# Active Disturbance Rejection Control of Valve-Controlled Cylinder Servo Systems Based on MATLAB-AMESim Cosimulation

Authors: Wenxiao Guo; Yanbin Zhao; Ruiqin Li; Haigang Ding; Jianwei Zhang
Journal: Complexity
 (2020)

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## Abstract

The valve-controlled cylinder position servo system has the advantages of large output force and large power. As characteristics of nonlinearity and uncertainty exist in the hydraulic servo system, it is difficult for the traditional PID control to meet the requirements of high precision and control. The active disturbance rejection control (ADRC) considers the uncertainty of the system and external disturbances as the total disturbance. In this paper, the valve-controlled cylinder servo system is designed based on ADRC, its working principle is described, and its mathematical model and cosimulation model based on MATLAB-AMESim are established. In the case of constant load, variable load, and long pipeline, the comparative simulation of ADRC and PID is carried out. The simulation results show that the ADRC can effectively suppress the disturbance of the internal parameter changes and external load changes of the hydraulic system and has strong robustness and high control accuracy. This study provides a reference for the application of ADRC in electrohydraulic servo systems.


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## Body

## 1. Introduction

The valve-controlled cylinder position servo system is a common hydraulic power execution system, with the advantages of large output force, large unit power volume ratio, and so on. It has been widely used in various fields. However, the electrohydraulic position servo control system is time-varying and nonlinear, such as nonlinearity of pressure flow and frictional force of the servo valve. It presents various features of time-varying parameters such as leakage coefficient, change of load, and change of damping ratio. Traditional PID control strategy is simple, but compared to some nonlinear, time-varying parameters of the system, it cannot achieve precise positioning control. In order to enhance the antijamming ability of electrohydraulic position servo control system while improving the precision control of the system, experts and scholars have researched a number of control strategies, including adaptive control, sliding mode control, and fuzzy control. Considering that the electrohydraulic servo system is nonlinear, Fang and Guan et al. [1–5] proposed an adaptive back-stepping sliding mode controller. The advantages of adaptive back-stepping control strategy and sliding mode controller strategy can be combined to strengthen the system’s tracking performance. Zhang et al. [6] proposed a multimodel robust adaptive control theory. According to the range of parametric uncertainties, multiple identification models are designed and nonlinear robust items are added to the models to suppress the influence of uncertain nonlinearities and improve the robustness and the transient response performance of the system. Na et al. [7, 8] proposed a new control method without using the back-stepping scheme and any function approximators. They also propose an alternative and simple, yet efficient, estimation method to handle unknown dynamics and external disturbances for motion control of robotic systems.In 1999, Han [9–11] proposed the active disturbance rejection control (ADRC). In view of the fact that the parameter turning of the original nonlinear ADRC is complicated and not convenient for practical industrial application, Gao et al. [12–17] simplified the nonlinear part of the ADRC, proposed LADRC that is convenient to set parameters, and introduced the basic idea and principle of ADRC in detail. ADRC control strategy does not depend on the accurate mathematical model of controlled systems and considers the uncertainty of the system and external disturbance as the total disturbance. The extended state observer is used for observing internal parameter uncertainties and external disturbances, so that the disturbances of the system are suppressed effectively. For systems with larger amount of uncertainties both in dynamics and external disturbances, the precise control is realized with an ADRC controller. It has been successfully applied in industrial process, servo system control, automobile engine control, aerospace, and other fields and has a good prospect of engineering application. However, there are few reports about ADRC used in hydraulic servo systems [18, 19].In this paper, an active disturbance rejection control strategy is developed to address those electrohydraulic position servo control systems with inherent nonlinear behaviors and modeling uncertainties. The simulation model of ADRC is established by using the MATLAB-AMESim cosimulation method in Simulink module library. The physical model of the valve-controlled cylinder position servo system was established on AMESim software. According to the simulation results, the effectiveness of the control method is verified and the influence of controller parameters on the control effect is analyzed.


## 2. Mathematical Modeling

The valve-controlled cylinder position servo system studied in this paper is shown in Figure1. In this control system, the servo valve is the control component and the cylinder is the drive component. The cylinder displacement is detected using a displacement sensor and fed back to the ADRC controller to control the opening of the servo valve, so that the cylinder displacement is in the closed-loop control. The load (mass block) on the right is driven by the hydraulic cylinder. The main goal of this paper is to design the controller so that the hydraulic cylinder displacement controlled by the controller can track any given displacement as quickly as possible.Figure 1
Model of valve-controlled cylinder position servo systems.The flow equation of the servo valve is(1)qL=CdωxvPS−PLsgnxvρ.Here,Cd is the valve’s port flow coefficient, ω is the servo valve’s area gradient, xv is the servo valve’s spool displacement, PS is the servo valve’s inlet pressure, PL is the load pressure, and ρ is the oil density.sgnxv is the symbolic function as follows:(2)sgnxv=1,xv≥0,−1,xv<0.Because the response speed of the servo amplifier is faster than that of the hydraulic system, the servo amplifier is treated as a proportional link to obtain the relationship between spool displacement (xv) and control input (u), and(3)xv=KvKsvu,where Kv is the gain of controller, Ksv is the gain of the servo valve, and u is the input signal of controller.The flow continuity equation of the hydraulic cylinder is(4)qL=APdxPdt+CtppL+Vt4βedpLdt.Here,AP is the effective area of the piston in the hydraulic cylinder, xP is the piston displacement, Ctp is the total leakage coefficient of the hydraulic cylinder, Ctp=Cip+0.5Cep, and Vt is the total volume of the hydraulic cylinder cavity.The force balance equation of the hydraulic cylinder and the load is(5)APpL=mtd2xPdt2+BpdxPdt+KxP+FL.Here,mt is the total mass of the piston and the load, Bp is the viscous damping coefficient of the piston and the load, K is the spring stiffness, and FL is the accidental load force acting on the piston.Take the state variablesx1=xp, x2=x˙p, and x3=x¨p, and they are displacement, velocity, and acceleration, respectively.The state space expression of the servo system is(6)x˙1=x2,x˙2=x3,x˙3=a0x1+a1x2+a2x3+bu+d,y=x1,where a0=−4βeCtp/mtvt,(7)a1=−Kmt−4βemtVtAp2−CtpBp,a2=−Bpmt−4βeCtVt,b=4ApβeCdωmtVtρPS−PLsgnxv,dt=−F˙Lmt−4βeCtpFLmtVt,and y is the output for system position.


## 3. Design of ADRC

The core design of ADRC is to define an extended state, take the simple cascade integral form as the standard type, treat the parts of the system dynamic that are different from the standard type (including the uncertainty and disturbance of the system) as the total disturbance (including internal disturbance and external disturbance), and define the total disturbance into the extended state. Then, by means of the extended state observer, the total disturbance is estimated and eliminated in real time, so as to restore the controlled object free of disturbance, uncertainty, and nonlinearity to the standard integral series type and realize the control of the system. ADRC makes the control system design from complex to simple, from abstract to intuitive.The linear ADRC consists of three parts: tracking differentiator, linear extended state observer, and linear state error feedback control law, as shown in Figure2.Figure 2
Structure of ADRC.The design of ADRC does not need to rely on the speciﬁc mathematical model of a controlled object. It only needs to know the relative order of the system. For the design of LADRC based on generalized controlled object formula (6), the following steps are arranged.


### 3.1. Transition Process

In this article, “Arrange transition” and “Track-Differentiator” are combined to simplify the controller structure. As shown in Figure3, the valve-controlled cylinder position servo system is a third-order system, so two tracking differentiators are used in series in the simulation process.Figure 3
Schematic of the tracking differentiator.Arrange the transition process according to the set valuex0 as follows:(8)fh=fhanx1−x0,x2,r,h,x1=x1+hx2,x2=x2+hfh.Define the fast-optimal control synthesis function of equation (9) as(9)fh=fhanx1−x0,x2,r,h0.The realization of fh is shown in the following equation:(10)d=rh0,d0=h0d,y=x1−x0+h0x2,a0=d2+8ry,a=x2+a0+d2signy,y>d0,x2+yh0,y≤d0,fhan=−rsigna,a>d,rad,a≤d.Here,h0 is the filter factor; h is the simulation step length and is related to the sampling frequency of the system; x0 is the expected displacement signal; and r is the velocity factor, which determines the speed of tracking expected displacement signal.


### 3.2. Extended State Observer

The extended state observer of the system is established by tracking and estimating system state and disturbance with system output and input:(11)x˙3=a0x1+a1x2+a2x3+bu+d.Here, it is denoted thatx˙3=fx1,x2,x3,d+bu to obtain the generalized controlled plant model:(12)x˙1=x2,x˙2=x3,x˙3=fx1,x2,x3,d+bu,y=x1.The real-time action offx1,x2,x3,d on the system is expanded to a new state variable x4, denoted as x4=fx1,x2,x3,d and denoted as x˙4=wt. Then, the system (12) can be expanded into a new system as follows:(13)x˙1=x2,x˙2=x3,x˙3=x4+bu,x˙4=wt,y=x1.A linear state observer is established for the extended system:(14)e=z1−y,z1=z1+hz2−β01e,z2=z2+hz3−β02e,z3=z3+hz4−β03e+bu,z4=z4+h−β04e,where e is the output error. State observer (14) is called the extended state observer (ESO) of system (10), the variable x4 is called the extended state, and the parameter of the ESO is(15)β01=1h,β02=13h2,β04=5133h4,β03=282h3.This set of parameters is “inherited” for objects of the fourth order and below and is not limited by the estimated disturbance amplitudeγ [11].


### 3.3. Feedback Law of State Error

Linear state error feedback (LSEF) compensates the system disturbance through state error feedback. In this system, LSEF is designed as follows:(16)e1=x1−z1,e2=x2−z2,e3=x3−z3,u0=α11e1+α12e2+α13e3,where xii=1,2,3 is the output value of the track differentiator, zii=1,2,3,4 is the output value of the ESO, eii=1,2,3 is the state error, α1ii=1,2,3 is the gain coefficient of the controller, and u0 is the linear error feedback control quantity. Considering the disturbance error of the system, the final output of linear ADRC is obtained by compensating u0:(17)u=u0−z4tb0.


### 3.4. Parameter Tuning

The ADRC controller has many parameters to be tuned. According to the functions of the tracking differentiator, the ESO, and the feedback control law, the parameters can be set independently according to the “separation principle”:(1)
The parameterr mainly affects the performance of the tracking differentiator. When r becomes larger, the response of the system becomes faster and the tracking accuracy becomes higher, but the overshoot of the system becomes larger as well. When r is small, the tracking speed of the system will become very slow, even unable to track the reference input signal.(2)
The increase ofβ01 and β02 in a certain range has no great influence on the control effect of the system, but when β01 is large, the system is prone to divergent oscillation and when β01 is small, the tracking effect of the system will become worse, so β01=1/h is generally adopted. Larger β03 will produce high-frequency noise signals, resulting in poor system control, but smaller β03 will increase the number of oscillations and increase the amplitude, so generally β03=2/82h3; when β04 decreases, the tracking speed of the system slows down, the transition process tends to be stable, but it is easy to cause a large phase lag, so β04=5/133h4.(3)
b0 is the only variable related to the controlled system in the whole controller. The choice of different b0 values is equivalent to the change of the total disturbance value in different ranges; that is, the compensation component will also produce corresponding changes. The gain α11 of the controller affect the corresponding rapidity of the system, but overshoot occurs when α11 is too large. An appropriate controller gain α12 will reduce overshoot.


## 3.1. Transition Process

In this article, “Arrange transition” and “Track-Differentiator” are combined to simplify the controller structure. As shown in Figure3, the valve-controlled cylinder position servo system is a third-order system, so two tracking differentiators are used in series in the simulation process.Figure 3
Schematic of the tracking differentiator.Arrange the transition process according to the set valuex0 as follows:(8)fh=fhanx1−x0,x2,r,h,x1=x1+hx2,x2=x2+hfh.Define the fast-optimal control synthesis function of equation (9) as(9)fh=fhanx1−x0,x2,r,h0.The realization of fh is shown in the following equation:(10)d=rh0,d0=h0d,y=x1−x0+h0x2,a0=d2+8ry,a=x2+a0+d2signy,y>d0,x2+yh0,y≤d0,fhan=−rsigna,a>d,rad,a≤d.Here,h0 is the filter factor; h is the simulation step length and is related to the sampling frequency of the system; x0 is the expected displacement signal; and r is the velocity factor, which determines the speed of tracking expected displacement signal.


## 3.2. Extended State Observer

The extended state observer of the system is established by tracking and estimating system state and disturbance with system output and input:(11)x˙3=a0x1+a1x2+a2x3+bu+d.Here, it is denoted thatx˙3=fx1,x2,x3,d+bu to obtain the generalized controlled plant model:(12)x˙1=x2,x˙2=x3,x˙3=fx1,x2,x3,d+bu,y=x1.The real-time action offx1,x2,x3,d on the system is expanded to a new state variable x4, denoted as x4=fx1,x2,x3,d and denoted as x˙4=wt. Then, the system (12) can be expanded into a new system as follows:(13)x˙1=x2,x˙2=x3,x˙3=x4+bu,x˙4=wt,y=x1.A linear state observer is established for the extended system:(14)e=z1−y,z1=z1+hz2−β01e,z2=z2+hz3−β02e,z3=z3+hz4−β03e+bu,z4=z4+h−β04e,where e is the output error. State observer (14) is called the extended state observer (ESO) of system (10), the variable x4 is called the extended state, and the parameter of the ESO is(15)β01=1h,β02=13h2,β04=5133h4,β03=282h3.This set of parameters is “inherited” for objects of the fourth order and below and is not limited by the estimated disturbance amplitudeγ [11].


## 3.3. Feedback Law of State Error

Linear state error feedback (LSEF) compensates the system disturbance through state error feedback. In this system, LSEF is designed as follows:(16)e1=x1−z1,e2=x2−z2,e3=x3−z3,u0=α11e1+α12e2+α13e3,where xii=1,2,3 is the output value of the track differentiator, zii=1,2,3,4 is the output value of the ESO, eii=1,2,3 is the state error, α1ii=1,2,3 is the gain coefficient of the controller, and u0 is the linear error feedback control quantity. Considering the disturbance error of the system, the final output of linear ADRC is obtained by compensating u0:(17)u=u0−z4tb0.


## 3.4. Parameter Tuning

The ADRC controller has many parameters to be tuned. According to the functions of the tracking differentiator, the ESO, and the feedback control law, the parameters can be set independently according to the “separation principle”:(1)
The parameterr mainly affects the performance of the tracking differentiator. When r becomes larger, the response of the system becomes faster and the tracking accuracy becomes higher, but the overshoot of the system becomes larger as well. When r is small, the tracking speed of the system will become very slow, even unable to track the reference input signal.(2)
The increase ofβ01 and β02 in a certain range has no great influence on the control effect of the system, but when β01 is large, the system is prone to divergent oscillation and when β01 is small, the tracking effect of the system will become worse, so β01=1/h is generally adopted. Larger β03 will produce high-frequency noise signals, resulting in poor system control, but smaller β03 will increase the number of oscillations and increase the amplitude, so generally β03=2/82h3; when β04 decreases, the tracking speed of the system slows down, the transition process tends to be stable, but it is easy to cause a large phase lag, so β04=5/133h4.(3)
b0 is the only variable related to the controlled system in the whole controller. The choice of different b0 values is equivalent to the change of the total disturbance value in different ranges; that is, the compensation component will also produce corresponding changes. The gain α11 of the controller affect the corresponding rapidity of the system, but overshoot occurs when α11 is too large. An appropriate controller gain α12 will reduce overshoot.


## 4. Cosimulation Modeling

Because the electrohydraulic position servo control systems have inherent nonlinear behaviors and modeling uncertainties, it is difficult to establish an accurate mathematical model, so the cosimulation platform using MATLAB and AMESim is applied in this work. The mechanical and hydraulic parts are built in AMESim and the control part is modeled by MATLAB-Simulink. By using AMESim’s interface technology to Simulink and combining two excellent professional simulation tools, AMESim’s outstanding fluid mechanical simulation performance can be brought into play and Simulink’s powerful numerical processing capability can be utilized to achieve more perfect complementary effects.The cosimulation principle of the valve-controlled cylinder servo system in ADRC based on MATLAB-AMESim platform is shown in Figure4. The concrete realization process of cosimulation between AMESim and Simulink is as follows: First, create an interface through the interface menu in the AMESim to connect Simulink. Next, complete the submodel mode and parameter mode setting. Finally, run the hydraulic system model to generate S-function for Simulink. A cosimulation model built on MATLAB-AMESim platform is shown in Figure 5, nad main parameters of the system are listed in Table 1.Figure 4
Schematic diagram of cosimulation principle.Figure 5
Cosimulation model. (a) Hydraulic system model in AMESim. (b) ADRC model in MATLAB.
(a)(b)Table 1
Main parameters of the system.
ParametersValueCylinder diameter45/63 mmLoad mass100 kgMotor speed1500 r/minPump delivery100 mL/rRelief pressure350 barLoad spring rate10000 N/mADRC parameters are set as follows:r=0.25, h=0.011, and T=0.011.Observer parameters are(18)β0i=1h13h2282h35133h4.Controller parameters are(19)b0=50,α1i=4000.0620.1.PID control is the most common and effective control method in engineering and its controller is designed as follows:(20)u=Kpe+Ki∫0tedt+Kddedt,where Kp is the proportional gain, Ki is the integral gain, Kd is the differential gain, and e is the error. Those parameters are tuned to the best after many tests. In this paper, ADRC and PID are compared and analyzed.


## 5. Simulation Results and Analysis

In order to analyze the dynamic performances of the system in ADRC, the following three simulation scenarios are designed in this section: (1) dynamic responses under constant load; (2) dynamic responses under variable load; (3) dynamic responses under long pipeline. Comparative analyses of the control characteristics of ADRC and PID are made.


### 5.1. Dynamic Responses under Constant Load

When the load force is constant, step responses of the system in ADRC and PID are shown in Figure6, where reference displacement of the hydraulic cylinder is 200 mm. Under this condition, the parameters of PID are set as follows: Kp = 200, Ki = 105, and Kd = 2.5. Figure 6(a) shows that, under the ADRC and PID, the maximum rise time is 0.5 s and 1 s, respectively; the maximum adjustment time is 1.2 s and 5 s, respectively; and the maximum overshoot quantity is 1% and 9.5%, respectively. Figure 6(b) shows that, compared to PID, the spool displacement under the ADRC changes smoothly during the process of opening, there is no impact, and the maximum opening is about 80% larger.Figure 6
Step responses in ADRC and PID under constant load. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)Figure7 indicates sinusoidal response under ADRC and PID. It shows that the system in ADRC can accurately track the reference signal with smaller phase lag. In the initial stage, the displacement of the spool in ADRC is large, so that the hydraulic cylinder can quickly refer to the signal. Then, the spool displacement is basically the same as the PID control. In the commutation phase, the overshoot of the hydraulic cylinder under ADRC control is smaller than under PID control.Figure 7
Sinusoidal responses in ADRC and PID under constant load. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)The step response and sinusoidal response show that ADRC has more advantages than PID and the system in ADRC has fast dynamic response and high control accuracy.


### 5.2. Dynamic Responses under Variable Load

In practice, the load usually changes, so it is necessary to investigate the dynamic characteristics of the control system under variable load. In this part, the load force is variable in the simulation process. Under this condition, the parameters of PID are set as follows:Kp = 200, Ki = 85, and Kd = 2.Figure8 shows that the actual displacement of the hydraulic cylinder controlled in ADRC and PID will be affected to different degrees in the process of load change. However, the ADRC controller considers the external disturbance as total disturbance and the disturbance is estimated and eliminated by the extended state observer in real time, so as to realize accurate control. Therefore, the system in ADRC can respond faster and can track the reference displacement. In addition, in the early stage of response in ADRC, the opening of the servo valve is very large to move the hydraulic cylinder to the set position quickly. The cylinder displacement controlled by PID not only takes a long time to reach the set value but also fluctuates greatly by the variable force, resulting in poor stability.Figure 8
Step responses in ADRC and PID under variable load. (a) Sinusoidal load. (b) Cylinder displacement response. (c) Spool position response.
(a)(b)(c)


### 5.3. Dynamic Responses under Long Pipeline

The hydraulic pipeline is one of the indispensable components of the hydraulic system and plays the role of connecting the component and the transmission medium. The characteristics of the pipeline have a great influence on the dynamic and static characteristics of the hydraulic system. When the pipeline is short, the pipeline effect can be ignored, but when the pipeline is long, the pipeline effect will cause the response to lag and the control accuracy will reduce. This section mainly discusses the dynamic characteristics of systems with long pipelines. In the simulation, the pipeline length is set to 50 m and diameter is set to 25 mm. Under this condition, the parameters of PID are set as follows:Kp = 105, Ki = 20, and Kd = 0.1.The simulation results shown in Figure9 indicate that there is a certain delay in the step response of the long pipeline hydraulic systems, but the delay by ADRC is short. The hydraulic cylinder in PID control has a long adjustment time and a large overshoot, while that in ADRC can reach the set position quickly, and there is almost no overshoot. It can be seen that ADRC has obvious advantages in the hydraulic system with long pipelines.Figure 9
Step responses of the hydraulic system with long pipelines. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)


## 5.1. Dynamic Responses under Constant Load

When the load force is constant, step responses of the system in ADRC and PID are shown in Figure6, where reference displacement of the hydraulic cylinder is 200 mm. Under this condition, the parameters of PID are set as follows: Kp = 200, Ki = 105, and Kd = 2.5. Figure 6(a) shows that, under the ADRC and PID, the maximum rise time is 0.5 s and 1 s, respectively; the maximum adjustment time is 1.2 s and 5 s, respectively; and the maximum overshoot quantity is 1% and 9.5%, respectively. Figure 6(b) shows that, compared to PID, the spool displacement under the ADRC changes smoothly during the process of opening, there is no impact, and the maximum opening is about 80% larger.Figure 6
Step responses in ADRC and PID under constant load. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)Figure7 indicates sinusoidal response under ADRC and PID. It shows that the system in ADRC can accurately track the reference signal with smaller phase lag. In the initial stage, the displacement of the spool in ADRC is large, so that the hydraulic cylinder can quickly refer to the signal. Then, the spool displacement is basically the same as the PID control. In the commutation phase, the overshoot of the hydraulic cylinder under ADRC control is smaller than under PID control.Figure 7
Sinusoidal responses in ADRC and PID under constant load. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)The step response and sinusoidal response show that ADRC has more advantages than PID and the system in ADRC has fast dynamic response and high control accuracy.


## 5.2. Dynamic Responses under Variable Load

In practice, the load usually changes, so it is necessary to investigate the dynamic characteristics of the control system under variable load. In this part, the load force is variable in the simulation process. Under this condition, the parameters of PID are set as follows:Kp = 200, Ki = 85, and Kd = 2.Figure8 shows that the actual displacement of the hydraulic cylinder controlled in ADRC and PID will be affected to different degrees in the process of load change. However, the ADRC controller considers the external disturbance as total disturbance and the disturbance is estimated and eliminated by the extended state observer in real time, so as to realize accurate control. Therefore, the system in ADRC can respond faster and can track the reference displacement. In addition, in the early stage of response in ADRC, the opening of the servo valve is very large to move the hydraulic cylinder to the set position quickly. The cylinder displacement controlled by PID not only takes a long time to reach the set value but also fluctuates greatly by the variable force, resulting in poor stability.Figure 8
Step responses in ADRC and PID under variable load. (a) Sinusoidal load. (b) Cylinder displacement response. (c) Spool position response.
(a)(b)(c)


## 5.3. Dynamic Responses under Long Pipeline

The hydraulic pipeline is one of the indispensable components of the hydraulic system and plays the role of connecting the component and the transmission medium. The characteristics of the pipeline have a great influence on the dynamic and static characteristics of the hydraulic system. When the pipeline is short, the pipeline effect can be ignored, but when the pipeline is long, the pipeline effect will cause the response to lag and the control accuracy will reduce. This section mainly discusses the dynamic characteristics of systems with long pipelines. In the simulation, the pipeline length is set to 50 m and diameter is set to 25 mm. Under this condition, the parameters of PID are set as follows:Kp = 105, Ki = 20, and Kd = 0.1.The simulation results shown in Figure9 indicate that there is a certain delay in the step response of the long pipeline hydraulic systems, but the delay by ADRC is short. The hydraulic cylinder in PID control has a long adjustment time and a large overshoot, while that in ADRC can reach the set position quickly, and there is almost no overshoot. It can be seen that ADRC has obvious advantages in the hydraulic system with long pipelines.Figure 9
Step responses of the hydraulic system with long pipelines. (a) Cylinder displacement response. (b) Spool position response.
(a)(b)


## 6. Conclusion

(1)
A cosimulation model of the valve-controlled cylinder based on MATLAB-AMESim platform is more accurate than the mathematical model and is closer to the real system.(2)
The structure and basic principles of active disturbance rejection control are introduced; the active disturbance rejection controller is designed, and the rule of parameter setting is clarified.(3)
The comparative simulation with ADRC and PID is carried out in cases of constant load, variable load, and long pipeline. The simulation results show that the ADRC can effectively suppress the disturbance of the internal parameter changes and external load changes of the hydraulic system, has strong robustness and control accuracy, and has potential in electrohydraulic systems for high-performance control.



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