A Compound Scheme Based on Improved ADRC and Nonlinear Compensation for Electromechanical Actuator

A compound scheme, based on an improved active disturbance rejection controller (ADRC) and nonlinear compensation, is developed for the electromechanical actuator (EMA) system in this paper. First, considering the influences of backlash, friction on the EMA system, a model for the EMA system is presented. The LuGre model and Hysteresis inverse model are used to compensate for the friction and backlash phenomenon. Then, the method of improved ADRC, based on the Fal function filter and a Linear extended state observer (LESO), is investigated. Simultaneously, since the controller parameters of the improved ADRC are complicated, the non-dominated sorting genetic algorithm II (NSGA-II) is presented to optimize the controller parameters, to achieve the best dynamic response. Finally, simulation and experiment are presented to validate the effectiveness of the proposed method. Under the nonlinear compensation, the performance of the proposed compound scheme is compared with the conventional proportional integral (PI) controller, in terms of step response analysis and sine wave response analysis. Simulation and experiments show that the proposed controller provides high-performance dynamic characteristics.


Introduction
The electromechanical actuator (EMA) system is vital in missiles. It is used to receive instructions from the navigation control system and deflect, according to the instructions, to change the flight attitude of the missile. With the development of high-performance guidance weapons, higher requirements are put forward for the EMA system. The EMA system is a typical mechatronic system, and the nonlinearity of internal and external disturbance, friction, and backlash [1,2] seriously affect the system's performance. It is vital to study the nonlinearity of the EMA system and propose effective control methods.
Friction compensation based on the friction model is a widely used method to alleviate the effect of friction. There are many friction models, such as the classic model [3], Dahl model [4], Boliman and sorine model [5], elasto-plastic model [6], LuGre model [7], Karnopp model [8], Borello model [9] and Generalized maxwell-slip model [10], although these models have some applications in different systems. Among them, the LuGre model provides a perfect approximation for the friction phenomenon and is widely used in many applications to describe friction [11,12]. It is regarded as a dynamic friction model, which can completely describe the pre-sliding and gross sliding periods of the motion in the mechanical transmission device [13]. Especially compared with the Karnopp model [8] and Borello model [9], the LuGre algorithm can more comprehensively describe the friction characteristics. Therefore, this model is used to describe the friction torque of the EMA system. Due to the play between adjacent movable parts of the EMA system, the backlash is a common phenomenon in the EMA system. The backlash can cause oscillations and inaccuracy in the system [14]. There are two methods to alleviate the backlash effects: the

System Model
The system model of the EMA system is presented in Figure 2. The brushless direct current motor (BLDCM) (shown in Figure 2, represented by the symbol M) is used to drive the mechanism of the EMA system. The transmitted torque and the motion relationship between the actual position and backlash is expressed by Equation (1).
where m J represents the equivalent moments of inertia. s K , a R , a L , d i denote the pulse width modulation (PWM) coefficient, the armature resistance, the armature inductance, and the armature current, respectively. n , em T , m K and e K denote the rotor speed, the motor torque, the torque constant, and the electrical constant, respectively. mf T is the friction torque, mh T is the load torque, 2B is the equivalent backlash of the output shaft, a δ is the actual position with backlash, and θ is the position without backlash.
As shown in Equation (1), if the load of the EMA system is determined, the motor selection is determined, and the model of nonlinear characteristics is clear, meaning the dynamic characteristics of the EMA system can be analyzed. In Section 2.2, the nonlinear model will be analyzed.

Nonlinear Factors
In the EMA system, nonlinear factors are inevitable, and they seriously degrade system performance. It is urgent to carry out research on the nonlinear model. Introduction and identification of the friction model are first presented. The LuGre model is a popular friction model. The schematic of the LuGre model is illustrated in Figure 3.

System Model
The system model of the EMA system is presented in Figure 2.  Figure 1. The diagrammatic sketch of the EMA system.

System Model
The system model of the EMA system is presented in Figure 2. The brushless direct current motor (BLDCM) (shown in Figure 2, represented by the symbol M) is used to drive the mechanism of the EMA system. The transmitted torque and the motion relationship between the actual position and backlash is expressed by Equation (1) where m J represents the equivalent moments of inertia. s K , a R , a L , d i denote the pulse width modulation (PWM) coefficient, the armature resistance, the armature inductance, and the armature current, respectively. n , em T , m K and e K denote the rotor speed, the motor torque, the torque constant, and the electrical constant, respectively. mf T is the friction torque, mh T is the load torque, 2B is the equivalent backlash of the output shaft, a δ is the actual position with backlash, and θ is the position without backlash.
As shown in Equation (1), if the load of the EMA system is determined, the motor selection is determined, and the model of nonlinear characteristics is clear, meaning the dynamic characteristics of the EMA system can be analyzed. In Section 2.2, the nonlinear model will be analyzed.

Nonlinear Factors
In the EMA system, nonlinear factors are inevitable, and they seriously degrade system performance. It is urgent to carry out research on the nonlinear model. Introduction and identification of the friction model are first presented. The LuGre model is a popular friction model. The schematic of the LuGre model is illustrated in Figure 3. The brushless direct current motor (BLDCM) (shown in Figure 2, represented by the symbol M) is used to drive the mechanism of the EMA system. The transmitted torque and the motion relationship between the actual position and backlash is expressed by Equation (1).
where J m represents the equivalent moments of inertia. K s , R a , L a , i d denote the pulse width modulation (PWM) coefficient, the armature resistance, the armature inductance, and the armature current, respectively. n, T em , K m and K e denote the rotor speed, the motor torque, the torque constant, and the electrical constant, respectively. T m f is the friction torque, T mh is the load torque, 2B is the equivalent backlash of the output shaft, δ a is the actual position with backlash, and θ is the position without backlash. As shown in Equation (1), if the load of the EMA system is determined, the motor selection is determined, and the model of nonlinear characteristics is clear, meaning the dynamic characteristics of the EMA system can be analyzed. In Section 2.2, the nonlinear model will be analyzed.

Nonlinear Factors
In the EMA system, nonlinear factors are inevitable, and they seriously degrade system performance. It is urgent to carry out research on the nonlinear model. Introduction and identification of the friction model are first presented. The LuGre model is a popular friction model. The schematic of the LuGre model is illustrated in Figure 3.  Friction torque is as follows [35]: where mf T is the friction torque, c T is the coulomb friction torque, s T is the static fric-  Friction torque is as follows [35]: where T m f is the friction torque, T c is the coulomb friction torque, T s is the static friction torque, σ 0 is the bristle stiffness, σ 1 is the bristle damping, σ 2 is the viscous friction coefficient, . θ s is the Stribeck velocity, .
θ is the velocity of the system, z is the dynamics of the deformation of bristles. T m f also appears in Equation (1). If the parameters of the friction model in Equation (2) of the system can be determined, the value of T m f can be obtained. When the value of T m f is obtained, it can be combined with Equation (1) to calculate the performance of the EMA system. Static parameters, such as T c , T s , . θ s and σ 2 , are obtained by identification with the constant speed motion method. Thus, . z = 0 (as a result σ 1 . z = 0), and z can be described by the following equation: (1)) is set as 0, and the friction torque is as follows:

Equation (3) is the intermediate equation for friction parameter identification. Substituting Equations (2) and (3) into Equation (1), T mh (shown in Equation
where the subscript ss denotes the steady state, that is, the speed is the data measured at a constant speed. It can be seen from Equation (4) that we can measure the armature current i dss to obtain the friction torque. The test bench is shown in Figure 4. The test bench consists of a PC and the EMA system. The PC is used to send commands to the EMA system and receive the sensors' output from the EMA system. Then, the PC processes the data to identify the friction parameters.      According to the type selection and constituent units of the EMA system, shown in Figure 1, ignoring the high-order factors, this paper uses the second-order model in Equation (1) to study the characteristics of the system. Therefore, in the next identification process, our physical model is consistent with the mathematical model shown in Equation (1).
The identification process is as follows: run the EMA system at a uniform speed and measure the corresponding speed and current to obtain a set of values, and then the speed increases continuously from a small value to a large value (the curve type shown in Figure 5). Then, the static parameters in the corresponding Equation (4) can be obtained by the least square method. Static parameters are identified by using the least square method and are shown in Table 1.    The identification of dynamic parameters is also very important. The dynamic parameters of the LuGre model can be obtained as follows: firstly, model linearization is adopted at , and then z = θ , and should be replaced in Equation (3), mf T shown in Equation (1) can be written as: In order to deduce how to obtain dynamic parameters, set 0 mh T = and combine Equation (1), Equation (2), and Equation (5) by Laplace transform, and we can get: According to the form of Equation (6), we can use the second-order system theory to analyze the dynamic parameters. Set 0 / n m J = ω σ , (6) can be described as: As shown in Equation (7), the theory of second-order damping systems can be used to deal with the system's friction problem. Using the experimental platform shown in Figure 4, the input command is the position command. By obtaining the step response curve  The identification of dynamic parameters is also very important. The dynamic parameters of the LuGre model can be obtained as follows: firstly, model linearization is adopted at z = 0 and dθ/dt = 0, and then z = θ, and dz/dt = dθ/dt should be replaced in Equation (3), T m f shown in Equation (1) can be written as: In order to deduce how to obtain dynamic parameters, set T mh = 0 and combine Equation (1), Equation (2), and Equation (5) by Laplace transform, and we can get: According to the form of Equation (6), we can use the second-order system theory to analyze the dynamic parameters. Set ω n = (6) can be described as: As shown in Equation (7), the theory of second-order damping systems can be used to deal with the system's friction problem. Using the experimental platform shown in Figure 4, the input command is the position command. By obtaining the step response curve of the system, then, according to the principle of a second-order system, ω n , ζ is obtained. Based on classical second-order control theory, σ 0 and σ 1 are obtained. Dynamic parameters are presented in Table 2. Introduction and identification of the backlash model are presented. The Hysteresis model is applied to describe backlash and is shown in Equation (8). The inverse model is presented in Equation (9) [36]: .
where δ d is the desired output of the EMA system, ∆(τ − t) is Dirac function, which compensates the backlash instantaneously when the backlash is 2iB, i is the reduction ratio.
The schematic diagrams of the Hysteresis and Hysteresis inverse model are shown in Figure 6. The backlash characteristic is shown in Figure 6a. The backlash inverse shown in Figure 6b is used to cancel the effect of the backlash [16]. Introduction and identification of the backlash model are presented. The Hysteresis model is applied to describe backlash and is shown in Equation (8). The inverse model is presented in Equation (9) [36]: , where d δ is the desired output of the EMA system, ( ) t τ Δ − is Dirac function, which compensates the backlash instantaneously when the backlash is 2iB , i is the reduction ratio.
The schematic diagrams of the Hysteresis and Hysteresis inverse model are shown in Figure 6. The backlash characteristic is shown in Figure 6a. The backlash inverse shown in Figure 6b is used to cancel the effect of the backlash [16]. The total length of the screw is 40 mm, and the total length of the nut is 16 mm. Thus, the nut needs to move 24 mm, since the backlash is different at each point, with eight points of 10 mm, 12 mm, 14 mm, 16 mm, 18 mm, 20 mm, 22 mm, 24 mm. They are set to measure the backlash. Finally, the average value of the backlash, obtained above, is the system backlash. The test bench shown in Figure 4 is applied to implement the experiment to measure the backlash. Finally, the system backlash is obtained by collecting and processing the position information.
The backlash is measured in the following steps. Firstly, rotate the motor in a clockwise direction until the nut cannot be rotated due to reaching the bracket wall. Here, the backlash is eliminated. Meanwhile, stop rotating the motor, and the value of the potentiometer is recorded at this position. Secondly, fix the output shaft of the EMA system using the chucking appliance, and then rotate the motor in an anticlockwise direction with a slow speed. The potentiometer records the position at that moment. The difference between the position at that moment and the position of the last time is the backlash at this The total length of the screw is 40 mm, and the total length of the nut is 16 mm. Thus, the nut needs to move 24 mm, since the backlash is different at each point, with eight points of 10 mm, 12 mm, 14 mm, 16 mm, 18 mm, 20 mm, 22 mm, 24 mm. They are set to measure the backlash. Finally, the average value of the backlash, obtained above, is the system backlash. The test bench shown in Figure 4 is applied to implement the experiment to measure the backlash. Finally, the system backlash is obtained by collecting and processing the position information.
The backlash is measured in the following steps. Firstly, rotate the motor in a clockwise direction until the nut cannot be rotated due to reaching the bracket wall. Here, the backlash is eliminated. Meanwhile, stop rotating the motor, and the value of the potentiometer is recorded at this position. Secondly, fix the output shaft of the EMA system using the chucking appliance, and then rotate the motor in an anticlockwise direction with a slow speed. The potentiometer records the position at that moment. The difference between the position at that moment and the position of the last time is the backlash at this point. The backlash of the different point is measured by the above method. Finally, the average of the backlash is 0.142 • , namely the system backlash.

Controller Design
The control block diagram of the EMA system is illustrated in Figure 7. Improved ADRC is used for speed loop control and LuGre model compensation, and Hysteresis inverse model compensation is utilized for controller design. Both of them comprise the compound controller. Friction compensation is carried out by feedback. Backlash compensation is based on the idea of inverse compensation by feedforward.
ADRC is used for speed loop control and LuGre model compensation, and Hysteresis inverse model compensation is utilized for controller design. Both of them comprise the compound controller. Friction compensation is carried out by feedback. Backlash compensation is based on the idea of inverse compensation by feedforward.
The improved ADRC is established by employing a proportional integral (PI) controller, LESO, and Fal function filter. Figure 8 shows the components of the improved ADRC. In Figure 8, r is the reference input, f is the disturbance, ( ) u t is the reference signal, ( ) y t is the system output. ω is the angular velocity of the system.

LESO
The LESO estimates the state variables and the unknown disturbances of the system, including internal disturbance [37], including variation of parameters, back electromotive forces, torque ripples unmodeled dynamics, and the external disturbance, such as load disturbances of the EMA system.
These disturbances may affect the performance of the system. The state equation is as follows: where 1 All the disturbances can be taken as f . The improved ADRC is established by employing a proportional integral (PI) controller, LESO, and Fal function filter. Figure 8 shows the components of the improved ADRC.
ADRC. In Figure 8, r is the reference input, f is the disturbance, signal, ( ) y t is the system output. ω is the angular velocity of the

LESO
The LESO estimates the state variables and the unknown distu including internal disturbance [37], including variation of paramete forces, torque ripples unmodeled dynamics, and the external dist disturbances of the EMA system.
These disturbances may affect the performance of the system. as follows: All the disturbances can be take In Figure 8, r is the reference input, f is the disturbance, u(t) is the reference signal, y(t) is the system output. ω is the angular velocity of the system.

LESO
The LESO estimates the state variables and the unknown disturbances of the system, including internal disturbance [37], including variation of parameters, back electromotive forces, torque ripples unmodeled dynamics, and the external disturbance, such as load disturbances of the EMA system.
These disturbances may affect the performance of the system. The state equation is as follows: All the disturbances can be taken as f . Based on the pole placement (pole placement can be used to achieve the regulation), all the observer poles are placed at ω 0 . z 1 and z 2 are the observer state variables. The LESO is shown in Equation (11) [38,39].
The control design problem is to process a double integral system. The control law is as follows: where K ps and K is are the proportional gain and the integral gain of the speed loop, respectively.

Fal Function Filter
The fitting curve of the Fal function [40] is presented in Figure 9. It implies that the larger the error between input and output, the smaller the gain, and vice versa [41]. The Fal function filter is as follows: A comparison of unit step response with band-limited white noise power of between the system with the filter and the system without the filter is executed to va the performance of the Fal function filter. The filter parameters are: k = 1000, δ = 0. 0.5. Figure 10 shows the error comparison for the filter performance. The standard d tion of the error between the reference input and the actual system output are 0.1721 0.0612°, respectively. The result shows that this Fal function filter has a good perform of state tracking for the system with noise.  A comparison of unit step response with band-limited white noise power of 0.003 between the system with the filter and the system without the filter is executed to validate the performance of the Fal function filter. The filter parameters are: k = 1000, δ = 0.8, α = 0.5. Figure 10 shows the error comparison for the filter performance. The standard deviation of the error between the reference input and the actual system output are 0.1721 • and 0.0612 • , respectively. The result shows that this Fal function filter has a good performance of state tracking for the system with noise.

Parameter Tuning for the Controller
This part of the paper outlines a method to tune the controller parameters. Controller parameters can be generally obtained by trial and error. Empirical methods may become unworkable if physical systems are complex or too expensive. Here, NSGA-II with multiple constraints handling, is adopted to optimize the improved ADRC parameters.
The objectives include overshoot, integrated time and absolute error (ITAE), and rise time. Overshoot and rise time are performance indexes of step response, and they are

Parameter Tuning for the Controller
This part of the paper outlines a method to tune the controller parameters. Controller parameters can be generally obtained by trial and error. Empirical methods may become unworkable if physical systems are complex or too expensive. Here, NSGA-II with multiple constraints handling, is adopted to optimize the improved ADRC parameters.
The objectives include overshoot, integrated time and absolute error (ITAE), and rise time. Overshoot and rise time are performance indexes of step response, and they are chosen as objectives to be minimized. ITAE as an optimal controller index is regarded as an objective to be minimized. According to the control strategy, the improved ADRC has the following input parameters: K ps , K is , ω 0 , k, α, δ. The multi-objective optimization problem is posed in Equation (14). (14) where e(t) is the error between the system's input and the system's output. J represents ITAE, here the unit of J is set as s · rpm. t r represents the rise time, Mp represents overshoot. Thus, the controller parameters are tuned by NSGA-II so that the performance indexes Fitness1, Fitness2, and Fitness3 are all minimized. The steps are as follows: give a certain initial value and corresponding range of controller parameters, and then combine them into different combinations of controller parameters. Using these controller parameters to control the system, take the step response as the evaluation standard to obtain Fitness1, Fitness2, and Fitness3. If Fitness1, Fitness2, and Fitness3 meet the requirements under the current parameter control, stop the system and record the controller combination under the current state, that is, the optimal controller parameters. If Fitness1, Fitness2, and Fitness3 are not the minimum, continue to simulate until the required simulation results are obtained.
The NSGA-II is an improved approach of the genetic algorithm (GA) for the multiobjective optimization of process responses. Non-dominated solutions of NSGA-II have high crowding distance, which are used to provide diversified Pareto optimal solutions. A Pareto optimal solution cannot be improved with respect to any objective without worsening at least one other objective [42]. The set of feasible non-dominated solutions in the solution space is referred to as the Pareto optimal set. The NSGA-II encompasses advanced concepts like elitism, fast non-dominated sorting, and diversity maintenance along the Pareto optimal front. The flowchart of the NSGA-II is shown in Figure 11. Figure 12 shows the optimization procedure of tuning improved the ADRC parameters, in order to investigate the effectiveness of NSGA-II for the improved ADRC. The population size and maximum generation numbers are set as 12 and 20, respectively. The crossover probability is 0.7, and mutation probability is 0.001. Further, a 1000 rpm step input signal, including band-limited white noise with noise power 0.0003, is given as the command. The Pareto front for triple objective optimization is shown in Figure 13. It can be seen from Figure 13 that green points express the Pareto solution. The optimal parameters and the corresponding optimized values of the objective functions, obtained above, are presented in Table 3. It can be seen from Table 3, that the overshoot is 7.01%, ITAE is 0.43, the rise time is 0.0024 with the optimized parameters. The step response of the EMA system adopting improved ADRC with optimal controller parameters is given in Figure 14. Hence, it can be concluded that the optimal parameters are feasible. solution space is referred to as the Pareto optimal set. The NSGA-II encompasses ad vanced concepts like elitism, fast non-dominated sorting, and diversity maintenance along the Pareto optimal front. The flowchart of the NSGA-II is shown in Figure 11.  Figure 12 shows the optimization procedure of tuning improved the ADRC parame ters, in order to investigate the effectiveness of NSGA-II for the improved ADRC. The population size and maximum generation numbers are set as 12 and 20, respectively. The crossover probability is 0.7, and mutation probability is 0.001. Further, a 1000 rpm step input signal, including band-limited white noise with noise power 0.0003, is given as the command. The Pareto front for triple objective optimization is shown in Figure 13. It can be seen from Figure 13 that green points express the Pareto solution. The optimal param eters and the corresponding optimized values of the objective functions, obtained above are presented in Table 3. It can be seen from Table 3, that the overshoot is 7.01%, ITAE is 0.43, the rise time is 0.0024 with the optimized parameters. The step response of the EMA system adopting improved ADRC with optimal controller parameters is given in Figure  14. Hence, it can be concluded that the optimal parameters are feasible.      Figure 14.
Step response comparison of 1000 rpm speed input.
The results show that this approach presents a perfect solution for optimizing the controller parameters of the proposed controller with multiple constraints. The results show that this approach presents a perfect solution for optimizing the controller parameters of the proposed controller with multiple constraints.

Simulation Results
The simulation model plays a key role in analyzing the control system design. Based on the above analysis, the performances of the PI controller and proposed controller are compared in the EMA system. The overall simulation model of the EMA system has been prepared in MATLAB/Simulink, used to establish the model of the EMA system. The adopted controllers of the position loop for the two speed loops are PI controllers. Figure 15 shows the sine wave response for the PI controller and proposed controller. It is seen from Figure 15 that the PI controller cannot deal with the phenomenon of the speed dead zone and position flattening, when the system speed tends to 0, but the new compound controller can solve this problem well. It can be seen that the proposed controller effectively suppresses the nonlinear factors.

Figure 14.
Step response comparison of 1000 rpm speed input.
The results show that this approach presents a perfect solution for optimizing th controller parameters of the proposed controller with multiple constraints.

Simulation Results
The simulation model plays a key role in analyzing the control system design. Base on the above analysis, the performances of the PI controller and proposed controller ar compared in the EMA system. The overall simulation model of the EMA system has bee prepared in MATLAB/Simulink, used to establish the model of the EMA system. Th adopted controllers of the position loop for the two speed loops are PI controllers. Figure 15 shows the sine wave response for the PI controller and proposed controlle It is seen from Figure 15 that the PI controller cannot deal with the phenomenon of th speed dead zone and position flattening, when the system speed tends to 0, but the new compound controller can solve this problem well. It can be seen that the proposed con troller effectively suppresses the nonlinear factors.

Disturbance Rejection Ability Verification
To validate the disturbance rejection ability, a step signal with an amplitude 200 rpm is set as the input of the system. A step disturbance is also added to the system at 0.01 s. The response curve is shown in Figure 16. It is seen from Figure 16 that the rise time and overshoot by the proposed controller are shorter than the conventional PI controller. The peak value and the tuning time of the disturbance by the proposed controller are better than the PI controller. It can be seen that the proposed controller can effectively improve the anti-disturbance ability of the system, on the premise of ensuring the dynamic characteristics of the system. overshoot by the proposed controller are shorter than the conventional PI controller. peak value and the tuning time of the disturbance by the proposed controller are be than the PI controller. It can be seen that the proposed controller can effectively impr the anti-disturbance ability of the system, on the premise of ensuring the dynamic cha teristics of the system. Step response with disturbance.

Experiment Testing
As discussed in the preceding section, the PI controller and the proposed compo controller are applied to the EMA system. The sample time is 1 ms, and the controll carried out on a Digital Signal Processing chip (DSP). The experimental facility of the E system is illustrated in Figure 17. A host PC is used as the upper computer to record monitor the system in real time. The simulator is used to download the program to DSP. The torsional spring is used as the load torque of the EMA surface. The oscillosc is used to monitor the output of the digital signals. The sine wave response is illustrated in Figure 18. The input of the sine is 0. (0.9πt). It can be seen from Figure 18 that, compared with the system controlled by th controller, there is a shorter position flat crest and smaller speed dead zone by the posed controller of the system output. Under the action of the proposed controller, Step response with disturbance.

Experiment Testing
As discussed in the preceding section, the PI controller and the proposed compound controller are applied to the EMA system. The sample time is 1 ms, and the controller is carried out on a Digital Signal Processing chip (DSP). The experimental facility of the EMA system is illustrated in Figure 17. A host PC is used as the upper computer to record and monitor the system in real time. The simulator is used to download the program to the DSP. The torsional spring is used as the load torque of the EMA surface. The oscilloscope is used to monitor the output of the digital signals. teristics of the system. Step response with disturbance.

Experiment Testing
As discussed in the preceding section, the PI controller and the proposed controller are applied to the EMA system. The sample time is 1 ms, and the c carried out on a Digital Signal Processing chip (DSP). The experimental facility system is illustrated in Figure 17. A host PC is used as the upper computer to monitor the system in real time. The simulator is used to download the prog DSP. The torsional spring is used as the load torque of the EMA surface. The o is used to monitor the output of the digital signals. The sine wave response is illustrated in Figure 18. The input of the sin (0.9πt). It can be seen from Figure 18 that, compared with the system controlle controller, there is a shorter position flat crest and smaller speed dead zone posed controller of the system output. Under the action of the proposed con The sine wave response is illustrated in Figure 18. The input of the sine is 0.9sin (0.9πt). It can be seen from Figure 18 that, compared with the system controlled by the PI controller, there is a shorter position flat crest and smaller speed dead zone by the proposed controller of the system output. Under the action of the proposed controller, the system output effectively suppresses the influence of friction and backlash nonlinearity. The comparison results are shown in Table 4. In addition, the noise effect is also alleviated by the proposed controller. Thus, the performance of the proposed controller is better than the PI controller. system output effectively suppresses the influence of friction and backlash nonlinearity. The comparison results are shown in Table 4. In addition, the noise effect is also alleviated by the proposed controller. Thus, the performance of the proposed controller is better than the PI controller.  Since the EMA system deflections are limited to ±15°, the performance comparisons of the tracking angular position, from ±1° to ±15°, by different controllers, are shown in Figure 19. Equivalent load torque is added to the EMA system using a torsional spring, which can be regarded as the disturbance. The elastic coefficient of the torsional spring is 0.62 N·m/°. It can be seen from Figure 19 that the PI controller has a long tuning time and a large overshoot, while the proposed controller has a small overshoot and a short tuning time. Taking the response of ±1° and ±15° as examples, the comparison data are shown in Table 5. For the four positions ±1° and ±15°, the three indexes of the proposed controller (tr, Mp, standard deviation) are smaller than the PI controller. It can be seen from the experiments that the proposed controller shows useful properties of good performance and robustness compared with the PI controller.    18 22 Since the EMA system deflections are limited to ±15 • , the performance comparisons of the tracking angular position, from ±1 • to ±15 • , by different controllers, are shown in Figure 19. Equivalent load torque is added to the EMA system using a torsional spring, which can be regarded as the disturbance. The elastic coefficient of the torsional spring is 0.62 N·m/ • . It can be seen from Figure 19 that the PI controller has a long tuning time and a large overshoot, while the proposed controller has a small overshoot and a short tuning time. Taking the response of ±1 • and ±15 • as examples, the comparison data are shown in Table 5. For the four positions ±1 • and ±15 • , the three indexes of the proposed controller (t r , M p , standard deviation) are smaller than the PI controller. It can be seen from the experiments that the proposed controller shows useful properties of good performance and robustness compared with the PI controller. Step response curve of tracking angular position by different controllers in speed loop.

Conclusions
In this paper, the compound scheme, based on improved ADRC and nonlinear compensation, is developed for the EMA system. The influences of backlash and friction on the EMA system are considered in this paper. The LuGre model and Hysteresis inverse model are used to compensate for the friction and backlash phenomenon, respectively.

Conclusions
In this paper, the compound scheme, based on improved ADRC and nonlinear compensation, is developed for the EMA system. The influences of backlash and friction on the EMA system are considered in this paper. The LuGre model and Hysteresis inverse model are used to compensate for the friction and backlash phenomenon, respectively. The improved ADRC, based on the Fal function filter and LESO, is investigated. The non-dominated sorting genetic algorithm II (NSGA-II) is presented to optimize the controller parameters, to achieve the best dynamic response. Simulations and experiments are presented to validate the effectiveness of the proposed method. As shown in Figures 18 and 19, Tables 4 and 5, the experimental results of the improved ADRC, with nonlinear compensation, indicate that rise time, overshoot and the steady state standard deviation of the EMA system are all improved by the proposed controller. In summary, it can be seen from the obtained results that the proposed controller has a quick response, slight overshoot, and strong anti-disturbance ability. Thus, the dynamic performance and steady precision of the system are both improved. Although the proposed controller does have some advantages, the proposed controller also requires some improvements. For example, how to make the system performance evaluation standard more perfect and reduce the controller parameters through the optimization algorithm are also very worthy of research.