# Vibration Characteristics of Rolling Mill System under Constraints of the Nonlinear Spring Force and Friction Force from Hydraulic Cylinder

Authors: Zhaolun Liu; Guixiang Pan; Jiahao Jiang; Bin Liu
Journal: Shock and Vibration
 (2021)

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## Abstract

Considering the two kinds of nonlinear constraints of rolling mill hydraulic cylinder, spring force and friction force, the vibration model of rolling mill system is established. The amplitude frequency response equations are obtained by using the average method. Comparing the time history curves of vertical vibration displacement of rolling mill system under the nonlinear spring force and friction force, the amplitude frequency characteristic curves are simulated. The external excitation amplitude is viewed as the bifurcation parameter, and the system bifurcation response changing with the external excitation amplitude is analyzed. The influence of the external excitation amplitude on the system stability is studied. The results indicate that the increase of the nonlinear spring force makes the rolling mill system’s unstable area to become wider, and the influence on the rolling mill system of nonlinear friction force behaves as the damping characteristics; the vibration of rolling mill system is alternating between the periodic, period-doubling, and the chaotic motion. The research results provide a theoretical support for restraining the vibration of the rolling mill system in the actual production process.


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## Body

## 1. Introduction

With the rapid development of science and technology, strip rolling mill in the field of heavy industrial machinery plays an increasingly important role [1]. However, the vibration of rolling mill not only limits the rolling speed, but impacts the accuracy. It affects the quality of rolling products and hazards the safety of mill production [2–4].The research on vibration of plate and strip rolling mill has lasted for nearly half a century, and scholars have studied it from different angles [5–7]. Yarita et al. constructed a simple mass-spring-damper vibration system and provided a method to estimate the spring constants and damping coefficients of the system [8]. Sun et al. studied the influence of the tension factor on the nonlinear vibration of the rolling mill [9]. The stability of the rolling mill vibration system was analyzed by changing the external excitation frequency. They found that the rolling speed and the thickness of the strip have great influence on the stability of the system. Yun et al. developed a suitable model to study the vibration of mill system. This model reflected the dynamic relationship among the rolling parameters. They announced that the self-excited vibration occurring in rolling process is the consequence of the interaction between the structural dynamics of mill stand and the dynamics of the rolling process itself [10]. Yang et al. took into account the interaction between the roller and the rolled piece and established a vertical vibration model of roll system based on the dynamic friction equation of roll gap [11]. The vertical vibration mechanism of cold rolling mill is studied under the influence of the dynamic friction mechanism between the workpiece and roll. Fan et al. introduced the Duffing oscillator and the parameters of the excitation system and established the roll system vertical vibration model [12]. The bifurcation characteristics of the rolling mill system amplitude in the nonlinear parameter variation are analyzed by the simulation. Bayón et al. considered the nonlinear friction coefficient and nonlinear equivalent stiffness of hydraulic cylinder are caused by the change of velocity and dynamic load [13]. The dynamic characteristics of the hydraulic system are also analyzed by controlling the electric motor speed [14]. The results show that the rotation angle of the base plate gradually becomes more negative during the open-loop control because of the difference in the area of the hydraulic cylinder. The above researches were from the background of rolling mill structure and rolling process. The rolling mill hydraulic cylinder is a typical nonlinear component in the rolling mill system, and the influence of nonlinear constraints on the vibration behavior of the rolling mill system cannot be ignored. The coefficient of friction between the cylinder and the piston will change due to the periodic change of the vibration velocity of the hydraulic cylinder, and the friction exhibits nonlinear. In the running process of the hydraulic cylinder system, under the action of the oil source pressure and the load pressure, the dynamic hydraulic spring can be formed due to the compressibility of the oil [15]. The nonlinearity of the spring force makes the natural frequency of the system unstable, and the stability of the response area becomes complicated [16]. The spring force will cause the nonlinear vibration of the hydraulic system under certain conditions. Zhang et al. analyzed the transverse nonlinear vibrations of a rotating flexible disk subjected to a rotating point force with a periodically varying rotating speed. The dynamics of the cantilevered shell-shaped workpiece was studied under time-delay effects, parametric excitation, and forcing excitation [17, 18]. Zhou et al. investigated the nonlinear dynamics of a thin-plate workpiece during milling process with cutting force nonlinearities [19]. Numerical methods are used to find the periodic and chaotic oscillations of the cantilevered thin-plate workpiece. Andrea et al. proposed an innovative controlled hydraulic pump solution to drastically improve the efficiency and to reduce the overall encumbrances, maintaining very high performance in terms of dynamical behavior and corresponding frequency response [20]. Valigi et al. presented a numerical model combining Orowan theory to predict the working parameters of full film lubrication cold rolling process. Using it, we can forecast the thickness reduction of the metal sheet and the pressure trend, and the rolling mill process parameters can be regulated to obtain a specific output thickness [21]. It is significant to establish a more practical vibration model of rolling mill system for the analysis of roll system vibration.In this paper, the rolling mill system with nonlinear spring force and friction force constraints is studied. Considering the nonlinear factors such as spring force and friction force of hydraulic cylinder, the vibration model of rolling mill system is established based on the two kinds of nonlinear constraint. The influence of nonlinear spring force, friction force, and the initial displacement of piston rod on the vibration behavior of rolling mill system and the bifurcation characteristics under the action of external excitation amplitude are studied.


## 2. Vibration Model of Rolling Mill System

### 2.1. Vibration Model of Rolling Mill System under Nonlinear Constraints

Based on the production line of Hebei Iron and Steel Group Chengde branch, the data of all the simulation experiments are derived from the structural parameters of the 1780 rolling mill and the parameters of the rolling process. Figure1 is the four-roller mill physical map, in which 1 is the hydraulic cylinder, 2 is the frame, 3 is the upper supporting roll, 4 is the upper work roll, 5 is the lower work roll, and 6 is the lower supporting roll.Figure 1
The four-roller mill physical map.According to the viewpoint of nonlinear dynamics, the effect of nonlinear spring force and friction force those from hydraulic cylinder on the vibration of rolling mill system is studied [22]. In order to simplify the research, taking into account the symmetry of the structure of the four-roller mill, only the upper roll of rolling mill system is analyzed. The vibration model of rolling mill system with nonlinear spring force and friction force constraints is established, and the diagram is shown in Figure 2.Figure 2
The vibration model of the rolling mill system.Based on the generalized Lagrange principle, the dynamic equation of rolling mill system can be expressed as [23](1)mx¨+cx˙+kx+αk1x+k3x3+βc0−c1x˙+c3x˙3=Fcosωt,where m indicates the equivalent mass of the upper supporting roller, the upper working roller, and the bearing seat of the four-roller mill. c is the equivalent damping system of the rolling mill. k is the equivalent stiffness of the rolling mill system. x is the displacement of the piston rod. F is equivalent to the load force. In order to study the influence of different nonlinear constraints on the roll system vibration behavior, the nonlinear spring force and friction force constraints of the equation are known as the coefficients α and β.


### 2.2. Nonlinear Spring Force

The hydraulic spring stiffness is the nonlinear spring stiffness of the liquid, which is formed when the volume of the fluid is compressed by the external force, when the hydraulic cylinder working chamber is completely closed. In this paper, the double-acting single-piston hydraulic cylinder used in rolling mill industry is analyzed. The spring stiffness of the rolling mill hydraulic cylinder is composed of the hydraulic oil stiffness and the stiffness of the piston rod. The bulk modulus of the piston rod is nearly 100 times that of the bulk modulus of hydraulic oil, so it is regarded as a rigid body. So the spring stiffness of the hydraulic cylinder system of the rolling mill is produced by the spring stiffness of the hydraulic oil [24]. The oil in the two cavities is always under pressure and in compression state, so the total hydraulic spring stiffness of the hydraulic cylinder can be equivalent to the parallel of the hydraulic spring stiffness of the two cavities [25].(2)kx=βeA12V1+βeA22V1=βeA12A1L1+x+Vl1+βeA22A2L−L1−x+Vl2,where βe is the volume elastic modulus of hydraulic cylinder oil, A1A2 is the hydraulic cylinder without (with) the effective area of the piston side of the rod cavity, L is the total stroke of the hydraulic cylinder, L1 is the initial position of the piston rod, Vl1Vl2 is the oil volume in the tubing between the inlet valve and the rodless (rod) chamber, and Vl1Vl2 has the small relative to the two oil chamber.The vibration displacement of the spring stiffness formula at the working point isx. At the origin, when x=0, the Taylor series can be expressed as(3)kx=k0+k˙0x+k¨02!x2+οx2.Makek0=k1, k˙0=k2, and k¨0/2!=k3; then(4)kx=k1+k2x+k3x2+οx2.Nonlinear spring force can be expressed as(5)kx=k0+k˙0x+k¨02!x2+οx2.Because the elastic potential energy of spring is symmetrical,U can be expressed as(6)U=12k1x2+14k3x4.The type (6) derivation, the spring force of the hydraulic cylinder, can be expressed as(7)Fsx=dUdx=k1x+k3x3.


### 2.3. Nonlinear Friction Force

In the hydraulic cylinder, friction occurs between the piston rod and the cylinder wall in order to achieve the transfer of energy. When it works, it shows the strong nonlinear effect, which can cause the rolling mill system to produce the flutter phenomenon, which makes the rolling mill system to produce the nonlinear vibration [24]. Therefore, the influence of the friction force on the dynamic characteristics of rolling mill system cannot be ignored. The friction coefficient between the rolling mill hydraulic cylinder piston rod and the cylinder wall is an expression related to speed [26]. Therefore, the friction coefficient can be expressed as(8)μ=μssgnx˙−λ1x˙+λ2x˙3,where λ1=3μs−μm/2νm and λ2=μs−μm/2νm3, where μs is the static friction coefficient, μm is the maximum dynamic friction factor, and νm is the vibration velocity when the friction coefficient is μm.The friction force of the hydraulic cylinder of the rolling mill can be expressed as(9)Ffx˙=p×μ=pμssgnx˙−λ1x˙+λ2x˙3=c0−c1x˙+c3x˙3,where p is the pressure between the piston rod and the cylinder wall, and p depends on the material of the rolling mill hydraulic cylinder, the hardness of the sealing material, and the radial component of the load where c0=p×μssgnx˙, c1=p×λ1, and c3=p×λ2. Fsx and Ffx˙ are the foundation of the vibration model of the rolling mill system.


## 2.1. Vibration Model of Rolling Mill System under Nonlinear Constraints

Based on the production line of Hebei Iron and Steel Group Chengde branch, the data of all the simulation experiments are derived from the structural parameters of the 1780 rolling mill and the parameters of the rolling process. Figure1 is the four-roller mill physical map, in which 1 is the hydraulic cylinder, 2 is the frame, 3 is the upper supporting roll, 4 is the upper work roll, 5 is the lower work roll, and 6 is the lower supporting roll.Figure 1
The four-roller mill physical map.According to the viewpoint of nonlinear dynamics, the effect of nonlinear spring force and friction force those from hydraulic cylinder on the vibration of rolling mill system is studied [22]. In order to simplify the research, taking into account the symmetry of the structure of the four-roller mill, only the upper roll of rolling mill system is analyzed. The vibration model of rolling mill system with nonlinear spring force and friction force constraints is established, and the diagram is shown in Figure 2.Figure 2
The vibration model of the rolling mill system.Based on the generalized Lagrange principle, the dynamic equation of rolling mill system can be expressed as [23](1)mx¨+cx˙+kx+αk1x+k3x3+βc0−c1x˙+c3x˙3=Fcosωt,where m indicates the equivalent mass of the upper supporting roller, the upper working roller, and the bearing seat of the four-roller mill. c is the equivalent damping system of the rolling mill. k is the equivalent stiffness of the rolling mill system. x is the displacement of the piston rod. F is equivalent to the load force. In order to study the influence of different nonlinear constraints on the roll system vibration behavior, the nonlinear spring force and friction force constraints of the equation are known as the coefficients α and β.


## 2.2. Nonlinear Spring Force

The hydraulic spring stiffness is the nonlinear spring stiffness of the liquid, which is formed when the volume of the fluid is compressed by the external force, when the hydraulic cylinder working chamber is completely closed. In this paper, the double-acting single-piston hydraulic cylinder used in rolling mill industry is analyzed. The spring stiffness of the rolling mill hydraulic cylinder is composed of the hydraulic oil stiffness and the stiffness of the piston rod. The bulk modulus of the piston rod is nearly 100 times that of the bulk modulus of hydraulic oil, so it is regarded as a rigid body. So the spring stiffness of the hydraulic cylinder system of the rolling mill is produced by the spring stiffness of the hydraulic oil [24]. The oil in the two cavities is always under pressure and in compression state, so the total hydraulic spring stiffness of the hydraulic cylinder can be equivalent to the parallel of the hydraulic spring stiffness of the two cavities [25].(2)kx=βeA12V1+βeA22V1=βeA12A1L1+x+Vl1+βeA22A2L−L1−x+Vl2,where βe is the volume elastic modulus of hydraulic cylinder oil, A1A2 is the hydraulic cylinder without (with) the effective area of the piston side of the rod cavity, L is the total stroke of the hydraulic cylinder, L1 is the initial position of the piston rod, Vl1Vl2 is the oil volume in the tubing between the inlet valve and the rodless (rod) chamber, and Vl1Vl2 has the small relative to the two oil chamber.The vibration displacement of the spring stiffness formula at the working point isx. At the origin, when x=0, the Taylor series can be expressed as(3)kx=k0+k˙0x+k¨02!x2+οx2.Makek0=k1, k˙0=k2, and k¨0/2!=k3; then(4)kx=k1+k2x+k3x2+οx2.Nonlinear spring force can be expressed as(5)kx=k0+k˙0x+k¨02!x2+οx2.Because the elastic potential energy of spring is symmetrical,U can be expressed as(6)U=12k1x2+14k3x4.The type (6) derivation, the spring force of the hydraulic cylinder, can be expressed as(7)Fsx=dUdx=k1x+k3x3.


## 2.3. Nonlinear Friction Force

In the hydraulic cylinder, friction occurs between the piston rod and the cylinder wall in order to achieve the transfer of energy. When it works, it shows the strong nonlinear effect, which can cause the rolling mill system to produce the flutter phenomenon, which makes the rolling mill system to produce the nonlinear vibration [24]. Therefore, the influence of the friction force on the dynamic characteristics of rolling mill system cannot be ignored. The friction coefficient between the rolling mill hydraulic cylinder piston rod and the cylinder wall is an expression related to speed [26]. Therefore, the friction coefficient can be expressed as(8)μ=μssgnx˙−λ1x˙+λ2x˙3,where λ1=3μs−μm/2νm and λ2=μs−μm/2νm3, where μs is the static friction coefficient, μm is the maximum dynamic friction factor, and νm is the vibration velocity when the friction coefficient is μm.The friction force of the hydraulic cylinder of the rolling mill can be expressed as(9)Ffx˙=p×μ=pμssgnx˙−λ1x˙+λ2x˙3=c0−c1x˙+c3x˙3,where p is the pressure between the piston rod and the cylinder wall, and p depends on the material of the rolling mill hydraulic cylinder, the hardness of the sealing material, and the radial component of the load where c0=p×μssgnx˙, c1=p×λ1, and c3=p×λ2. Fsx and Ffx˙ are the foundation of the vibration model of the rolling mill system.


## 3. Rolling Mill System Response

In order to facilitate the calculation, the kinetic equation (11) can be simplified as(10)x¨+2ξω0x˙+ω02x+αρ1x+γ1x3+ρ2x+γ2x3+βc1∗x˙+c3∗x˙3=F∗cosωt,where ξ=c/2mω0, ω0=k/m, ρ1=βeA1/mL1, ρ2=βeA2/mL−L1, γ1=βeA1/mL13, γ2=βeA2/mL−L13, c1∗=−c1/m, c3∗=c3/m, F∗=F/m, and c0/m⟶0.Taking into account the primary resonance with the external excitation, makeω2=ω021+εσ, and then(11)x¨+ω2x=εfx,x˙,where ε is the nonlinear term coefficient and σ is the frequency tuning factor:(12)fx,x˙=F∗cosωt+εσω02x−2ξω0x˙−αρ1x+γ1x3+ρ2x+γ2x3−βc1∗x˙+c3∗x˙3.Whenε=0, the derived system of equation (11) is a linear conservative system, and the solution of the derived system and its derivative can be expressed as(13)x=acosω0t−θ,x˙=−aω0sinω0t−θ.By substituting equation (13) into equation (11), the following expression can be obtained:(14)a˙=−εω0fx,x˙sinϕ,θ˙=εω0afx,x˙cosϕ,where ϕ=ωt−θ. When the parameter ε is sufficiently small, a and θ are slowly varying functions near the constant. The right term of equation (11) is approximately replaced by the average value of one cycle of ϕ, and it is also believed that a and θ remain unchanged in one cycle of ϕ. Thus the equation obtained is called the mean equation of the original equation:(15)a˙=−ε2ω0Qa,θ,θ˙=ε2ω0aPa,θ,where Qa,θ and Pa,θ can be expressed as(16)Qa,θ=1π∫02πfx,x˙sinϕdϕ,Pa,θ=1π∫02πfx,x˙cosϕdϕ.By substituting equation (12) into equation (16), the following expression can be obtained:(17)Qa,θ=F∗sinθ+2ξω02a+βc1∗aω0+0.75c3∗a3ω03,Pa,θ=F∗cosθ+εσω02a−αρ1a+0.75γ1a3+ρ2a+0.75γ2a3.By substituting equation (17) into equation (15), the following expression can be obtained:(18)a˙=−ε2ω0−F∗sinθ+2ξω02a+βc1∗aω0+0.75βc3∗a3ω03,θ˙=ε2ω0aF∗cosθ+εσω02a−αρ1a−0.75αγ1a3−αρ2a−0.75αγ2a3.Whena˙=0, θ˙=0, after eliminating θ in equation (18), the amplitude frequency equation of the system can be obtained:(19)2ξω02a+βc1∗aω0+0.75βc3∗a3ω032+εσω02a−αρ1a−0.75αγ1a3−αρ2a−0.75αγ2a32=F∗2.Equation (19) is the amplitude frequency characteristic equation of rolling mill system, which is the basis of research on the vibration behavior of rolling mill system with nonlinear spring force and friction force constraints. The average method is used to solve the rolling mill roll system vibration system under the nonlinear constraint of the hydraulic cylinder, and the dynamic amplitude frequency response equation of the vibration system is obtained.


## 4. Vibration Characteristics of Rolling Mill System

Taking the parameters of the 1780 strip rolling mill in a certain factory as an example, the vertical vibration model of the roller system under the nonlinear action of the hydraulic cylinder is solved by using the actual parameters of the rolling mill. Based on the actual numerical experiments, the effects of the nonlinear spring force and the nonlinear friction force on the dynamic characteristics of the rolling mill system are studied. The parameters in the system model are shown in Table1.Table 1
Vibration parameters of rolling mill system.
ParametersValuesMass of up rolls (m)1.44×105 kgStiffness of up rolls (k)2.35×1010 N/mDamping of up rolls (c)2.54×106 N·s/mTotal stroke of hydraulic cylinder (L)0.11 mPiston side area (A1)0.6361 m2Piston side area (A2)0.3243m2Pressure (p)0.04 MNOil elastic modulus (βe)1.6×109 PaAmplitude of external excitation (F0)0.6 MNNonlinear term coefficient (ε)0.01Maximum dynamic friction factor (μm)0.01Static friction coefficient (μs)0.02Vibration velocity (vm)0.01 m/s


### 4.1. Time-Domain Characteristics

The vibration of rolling mill system is influenced by the nonlinear spring force and nonlinear friction force of the hydraulic cylinder of rolling mill. By taking different nonlinear spring force and friction coefficient, the variation law of time-domain response is simulated and analyzed. The simulation results are shown in Figures3–5.Figure 3
The vertical vibration curve of rolling mill system.
(a)(b)(c)Figure 4
Amplitude frequency characteristics of different initial displacement.Figure 5
The influence of nonlinear friction coefficient on amplitude frequency characteristic curve.As is shown in Figures3(a) and 3(b), with the increase of nonlinear friction, the peaks and troughs of the vertical vibration curve of the rolling mill system showed irregular vibration. It can be seen from Figures 3(b) and 3(c) that when the nonlinear spring force is increased, the vibration curve of rolling mill system has various irregular vibration. With the increase of the nonlinear binding force, the more irregular vibration of the milling mill system occurred, and this affects the stability of the system. From Figure 3(a) to Figure 3(c), when the nonlinear friction force is increased, the amplitude of the vibration displacement has no obvious change, but the amplitude of the vibration displacement is greatly reduced when the nonlinear spring force is increased. The above conclusions provide data support for the manufacture of rolling mill hydraulic cylinder. It is helpful to improve the stability of the rolling mill by selecting the appropriate nonlinear spring stiffness coefficient and friction coefficient.


### 4.2. Frequency-Domain Characteristics

The influence of different rolling parameters on the vibration of rolling mill system is studied. By using the actual parameters listed in Table1, the amplitude frequency characteristics of the system are simulated, and then the influence of the initial displacement of the piston rod, the nonlinear friction force, and the nonlinear spring force on the rolling mill system vibration are analyzed.Figure4 shows the different amplitude frequency characteristic curves of hydraulic cylinder piston rod under different initial displacement. The amplitude frequency characteristic curves are very sensitive to the initial displacement of the piston rod. The initial displacement is slightly smaller, the amplitude-frequency curve moves to the right, the rolling natural frequency is slightly larger, and the curvature of the amplitude-frequency characteristic curve becomes larger, which means the instability region of the system becomes wider. The stability of the system can be enhanced by properly adjusting the initial displacement of the hydraulic cylinder of the rolling mill, which provides technical support for the manufacture of hydraulic cylinder.The comparison of different nonlinear friction coefficients in Figure5 shows that the nonlinear friction in the system is equivalent to the damping of the system. With the increase of β, amplitude frequency characteristic curve of the amplitude decreases. In a certain range, with the increase of nonlinear friction, the vibration of the rolling mill system increases.The comparison of different nonlinear spring coefficients in Figure6 shows that with the increase of the nonlinear spring force coefficient, the amplitude frequency curves of the system moves to the right, and the inherent frequency of the rolling mill becomes larger. At the same time, the bending degree of the amplitude frequency characteristic curve becomes larger, the unstable region of the system becomes wider, and the rolling process of rolling mill system will be easier to lose stability.Figure 6
Influence of nonlinear spring force coefficient on amplitude frequency characteristic curve.


### 4.3. Bifurcation Characteristics

The amplitude of excitation amplitude is used as the bifurcation parameter, the change law of the system bifurcation response is analyzed, and the influence of the amplitude of the external excitation on the stability of the system is studied.It can be seen from Figure7 that when the external excitation takes different values, the system has different degrees of bifurcation phenomena. The bifurcation diagram shows the single-value curve, the multivalued curve, and the infinite valued curve. The solutions of the system equations may be single solution, multiple solutions, and infinite solutions. That is, the vibration of rolling mill system is changed between one period, double period, and the chaotic motion. When the external excitation is F=5.91×105 N, the simulation results are shown in Figure 8: the phase trajectory is repeated in a finite region, which is a closed curve. There is only one isolated point in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is periodic motion. When the external excitation is F=6.012×105 N, the simulation results are shown in Figure 9: the phase trajectory is still repeated in a limited area, which is a closed curve. There are two isolated points in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is 2 times of the periodic motion. When the external excitation is F=6.15×105 N, the simulation results are shown in Figure 10: the phase trajectory is still repeated in a limited area, which is a closed curve. There are three isolated points in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is 3 times of the periodic motion. When the external excitation is F=6.27×105 N, the simulation results are shown in Figure 11: the phase trajectory is no longer a closed curve, and the corresponding Poincaré section is a discrete point in a certain region. At this time, the vibration of rolling mill system is chaotic motion state. In this paper, the data of all the simulation experiments are derived from the structural parameters of the 1780 rolling mill and the parameters of the rolling process. The simulation experiments are consistent with the actual working process of the rolling mill, and the simulation results reflect the characteristics of the rolling mill.Figure 7
Bifurcation characteristics of rolling mill system.Figure 8
F=5.91×105N, 1 time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 9
F=6.012×105N, 2-time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 10
F=6.15×105N, 3-time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 11
F=6.27×105N, chaotic motion. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)As to the limitations of the passive rotational magnetorheological (MR) damper, the need of keeping the electric current continuously in the damper, the strategy of using a discontinuous signal of the current proved to be a good alternative [27]. Through the simulation experiment of actual rolling mill parameters, the data basis for improving the stability of rolling mill vibration is provided. In the actual production process, the vibration of rolling mill can be suppressed by adjusting the external excitation to reduce the influence of vibration on the quality of rolling piece. Due to the special structure of the 1780 mill system, the quality of the rolling mill system, the spring stiffness, and the friction coefficient of the hydraulic cylinder cannot be changed. The actual experiment cannot test the vibration law of the rolling mill by changing these parameters. At present, it is difficult to test in the field, which can only capture the time-domain characteristic and weak spectrum characteristic of the rolling mill vibration. By using the real parameters of the 1780 rolling mill, the characteristics of the nonlinear spring force and the nonlinear friction force on the rolling mill are obtained. The amplitude frequency characteristics and bifurcation characteristics obtained from the simulation experiments can be used to analyze the characteristics of the working process of the rolling mill. The results of simulation experiment are applied to the field experiment, and the structural parameters and process parameters are adjusted according to the simulation results.


## 4.1. Time-Domain Characteristics

The vibration of rolling mill system is influenced by the nonlinear spring force and nonlinear friction force of the hydraulic cylinder of rolling mill. By taking different nonlinear spring force and friction coefficient, the variation law of time-domain response is simulated and analyzed. The simulation results are shown in Figures3–5.Figure 3
The vertical vibration curve of rolling mill system.
(a)(b)(c)Figure 4
Amplitude frequency characteristics of different initial displacement.Figure 5
The influence of nonlinear friction coefficient on amplitude frequency characteristic curve.As is shown in Figures3(a) and 3(b), with the increase of nonlinear friction, the peaks and troughs of the vertical vibration curve of the rolling mill system showed irregular vibration. It can be seen from Figures 3(b) and 3(c) that when the nonlinear spring force is increased, the vibration curve of rolling mill system has various irregular vibration. With the increase of the nonlinear binding force, the more irregular vibration of the milling mill system occurred, and this affects the stability of the system. From Figure 3(a) to Figure 3(c), when the nonlinear friction force is increased, the amplitude of the vibration displacement has no obvious change, but the amplitude of the vibration displacement is greatly reduced when the nonlinear spring force is increased. The above conclusions provide data support for the manufacture of rolling mill hydraulic cylinder. It is helpful to improve the stability of the rolling mill by selecting the appropriate nonlinear spring stiffness coefficient and friction coefficient.


## 4.2. Frequency-Domain Characteristics

The influence of different rolling parameters on the vibration of rolling mill system is studied. By using the actual parameters listed in Table1, the amplitude frequency characteristics of the system are simulated, and then the influence of the initial displacement of the piston rod, the nonlinear friction force, and the nonlinear spring force on the rolling mill system vibration are analyzed.Figure4 shows the different amplitude frequency characteristic curves of hydraulic cylinder piston rod under different initial displacement. The amplitude frequency characteristic curves are very sensitive to the initial displacement of the piston rod. The initial displacement is slightly smaller, the amplitude-frequency curve moves to the right, the rolling natural frequency is slightly larger, and the curvature of the amplitude-frequency characteristic curve becomes larger, which means the instability region of the system becomes wider. The stability of the system can be enhanced by properly adjusting the initial displacement of the hydraulic cylinder of the rolling mill, which provides technical support for the manufacture of hydraulic cylinder.The comparison of different nonlinear friction coefficients in Figure5 shows that the nonlinear friction in the system is equivalent to the damping of the system. With the increase of β, amplitude frequency characteristic curve of the amplitude decreases. In a certain range, with the increase of nonlinear friction, the vibration of the rolling mill system increases.The comparison of different nonlinear spring coefficients in Figure6 shows that with the increase of the nonlinear spring force coefficient, the amplitude frequency curves of the system moves to the right, and the inherent frequency of the rolling mill becomes larger. At the same time, the bending degree of the amplitude frequency characteristic curve becomes larger, the unstable region of the system becomes wider, and the rolling process of rolling mill system will be easier to lose stability.Figure 6
Influence of nonlinear spring force coefficient on amplitude frequency characteristic curve.


## 4.3. Bifurcation Characteristics

The amplitude of excitation amplitude is used as the bifurcation parameter, the change law of the system bifurcation response is analyzed, and the influence of the amplitude of the external excitation on the stability of the system is studied.It can be seen from Figure7 that when the external excitation takes different values, the system has different degrees of bifurcation phenomena. The bifurcation diagram shows the single-value curve, the multivalued curve, and the infinite valued curve. The solutions of the system equations may be single solution, multiple solutions, and infinite solutions. That is, the vibration of rolling mill system is changed between one period, double period, and the chaotic motion. When the external excitation is F=5.91×105 N, the simulation results are shown in Figure 8: the phase trajectory is repeated in a finite region, which is a closed curve. There is only one isolated point in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is periodic motion. When the external excitation is F=6.012×105 N, the simulation results are shown in Figure 9: the phase trajectory is still repeated in a limited area, which is a closed curve. There are two isolated points in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is 2 times of the periodic motion. When the external excitation is F=6.15×105 N, the simulation results are shown in Figure 10: the phase trajectory is still repeated in a limited area, which is a closed curve. There are three isolated points in a certain area of the Poincaré section, which indicates that the vibration of rolling mill system is 3 times of the periodic motion. When the external excitation is F=6.27×105 N, the simulation results are shown in Figure 11: the phase trajectory is no longer a closed curve, and the corresponding Poincaré section is a discrete point in a certain region. At this time, the vibration of rolling mill system is chaotic motion state. In this paper, the data of all the simulation experiments are derived from the structural parameters of the 1780 rolling mill and the parameters of the rolling process. The simulation experiments are consistent with the actual working process of the rolling mill, and the simulation results reflect the characteristics of the rolling mill.Figure 7
Bifurcation characteristics of rolling mill system.Figure 8
F=5.91×105N, 1 time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 9
F=6.012×105N, 2-time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 10
F=6.15×105N, 3-time cycle movement. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)Figure 11
F=6.27×105N, chaotic motion. (a) Phase trajectory diagram. (b) Poincaré section.
(a)(b)As to the limitations of the passive rotational magnetorheological (MR) damper, the need of keeping the electric current continuously in the damper, the strategy of using a discontinuous signal of the current proved to be a good alternative [27]. Through the simulation experiment of actual rolling mill parameters, the data basis for improving the stability of rolling mill vibration is provided. In the actual production process, the vibration of rolling mill can be suppressed by adjusting the external excitation to reduce the influence of vibration on the quality of rolling piece. Due to the special structure of the 1780 mill system, the quality of the rolling mill system, the spring stiffness, and the friction coefficient of the hydraulic cylinder cannot be changed. The actual experiment cannot test the vibration law of the rolling mill by changing these parameters. At present, it is difficult to test in the field, which can only capture the time-domain characteristic and weak spectrum characteristic of the rolling mill vibration. By using the real parameters of the 1780 rolling mill, the characteristics of the nonlinear spring force and the nonlinear friction force on the rolling mill are obtained. The amplitude frequency characteristics and bifurcation characteristics obtained from the simulation experiments can be used to analyze the characteristics of the working process of the rolling mill. The results of simulation experiment are applied to the field experiment, and the structural parameters and process parameters are adjusted according to the simulation results.


## 5. Conclusions

Based the nonlinear spring force and friction force of the hydraulic cylinder, the vibration model of rolling mill system is established. The dynamic equations of the system are constructed, and then the amplitude frequency response equations are obtained. The simulation analysis is carried out from three aspects: the time domain, the amplitude frequency, and the bifurcation characteristic. Through the analysis of numerical simulation, the main conclusions are obtained as follows:(1)
Increasing the nonlinear friction force and spring force lead to the irregular change of the vertical vibration curve of rolling mill system. With the increase of nonlinear force, the rolling mill system shows irregular vibration, which affects the stability of the system.(2)
The initial position of the hydraulic cylinder is changed, which affects the size of the natural frequency of the rolling mill and the range of the stable region of the system; the increase of nonlinear friction force restrains the vibration of rolling mill system; the increase of the nonlinear spring force makes the unstable region of the roller system of rolling mill to become wider, and the stability of the system is affected.(3)
Under different excitation amplitude, the vibration of rolling mill system is alternating between periodic motion, period-doubling motion, and chaotic motion. The dynamic behavior of roll system can be controlled by changing the amplitude of the external excitation.



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*Source: 6632714-2021-01-19.xml*