Summarisation, Simulation and Comparison of Nine Control Algorithms for an Active Control Mount with an Oscillating Coil Actuator

Abstract

With the further development of the automotive industry, the traditional vibration isolation method is difficult to meet the requirements for wide frequency bands under multiple operating conditions, the active control mount (ACM) is gradually paid attentions, and the control algorithm plays a decisive role. In this paper, the ACM with oscillating coil actuator (OCA) is taken as the object, and the comparative study of the control algorithms is performed to select the optimal one for ACM. Through the modelling of ACM, the design of controller and the system simulations, the force transmission rate is used to compare the vibration isolation performance of the nine control algorithms, which are least mean square (LMS) adaptive feedforward control, recursive least square (RLS) adaptive feedforward control, filtered reference signal LMS (FxLMS) adaptive control, linear quadratic regulator (LQR) optimal control, H2 control, H∞ control, proportional integral derivative (PID) feedback control, fuzzy control and fuzzy PID control. In summary, the FxLMS adaptive control algorithm has the better performance and the advantage of easier hardware implementation, and it can apply in ACMs.

Fixed Points on Active and Passive Dynamics of Active Hydraulic Mounts with Oscillating Coil Actuator

“…Thus, K2 is set to zero, and the pressure fluctuation in the lower fluid chamber is ignored and set p2 = 0 [5,7−9]. Denote the length of inertia track as l2, the cross-sectional area as A2, the wet perimeter of cross section as L2, and the hydraulic diameter as d2 = Referring to the hydraulic mount mechanical models [5][6][7][8][9], a unified lumped parameter mechanical model for AHM-IT-DM and PHM-IT-DM is built, as shown in Figure 2. The displacement of the engine side is y 1 and the corresponding reaction force, i.e., the force acting on the mount, is f 1 .…”

“…These are variables for the lumped parameter model. Referring to the hydraulic mount mechanical models [5][6][7][8][9], a unified lumped parameter mechanical model for AHM-IT-DM and PHM-IT-DM is built, as shown in Figure 2. The displacement of the engine side is y1 and the corresponding reaction force, i.e., the force acting on the mount, is f1.…”

“…Due to the wrinkled rubber bellow, K 2 is several orders of magnitude smaller than K 1 . Thus, K 2 is set to zero, and the pressure fluctuation in the lower fluid chamber is ignored and set p 2 = 0 [5,[7][8][9]. Denote the length of inertia track as l 2 , the cross-sectional area as A 2 , the wet perimeter of cross section as L 2 , and the hydraulic diameter as d 2 = 4A 2 /L 2 .…”

“…Based on the unified mechanical model as shown in Figure 2, set m 1 = 0, y 5 = 0, and f a = 0 to obtain the following nonlinear mathematical model for passive dynamics [8,9]:…”

Fractional-Order Least-Mean-Square-Based Active Control for an Electro–Hydraulic Composite Engine Mounts

“…However, establishing an accurate system model for the active vibration control of powertrains is a formidable challenge [10]. FxLMS algorithms are based on the assumptions that the secondary path is a sliding average processes and random input signals, which avoids the dependence on an accurate system model, and thus has been widely studied in the field [11,12].…”