Volume 15 Number 4
August 2018
Article Contents
Chang-Fan Zhang, Yuan-Yuan Xiao, Jing He and Min Yan. Improvement of Electronic Line-shafting Control in Multi-axis Systems. International Journal of Automation and Computing, vol. 15, no. 4, pp. 474-481, 2018. doi: 10.1007/s11633-016-1031-1
Cite as: Chang-Fan Zhang, Yuan-Yuan Xiao, Jing He and Min Yan. Improvement of Electronic Line-shafting Control in Multi-axis Systems. International Journal of Automation and Computing, vol. 15, no. 4, pp. 474-481, 2018. doi: 10.1007/s11633-016-1031-1

Improvement of Electronic Line-shafting Control in Multi-axis Systems

Author Biography:
  • Chang-Fan Zhang   received the M.Sc. degree from Southwest Jiaotong University China in 1989, and the Ph.D.degree from Hunan University, China in 2001.He is currently a professor at College of Electrical and Information Engineering, Hunan University of Technology, China.
      His research interests include fault diagnosis on electric machines and industrial process control.
      E-mail:zhangchangfan@263.net

    Yuan-Yuan Xiao   graduated from Hunan University of Technology, China in 2011.She is currently a master student at the College of Electrical and Information Engineering, Hunan University of Technology, China.
      Her research interest is fault diagnosis on electric machines
      E-mail:xiaoyy3690@sina.com

    Min Yan   graduated from Hunan University of Technology, China in 2011.She is currently a master student at the College of Electrical and Information Engineering, Hunan University of Technology, China.
      Her research interest is fault diagnosis on electric machines
      E-mail:yanminhuixiao@163.com

  • Corresponding author: Jing He   received the M.Sc.degree from Central South University of Forestry and Technology, China in 2002, and the Ph.D. degree from National University of Defense Technology, China in 2009.She is currently a professor at the College of Electrical and Information Engineering, Hunan University of Technology, China.
      Her research interests include fault diagnosis on mechatronics and industrial process control.
      E-mail:hejing@263.net (Corresponding author)
      ORCID iD:0000-0002-3650-3270
  • Received: 2014-02-27
  • Accepted: 2014-05-13
  • Published Online: 2016-09-02
通讯作者: 陈斌, bchen63@163.com
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Improvement of Electronic Line-shafting Control in Multi-axis Systems

  • Corresponding author: Jing He   received the M.Sc.degree from Central South University of Forestry and Technology, China in 2002, and the Ph.D. degree from National University of Defense Technology, China in 2009.She is currently a professor at the College of Electrical and Information Engineering, Hunan University of Technology, China.
      Her research interests include fault diagnosis on mechatronics and industrial process control.
      E-mail:hejing@263.net (Corresponding author)
      ORCID iD:0000-0002-3650-3270

Abstract: Electronic line-shafting (ELS) is the most popular control strategy for printing machines with shaftless drives. A slidingmode controller for tracking control is designed in this study as the first step towards an improved ELS control scheme. This controller can eliminate the negative effects on synchronization precision resulting from the friction at low speed present in the pre-registration step of a shaftless driven printing machine. Moreover, it can eliminate the synchronization error of the printing process resulting from nonlinearities and load disturbances. Based on observer techniques, the unknown components of load torque and system parameter variations are estimated. On this basis, a novel ELS control method using equivalent load-torque observers is proposed. Experimental results demonstrate the effectiveness of the proposed control system for four-axis position control.

Chang-Fan Zhang, Yuan-Yuan Xiao, Jing He and Min Yan. Improvement of Electronic Line-shafting Control in Multi-axis Systems. International Journal of Automation and Computing, vol. 15, no. 4, pp. 474-481, 2018. doi: 10.1007/s11633-016-1031-1
Citation: Chang-Fan Zhang, Yuan-Yuan Xiao, Jing He and Min Yan. Improvement of Electronic Line-shafting Control in Multi-axis Systems. International Journal of Automation and Computing, vol. 15, no. 4, pp. 474-481, 2018. doi: 10.1007/s11633-016-1031-1
  • High-precision synchronization control technology is extensively used in manufacturing industries such as printing, aerospace, textile, and steel rolling[1-3]. The higher precision design of it for system with nonlinearity and disturbances is the key to its application in manufacturing.

    Traditional synchronization control strategies include master-slave control, cross-coupling control, relative-coupling control, and electronic line-shafting (ELS) control[4]. As a typical one among them, ELS is extensively used in engineering application due to its excellent synchronization performance[5, 6]. Lorenz[7] conducted extensive research in this area, and Payette[8, 9] also made contributions in ELS development. Valenzuela and Lorenz[10] described the physical meaning of ELS and applied it to printing machines. Based on the previous achievements, Perez[11] extended the study of ELS control strategy and perfected the ELS algorithm, Wolf and Lorenz[12] proposed compensation-based ELS control to eliminate the effect of tension on printing paper. Furthermore, improved tracking-control algorithms were developed to increase the synchronization precision of multi-axis systems[13, 14].

    In a multi-axis motion system, synchronization is required in the case of load variation. Because the real load torque is time-varying and not measurable, existing ELS-based control strategies take the virtual load torque (i.e., the coupling torque) of each axis as their load torque "feedback". These feedback signals act together on the virtual shaft to form a coordinated signal for the motion synchronization of all the axes. Under steady-state conditions, this feedback control can provide excellent synchronization performance. However, if a severe unknown load disturbance occurs in the system, loss of synchronization among the axes probably happens. To address this problem, a novel ELS control strategy is proposed in this paper. By constructing an observer, the equivalent load torque is observed, and the observed value is directly fed back to the virtual shaft.

    The paper is organized as follows: Section 2 describes a direct current (DC) motor system. Section 3 introduces the traditional ELS control method. Section 4 presents a novel ELS structure. Section 5 describes the control design. Section 6 presents experimental results and conclusions in Section 7.

  • Synchronous coordinated running of each printing roller of a shaftless-driven printing press is accomplished mainly by independent-drive servo motors. Register control is carried out if chromatic aberration occurs. This control scheme results in fast, accurate, and steady control of the system with respect to object position and velocity. There are many models of servo drive motors. But to reflect a practical implementation more precisely, it is desirable to take parameter variation, friction, and load torque into consideration in the model. Therefore, a DC motor is selected as the servo motor type. The dynamic system can be described by

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot x_1 {\rm{ = }}x_2 \\ \dot x{}_2{\rm{ = - }}\dfrac{{k_m c_e }}{{JR}}x_2 {\rm{ + }}k_u \dfrac{{k_m }}{{JR}}u(t){\rm{ - }}\dfrac{1}{J}F_f {\rm{(}}t{\rm{) - }}\dfrac{1}{J}{\rm{T}}_L \\ \end{array} \right. \end{eqnarray} $

    (1)

    where $x_1=\theta$ is the angular position, $x_2=\omega$ is the angular velocity, $c_e$ is the voltage feedback coefficient, $J$ is the inertia, $R$ is the total armature resistance, $k_m$ is the electromechanical torque coefficient, $k_u$ is the pulse-width modulation (PWM) coefficient of amplification of the power amplifier, $u(t)$ is the control input, $T_L$ is the load torque, and ${F_f}(t)$ is the friction. The mathematical model of ${F_f}(t)$ can be expressed as follows[15]:

    When $\left| {\dot \theta } \right|{\rm{ < }}\sigma _1$ , the static friction is

    $ \begin{eqnarray} F_f {\rm{(}}t{\rm{) = }}\left\{ \begin{array}{l} F_m \begin{array}{*{20}c} {},&{\rm if}\quad {F_t > F_m } \\ \end{array} \\ F_t^{} \begin{array}{*{20}c} {},&{\rm if}\quad {{\rm{ - }}F_m {\rm{ < }}F < F_m } \\ \end{array} \\ {\rm{ - }}F_m \begin{array}{*{20}c} {},&{\rm if}\quad {F_t {\rm{ < - }}F_m }. \\ \end{array} \\ \end{array} \right. \end{eqnarray} $

    (2)

    When $\left| {\dot \theta } \right|{\rm{ > }}\sigma _1 $ , the dynamic friction is

    $ \begin{eqnarray} F_f {\rm{(}}t{) = [F}_c {\rm{ + (}}F_m {\rm{ - }}F_c {\rm{)}}{\rm e}^{{\rm{ - }}\sigma _2 \left| {\dot \theta } \right|} {\rm{]}}{\mathop{\rm sgn}} {\rm{(}}\dot \theta {\rm{) + }}k_v \dot \theta. \end{eqnarray} $

    (3)

    While the driving force $F(t)$ is

    $ \begin{eqnarray} F(t) = J \ddot \theta \end{eqnarray} $

    (4)

    where $F_m$ is the maximum static friction, $F_c$ is the coulomb friction, $k_v$ is the proportionality factor for viscous friction torque, and $\sigma_1$ and $\sigma_2$ are very small positive constants.

    It is assumed that $ \overline {a_1 } {\rm{ = - }}\frac{{k_m c_e }}{{JR}} $ , $ \overline b {\rm{ = }}\frac{{k_u k_m }}{{JR}} $ and $ \overline {a_2 } {\rm{ = - }}\frac{1}{J} $ are three nomimal values. Considering parameter variation, (1) can be rewritten as

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot x_1 = x_2 \\ \dot x_2 = a_1 x_2 { + b}u(t){\rm{ + }}a_2 F_f {\rm{(}}t{\rm{) + }}a_2 {\rm{T}}_L \\ \end{array} \right. \end{eqnarray} $

    (5)

    where $ a_1 {\rm{ = }}\overline {a_1 } {\rm{ + }}\Delta a_1 $ , $ b{\rm{ = }}\overline b {\rm{ + }}\Delta b $ , $ a_2 {\rm{ = }}\overline {a_2 } {\rm{ + }}\Delta a_2 $ , $ \Delta a_1 $ , $ \Delta b $ and $\Delta a_2$ are uncertain items caused by the variation of parameters $k_m$ , $J$ and $R$ .

    Define $T_L^ * = \Delta a_1 x_2 + \Delta bu(t) + \Delta a_2 F_f (t) + a_2 T_L$ as the equivalent load torque, then (5) can be rewritten as

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot x_1 = x_2 \\ \dot x_2 = \bar a_1 x_2 + \bar bu(t) + \bar a_2 F_f (t) + T_L^ * .\\ \end{array} \right. \end{eqnarray} $

    (6)
  • The mechanical shaft driven system provides power to each individual servo drive unit by means of a mechanical shaft and maintains their motion synchronization simultaneously. In the ELS control strategy, a virtual shaft is used to replace the mechanical shaft by realistically simulating its physical characteristics. Each axis follows the motion of the virtual shaft and couples with it by torque integration and feedback. When the signal from the virtual shaft control system is applied to the mechanical shaft, a reference signal for each unit controller is obtained. In other words, the reference input signal, instead of the system input signal, is synchronized among all unit controllers. Because it is a filtered signal applied to the shaft, it can be tracked more easily by the unit controllers, and can improve synchronization performance. The ELS control structure is shown in Fig. 1.

    Figure 1.  Structure of traditional ELS system

    Fig. 1 shows that the virtual electric line shaft, known as the master, involves the adjustment of shaft velocity or position and provides the velocity or position reference value to its slaves. Under steady-state conditions, every axis follows the virtual shaft, and excellent synchronization performance can be achieved. If one or more axes deviate from the reference value due to a disturbance, torque integration and feedback enables the virtual shaft to sense this variation and produce an adjusted reference value for the other slaves. In this manner, synchronization is always achieved among the axes. The torque balancing equation is

    $ \begin{eqnarray} T{\rm{ - }}\sum T_i {\rm{ = }}J_m \ddot \theta_m \end{eqnarray} $

    (7)

    where $T$ , $J_m$ , $\theta_m$ are the driving torque, the inertia and the angular position of the virtual shaft, respectively, $T_i$ $ (i{\rm{ = }}1{\rm{, }}2{\rm{, }} \cdots, n) $ is the feedback restoring torque from each physical axis, namely, virtual load torque. Payette defined virtual load torque as[8]

    $ \begin{eqnarray} T_i = b_r \Delta \omega + k_r \Delta \theta + k_{ir} \int {\Delta \theta {\kern 1pt} {\kern 1pt} {\rm d}t} \end{eqnarray} $

    (8)

    where $b_r$ is the damping gain, $k_r$ is the stiffness gain, $k_{ir}$ is the integrated stiffness, $\Delta\omega$ is the angular velocity error, and $\Delta\theta$ is the angular position error.

  • Because the load torque of the servo drive $T_{li}$ $( i{\rm{ = }}1{\rm{, }} 2{\rm{, }} \cdots, n) $ is time-varying and unpredictable, the traditional ELS control strategy integrates the virtual load torque of each axis $T_i$ $( i{\rm{ = }}1{\rm{, }}2{\rm{, }} \cdots, n) $ as the torque feedback on virtual shaft, with which the motion synchronization is harmonized among axes. This virtual load torque is obtained by calculating the virtual stiffness gain and damping gain with the error between the system reference value and the actual output value (velocity or position error). Under steady-state conditions, the system error can be eliminated by properly designing the tracking controller of each axis. However, if a severe load disturbance occurs in the system, asynchronization probably happens among the axes due to the time delay caused by calculation of the virtual load torque. To solve this problem, a load observer is designed in this research, and the observed value is taken as the torque fed back to virtual shaft for the motion synchronization among the axes. This way reflects the dynamic relationship among the axes in a more precise manner. In this case, the torque balancing equation is

    $ \begin{eqnarray} T{\rm{ - }}\sum \hat T_{Li}^ * {\rm{ = }}J_m \ddot \theta _m \end{eqnarray} $

    (9)

    where $ \hat T_{Li}^ * $ $( i{\rm{ = }}1, 2, \cdots, n )$ is the estimation value of the equivalent load torque. A block diagram of the improved ELS control topology is shown in Fig. 2.

    Figure 2.  Structure of improved ELS system

  • Fig. 2 shows that every servo drive unit under the control of virtual shaft has symmetric structure. Therefore, the same control algorithm can be applied to each of them. Taking axis 1 for example, the design of a tracking controller and an equivalent load-torque observer for servo motor No. 1 is described in this section.

  • For a shaftless driven printing machine, each paper roller is driven by an independent servo motor, and in case of chromatic aberration, register control is carried out. These lead to higher requirements on multi-axis synchronization control in which the driving motor is considered as a complex object with nonlinear and variable parameters. With common PID control, satisfactory speed regulation and positioning are hard to achieve due to the weak robustness to disturbances and parameter variations.

    In contrast, with the sliding-mode variable structure control, a type of nonlinear and discontinuous control, the system is capable to obtain excellent robustness which is actually called invariability through keeping motion within sliding surface[16]. Together with its simplicity, high real-time performance, and easy implementation, this method applied to high-precision tracking control has attracted significant attention[17]. This section describes the design of a sliding-mode controller for a single-axis system which guarantees not only the excellent tracking performance but also the high performance of observer. Moreover, it is also applicable to a multi-axis system with symmetrical motors.

    As shown in Fig. 2, $\theta_m$ is the reference position of axis 1, and (1) shows that $ x_1 = \theta _1 $ , thus the tracking error can be $ e = \theta _m - x_1 $ .

    Choose the linear sliding surface

    $ \begin{eqnarray} s = ce + \dot e \end{eqnarray} $

    (10)

    where $c$ indicates the slope of the sliding surface and is a positive constant need to be designed.

    The output of the sliding mode controller can be obtained from $(6)$ and $(10)$ so that

    $ \begin{align} u(t) = \frac{1}{{\bar b}}_{_{} } \left[ {c\dot e + \ddot \theta _m + \beta (x, t){\mathop{\rm sgn}} (s) + ks - \bar a_1 x_2 - \bar a_2 F_f (t)} \right] \end{align} $

    (11)

    where $k$ is a positive constant and $\beta(x, t)$ is the switched gain. Both of them need to be designed. ${\rm sgn} (\cdot)$ is the signum.

    Assume that $ T_L^ * $ is unknown but bounded and subject to $ \left| {T_L^ * } \right| \le M $ , where the positive constant $M$ is known.

    If design

    $ \begin{eqnarray} \beta (x, t) = M + \eta \end{eqnarray} $

    (12)

    then $ s\dot s = - \eta \left| s \right| - ks^2 \le 0 $ , which means that the reachability condition is satisfied, and a sliding mode motion on $s$ is attainable in finite time, where $\eta$ is also a positive constant.

    A sigmoid function $\lambda(s)$ is used instead of the signum function ${\rm sgn}(s)$ as the switching function in order to reduce the effect of chattering which occurs on the sliding surface[18]. The sigmoid function is defined as

    $ \begin{eqnarray} \lambda {\rm{(}}s{\rm{) = }}\frac{2}{{1 + {\rm e}^{ - as} }} - 1 \end{eqnarray} $

    (13)

    where $a$ is a positive constant used to regulate the slope of the sigmoid function.

  • From (6), the sliding mode observer is designed as

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot {\hat x}_1 = \hat x_2 + v_1 \\ v_1 = L_1 {\mathop{\rm sgn}} (x_1 - \hat x_1 ) \\ \end{array} \right. \end{eqnarray} $

    (14)

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot{\hat x}_2 = \bar a_1 \hat x_2 + \bar bu(t) + \bar a_2 F_f (t) + v_2 \\ v_2 = L_2 {\mathop{\rm sgn}} (x_2 - \hat x_2 ) \\ \end{array} \right. \end{eqnarray} $

    (15)

    where $L_1$ and $L_2$ are two positive constants to be designed later.

    Define the estimation errors of the observer as

    $ \begin{eqnarray} \left\{ \begin{array}{l} e_1 = x_1 - \hat x_1 \\ e_2 = x_2 - \hat x_2. \\ \end{array} \right. \end{eqnarray} $

    (16)

    From $(6)$ , (14) $-$ (16), the error equation can be obtained as

    $ \begin{eqnarray} \left\{ \begin{array}{l} \dot e_1 = e_2 - v_1 \\ \dot e_2 = \bar a_1 e_2 + T_L^ * - v_2 . \\ \end{array} \right. \end{eqnarray} $

    (17)

    Proposition 1. Consider the system described by (6) and its observers described by (14) and (15). If $L_1$ and $L_2$ are sufficiently large, then the estimated equivalent load torque can be obtained by $\hat T_L^ * = L_2 {\mathop{\rm sgn}} \left[ {L_1 {\mathop{\rm sgn}} e_1 } \right]$ .

    Proof.

    The first step: Define the sliding surface

    $ \begin{eqnarray} s_1 = e_1 \end{eqnarray} $

    (18)

    The second step: Choose the Lyapunov function $ V_1 = \frac{1}{2}e_1^2$ .

    Along the trajectory of system (17), the derivative of the Lyapunov function with respect to time is

    $ \begin{eqnarray} &\dot V_1 = e_1 \dot e_1 = e_1 e_2 - e_1 v_1 =\notag\\ &\qquad e_1 e_2 - e_1 L_1 {\mathop{\rm sgn}} e_1 =\notag\\ &\;\; e_1 e_2 - L_1 \left| {e_1 } \right| \le\notag\\ &\qquad\left| {e_1 } \right|\left| {e_2 } \right| - L_1 \left| {e_1 } \right| =\notag\\ &\left| {e_1 } \right|\left[ {\left| {e_2 } \right| - L_1 } \right]. \end{eqnarray} $

    (19)

    When $ L_1 \ge \left| {e_2 } \right| $ by design, there is $ \dot V_1 \le 0 $ , i.e., $ s_1 \dot s_1 \le 0 $ . It means that the reachability condition is satisfied, and a sliding-mode motion on $s_1$ is attained in finite time. According to the equivalence principle of the sliding-mode theory, it follows that

    $ \begin{eqnarray} s_1 = \dot s_1 = 0. \end{eqnarray} $

    (20)

    Then, from (14) $-$ (18), $(20)$ ,

    $ \begin{eqnarray} e_2 = L_1 {\mathop{\rm sgn}} e_1. \end{eqnarray} $

    (21)

    Now $e_2$ can be expressed using (21).

    The third step: Define the sliding surface

    $ \begin{eqnarray} s_2 = e_2. \end{eqnarray} $

    (22)

    The fourth step: Choose the Lyapunov function $ V_2 = \frac{1}{2}(e_1^2 + e_2^2 ) $ , then

    $ \begin{eqnarray} \dot V_2 = e_1 \dot e_1 + e_2 \dot e_2 = \dot V_1 + e_2 \dot e_2. \end{eqnarray} $

    (23)

    Applying the same reasoning as in the proof of the second step, we obtain $ \dot V_2 \le e_2 \dot e_2 $ .

    Then, from (17)

    $ \begin{eqnarray} \begin{array}{l} \dot V_2 \le e_2 \dot e_2 = \bar a_1 e_2^2 + \left| {e_2 } \right|\left[ {T_L^ * - L_2 } \right]= \\ {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} {\kern 1pt} \; - \left| {\bar a_1 } \right|e_2^2 + \left| {e_2 } \right|\left[ {T_L^ * - L_2 } \right]. \\ \end{array} \end{eqnarray} $

    (24)

    When $ L_2 \ge \left| {T_L^ * } \right| \ge M $ by design, there is $ s_2 \dot s_2 \le 0$ . It means that the reachability condition is satisfied and a sliding-mode motion on $s_2$ is attained in finite time. According to the equivalent principle of the sliding-mode theory, it follows that

    $ \begin{eqnarray} s_2 = \dot s_2 = 0. \end{eqnarray} $

    (25)

    The estimated value of the equivalent load torque can be obtained from (14)-(18), (23) and (25):

    $ \begin{eqnarray} \hat T_L^ * = v_2 = L_2 {\mathop{\rm sgn}} e_2 = L_2 {\mathop{\rm sgn}} \left[ {L_1 {\mathop{\rm sgn}} e_1 } \right]. \end{eqnarray} $

    (26)

    Now the load torque $T_L$ and the uncertain items caused by parameter variation can be obtained from (26).

    Based on the above analysis, the procedure of observer design for system synchronization can be summarized as follows:

    Step 1. Design the system control algorithm of a single-axis system according to (11) in order to maintain the tracking performance of the system.

    Step 2. Replace the sgn(s) in (11) with the sigmoid function in (13) in order to minimize sliding-model chattering. This chattering reduction method will be used again in the subsequent design.

    Step 3. Construct the observer according to (14) and (15) and calculate the estimated value of equivalent load torque according to (26).

    Step 4. Carry out ELS synchronization control according to Fig. 2 and (9).

  • Taking a four-axis printing machine with shaftless drive for example, a Matlab simulation model was built. Considering that in printing machine, the strong system nonlinearity only happens during the low speed pre-register stage, a low-amplitude, low-frequency sinusoidal signal $ \theta _d = 0.1\sin (2\pi t) $ rad is used as the given position signal. By choosing the nominal values of the system as $F_c=15 {\rm N} \cdot {\rm m}$ , $k_v=2.0 {\rm N \cdot m \cdot s/rad}$ , $F_m=20 {\rm N} \cdot {\rm m}$ , $\sigma_1=0.01$ and $\sigma_2=0.1$ . DC motor parameters are shown in Table 1. And the corresponding control system parameters are $c=30$ , $k=5$ , $a=50$ , $M=10$ , $\eta=10$ , $L_1=20$ and $L_2=100$ .

    Table 1.  DC motor parameters

  • Use the sinusoidal signal sin(4 $t$ ) to simulate the disturbance of system parameters $R$ and $J$ , and a 2 N step signal added on axis 1 at the moment of 1 s to simulate an abrupt load change. The position tracking results and the observed results of the equivalent load observer for a single-axis system are shown in Figs. 3 and 4, respectively. Fig. 3 shows that with the use of a sliding-mode controller, the actual system value tracks the given value rapidly accompanied by excellent system robustness, and after $t>2$ s, good tracking performance is obtained. Fig. 4 shows that the designed observed load-torque values converge within a short time. These results indicate that the control method satisfies control system requirements and lays a good foundation for multi-axis synchronization control as well.

    Figure 3.  Tracking performance of single-axis system

    Figure 4.  Estimated value of the designed observer

  • To verify the effectiveness of the method proposed in this paper, a comparative experiment was performed based on the traditional ELS control method shown in Fig. 1 and the improved ELS control method shown in Fig. 2.

    1) Synchronization performance without disturbance.

    2) Synchronization performance with disturbance.

    At 2 s, a 3 N step signal was added on axis 1 to simulate an abrupt load change.

    As Fig. 5 shows, if there is no any external disturbance, both control schemes achieve excellent tracking performance by means of well-designed controllers. However, by examining the details shown in Figs. 6 and 7, it apparently shows that taking coupling torque as the torque feedback leads to a constant deviation between the main reference value and each axis, so that the tracking error of each axis deviates from zero to the balance point. It implies that the traditional ELS achieves high tracking performance with the cost of tracking performance loss in each axis.

    Figure 5.  Tracking performance of multi-axis system without disturbance

    Figure 6.  Synchronization errors of multi-axis system without disturbance

    Figure 7.  Synchronization errors of multi-axis system with disturbance

    In contrast, the improved ELS introduces a solution based on the equivalent load torque observer. By taking the observed value of the equivalent load torque as the torque feedback, the control system can guarantee not only high synchronization performance, but also excellent tracking performance on each axis. In addition, sliding-mode variable structure keeps system operation status stable in case of disturbance. Furthermore, it plays its role on improving overall robustness, steady-state performance, and synchronization performance.

  • Focusing on improving the synchronization performance of traditional ELS control, an equivalent load observer based control strategy is proposed in this paper. First, sliding-mode controllers are designed for each axis in a multi-axis synchronization system to achieve high tracking performance and improve system resistance to disturbances. Second, the equivalent load-torque observer is designed to get the observer equivalent torque value of each axis for eliminating the constant deviation between the main reference value and each axis. This control strategy is especially helpful in maintaining synchronized motion control when severe load disturbances occur. Experimental results have demonstrated the effectiveness of the proposed control strategy for multi-axis systems when taking unexpected load disturbances into account during normal operations.

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