0−Tf0−Td0mrω2A≈0.782<1.The above values satisfy the criterion of synchronization, and the phase difference is in the first quadrant. The simulation results are shown in Figure2.The motor is in electric working state, and the synchronization phase differenceΔα≈−80.791rad (approximately 51.02° in the range of 360°) is in the first quadrant.Simulation 2: the angular velocity isω=25.1πrad/s.Whenω=25.1πrad/s, we get slip rate s=−0.004, TM0=−7.949, Tf0=fω≈0.158, Td0=mrω2fd/2≈0.622, and mrω2A=18.654; substituting the above values into the synchronization criterion, we obtain(36)2TM0−Tf0−Td0mrω2A≈0.935<1.The above values satisfy the criterion of synchronization, and the phase difference is in the fourth quadrant. The simulation results are shown in Figure3.The motor is in the feedback state, and the synchronization phase differenceΔα≈−89.164rad (approximately 291.28° in the range of 360°) is in the fourth quadrant.Simulation 3: the angular velocity isω=24.9πrad/s and amplitude isA=0.002m.Whenω=24.9πrad/s, we get slip rate s=0.004, TM0=7.949, Tf0=fω≈0.156, Td0=mrω2fd/2≈0.612, and mrω2A=12.239; substituting the above values into the synchronization criterion, we obtain(37)2TM0−Tf0−Td0mrω2A≈1.17>1.The above values do not satisfy the criterion of synchronization. The simulation results are shown in Figure4.Figure 2
Simulation curve whenω = 24.9π. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)Figure 3
Simulation curve whenω = 25.1π. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)Figure 4
Simulation curve whenω = 24.9π and A = 0.002 m. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)


## 4.1. Setting Parameters

The motor model is established based on the practical expression of the mechanical characteristics of the asynchronous motor. The model parameters are listed in Table1.Table 1
Parameters of the vibration system.
ParametersValueMaximum torque of motorTM (N⋅m)50Maximum slip of motorSM0.05No-load angular velocity of exciterω0 (rad/s)25πAmplitude of simple harmonicA (m)0.003Rotation radius of eccentric rotorr (m)0.2Mass of eccentric rotorm (kg)10Load equivalent diameter of motor fand (m)0.1Coefficient of frictionf0.002Moment of inertia of eccentric rotorJ (kg⋅m2)0.02Simulation timeT (s)100


## 4.2. Simulation and Analysis

Based on the established mathematical model, a simulation model is established in MATLAB/Simulink.Simulation 1: the angular velocity isω=24.9πrad/s.Whenω=24.9πrad/s, we get slip rate s=0.004, TM0=7.949, Tf0=fω≈0.156, Td0=mrω2fd/2≈0.612, and mrω2A=18.358; substituting the above values into the synchronization criterion, we obtain(35)2TM0−Tf0−Td0mrω2A≈0.782<1.The above values satisfy the criterion of synchronization, and the phase difference is in the first quadrant. The simulation results are shown in Figure2.The motor is in electric working state, and the synchronization phase differenceΔα≈−80.791rad (approximately 51.02° in the range of 360°) is in the first quadrant.Simulation 2: the angular velocity isω=25.1πrad/s.Whenω=25.1πrad/s, we get slip rate s=−0.004, TM0=−7.949, Tf0=fω≈0.158, Td0=mrω2fd/2≈0.622, and mrω2A=18.654; substituting the above values into the synchronization criterion, we obtain(36)2TM0−Tf0−Td0mrω2A≈0.935<1.The above values satisfy the criterion of synchronization, and the phase difference is in the fourth quadrant. The simulation results are shown in Figure3.The motor is in the feedback state, and the synchronization phase differenceΔα≈−89.164rad (approximately 291.28° in the range of 360°) is in the fourth quadrant.Simulation 3: the angular velocity isω=24.9πrad/s and amplitude isA=0.002m.Whenω=24.9πrad/s, we get slip rate s=0.004, TM0=7.949, Tf0=fω≈0.156, Td0=mrω2fd/2≈0.612, and mrω2A=12.239; substituting the above values into the synchronization criterion, we obtain(37)2TM0−Tf0−Td0mrω2A≈1.17>1.The above values do not satisfy the criterion of synchronization. The simulation results are shown in Figure4.Figure 2
Simulation curve whenω = 24.9π. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)Figure 3
Simulation curve whenω = 25.1π. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)Figure 4
Simulation curve whenω = 24.9π and A = 0.002 m. (a) ε′t graph. (b) εt+Δα graph.
(a)(b)


## 5. Conclusions and Discussion

### 5.1. Main Conclusions

In this paper, a new method for vibration synchronization research using small parameter integral mean periodic coefficient differential equation is proposed. The system is transformed into a second-order periodic coefficient differential equation so that the related theories of the second-order periodic coefficient differential equation can be used for synchronization and stability analysis.The synchronization criterion and stability criterion of the vibration of the electrically driven eccentric rotor in a vibrating environment are obtained. The combination of the two criteria determines the stable phase of the electrically driven eccentric rotor in the vibrating environment. The idea of synchronization between the eccentric rotor and the vibration environment proposed in this paper provides a new way to study vibration synchronization. The method of differential equations with small parameter mean and variable periodic coefficients provides a new method for studying vibration synchronization.


### 5.2. Discussion

Since the periodic coefficient differential equation based on small parameter integral mean variable is used to research on vibration synchronization theory, the problem of vibration synchronization is transformed into a second-order periodic coefficient differential equation. In essence, it is still the basic idea of the averaging method, which also makes the influence of the moment of inertia not be reflected in the stability criterion. The authors will further carry out related research.


## 5.1. Main Conclusions

In this paper, a new method for vibration synchronization research using small parameter integral mean periodic coefficient differential equation is proposed. The system is transformed into a second-order periodic coefficient differential equation so that the related theories of the second-order periodic coefficient differential equation can be used for synchronization and stability analysis.The synchronization criterion and stability criterion of the vibration of the electrically driven eccentric rotor in a vibrating environment are obtained. The combination of the two criteria determines the stable phase of the electrically driven eccentric rotor in the vibrating environment. The idea of synchronization between the eccentric rotor and the vibration environment proposed in this paper provides a new way to study vibration synchronization. The method of differential equations with small parameter mean and variable periodic coefficients provides a new method for studying vibration synchronization.


## 5.2. Discussion

Since the periodic coefficient differential equation based on small parameter integral mean variable is used to research on vibration synchronization theory, the problem of vibration synchronization is transformed into a second-order periodic coefficient differential equation. In essence, it is still the basic idea of the averaging method, which also makes the influence of the moment of inertia not be reflected in the stability criterion. The authors will further carry out related research.



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*Source: 8892919-2021-01-20.xml*