Design parameters of the MR damper
1. Introduction
Vehicle suspension is used to attenuate unwanted vibrations from various road conditions. So far, three types of suspension system have been proposed and successfully implemented; passive, active and semiactive. Though the passive suspension system featuring oil damper provides design simplicity and cost-effectiveness, performance limitations are inevitable due to the lack of damping force controllability. On the other hand, the active suspension system can provides high control performance in wide frequency range. However, this type may require high power sources, many sensors and complex actuators such as servovalves. Consequently, one way to resolve these requirements of the active suspension system is to adopt the semiactive suspension system. The semiactive suspension system offers a desirable performance generally enhanced in the active mode without requiring large power sources and expensive hardware.
One of very attractive and effective semiactive vehicle suspension systems is to utilize magnetorheological (MR) fluid. MR fluids are currently being studied and implemented as actuating fluids for valve systems, shock absorbers, engine mounts, haptic systems, structure damper, and other control systems. The rheological properties of MR fluids are reversibly and instantaneously changed by applying a magnetic field to the fluid domain. Recently, a very attractive and effective semi-active suspension system featuring MR fluids has been researched widely. Carlson et al., 1996 proposed a commercially available MR damper which is applicable to on-and-off-highway vehicle suspension system. They experimentally demonstrated that sufficient levels of damping force and also superior control capability of the damping force by applying control magnetic field. Spencer Jr. et al., 1997 proposed dynamic model for the prediction of damping force of a MR damper. They compared the measured damping forces with the predicted ones in time domain. Kamath et al., 1998 proposed a semi-active MR lag mode damper. They proposed dynamic model and verified its validity by comparing the predicted damping force with the measured one. Yu et al., 2006 evaluated the effective performance of the MR suspension system by road testing. Guo & Hu, 2005 proposed nonlinear stiffness model of a MR damper. They proposed nonlinear stiffness model and verified it using simulation and experiment. Du et al., 2005proposed H-infinity control algorithm for vehicle MR damper and verified its effectiveness using simulation. Shen et al., 2007 proposed load-levelling suspension with a magnetorheological damper. Pranoto et al., 2005 proposed 2DOF-type rotary MR damper and verified its efficiencies. Ok et al., 2007 proposed cable-stayed bridges using MR dampers and verified its effectiveness using semi-active fuzzy control algorithm. Choi et al., 2001 manufactured an MR damper for a passenger vehicle and presented a hysteresis model for predicting the field-dependent damping force. Hong et al., 2008 derived a nondimensional Bingham model for MR damper and verified its effectiveness through experimental investigation. Yu et al., 2009 developed human simulated intelligent control algorithm and successfully applied it to vibration control of vehicle suspension featuring MR dampers. Seong et al., 2009 proposed hysteretic compensator of MR damper. They developed nonlinear Preisach hysteresis model and hysteretic compensator and demonstrated its damping force control performance.
As is evident from the previous research work, MR damper is very effective solution for vibration control of vehicle suspension system. So in this chapter, we formulate various vibration control strategies for vibration control of MR suspension system and evaluate their control performances. In order to achieve this goal, material characteristics of MR fluid are explained. Then the MR damper for vehicle suspension system is designed, modelled and manufactured. The characteristics of manufactured MR damper are experimentally evaluated. For vibration control, the quarter vehicle suspension system featuring MR damper is modelled and constructed. Then, various vibration control strategies such as skyhook control, PID control, LQG control, H∞ control, Sliding mode control, moving sliding mode control and fuzzy moving sliding mode control are formulated. Finally, control performances of the proposed control algorithms are experimentally evaluated and compared.
2. Suspension modelling
2.1. MR fluid
Since Jacob Rabinow discovered MR fluid in the late 1940s, of which yield stress and viscosity varies in the presence of magnetic field, various applications using MR fluid have been developed such as shock absorbers, clutches, engine mounts, haptic devices and structure dampers, etc (Kim et al., 2002). Physical property changes of MR fluid are resultedfrom the chain-like structures between paramagnetic MR particles in the low permeability solvent. At the normal condition, MR fluid shows the isotropic Newtonian behavior because the MR particles move freely as shown in Fig. 1 (a). However, when the magnetic field applied to the MR fluid, MR fluid shows the anisotropic Bingham behavior and resist to flow or external shear force because the MR particles make a chain structure as shown in Fig. 1 (b). From this property, force or torque of application devices can be easily controlled by the intensity of the magnetic field.
2.2. MR damper
The schematic configuration of the cylindrical type MR damper proposed in this work is shown in Fig. 2. The MR damper is composed of the piston, cylinder and gas chamber. The floating piston between the cylinder and the gas chamber is also used in order tocompensate for the volume induced by the motion of the piston. Also the gas chamber
which is filled with nitrogen gas acts as an accumulator for absorbing sudden pressure variation of lower chamber of the MR damper induced by the rapid motion of the piston. The MR damper is divided into the upper and lower chambers by piston, and it is fully filled with the MR fluid. By the motion of the piston, the MR fluid flows through the annular duct between inner and outer piston from one chamber to the other. The magnetic poles in the piston head is placed to control the yield stress of the MR fluid by supplying current to the coil. In order effectively to generate the magnetic field in the magnetic pole, the outer cylinder and both ends of inner piston are made of ferromagnetic substance, while the center of the inner piston is a paramagnetic substance. In the absence of a magnetic field, the MR damper produces a damping force caused only by fluid viscous resistance. However, if a certain level of magnetic field is supplied to the MR damper, the MR damper produces an additional damping force owing to the yield stress of the MR fluid. This damping force of the MR damper can be continuously tuned by controlling the intensity of the magnetic field.
In order to simplify the analysis of the MR damper, it is assumed that the MR fluid is incompressible and that pressure in one chamber is uniformly distributed. The pressure drops due to the geometric shape of the annular duct and the fluid inertia are assumed to be negligible. For laminar flow in the annular duct, the fluid resistance is given by (Liu et al., 2006; White, 1994)
where
where
Where c is a coefficient that depends on flow velocity profile and has a value range from 2.0 to 3.0,
where
|
|
Duct Length ( |
82mm |
Piston Area ( |
1661.90mm2 |
Piston Rod Area ( |
380.13mm2 |
Duct Width ( |
123.53mm |
Maximum Stroke | 164mm |
where
The photograph of the manufactured MR damper with optimally obtained design parameters are shown in Fig. 3. The principal design parameters of the manufactured MR damper, which can be applied to a mid-sized commercial passenger vehicle, are presented in Table 1. Fig. 4 presents the measured and analysed damping force
2.3. Quarter vehicle MR suspension
In order to investigate the effectiveness of vibration control algorithm, a quarter vehicle MR suspension system is constructed as shown in Fig. 6. It shows that the proposed quarter vehicle suspension model with the MR damper has two degrees of freedom. The spring for the suspension is assumed to be linear and the tire is also modelled as linear spring component. From the mechanical model, dynamic equation of system considering time constant can be expressed as follows:
|
|
Sprung Mass ( |
373.5kg |
Unsprung Mass ( |
40kg |
Stiffness Coefficient ( |
27358N/m |
Tire Stiffness Coefficient ( |
211625N/m |
Damping Coefficient ( |
570Ns/m |
where
where
The system parameters of the quarter vehicle MR suspension system are chosen on the basis of the conventional suspension system for a mid-sized passenger vehicle, and listed in Table 2.
3. Control strategies
In order to evaluate vibration control performance of the quarter vehicle MR suspension system, various control strategies are formulated and experimentally implemented.
3.1. Skyhook controller
Skyhook controller is simple but very effective control algorithm. It is well known that the logic of the skyhook controller is easy to implement in the real field. The principle of skyhook control is to design the active or semiactive suspension control so that the sprungmass is linked to the sky in order to reduce the vertical oscillations of the sprung mass. Fig. 7 shows the conceptual scheme of skyhook controller for vehicle suspension system. The desired damping force is set by
where
3.2. LQG controller
Optimal control of a linear system with respect to the quadratic objective function under incomplete measurements corrupted by white Gaussian noise is generally referred to as the linear quadratic Gaussian (LQG) problem. The optimal control is a linear function of the state estimates obtained from the Kalman-Bucy filter. The LQR (linear quadratic regulation) is a state feedback problem, whereas LQG is an output feedback problem, which is more realistic (Bahram& Michael, 1993). Fig. 8 shows the block diagram of an LQG controller. In this study, the control input is formulated as follows:
where
3.3.
H
∞
controller
In reality, the sprung mass of the vehicle is varied by the loading conditions such as the number of riding persons and payload. And it makes the pitch and roll mass moment of inertia to be changed. Therefore, in order to successfully control the vibration, a robust control algorithm is required by considering the parameter variations of the system. From the structured suspension model, a desirable damping force required to effectively suppress the vibration is determined by adopting
For reducing the steady state error and suppressing the effectiveness of disturbance, weighting function can be designed as follows (Choi et al., 1999; 2002):
For the design of controller, design index
Where
3.4. Sliding mode controller (SMC)
Fig. 11 shows the conceptual scheme of sliding mode control algorithm. After the initial reaching phase, the system states slides along the sliding surface. The first step to formulate the SMC is to design a stable sliding surface. The stable sliding surface for the control system is defined as follows:
where
Where
3.5. Moving sliding mode controller (MSMC)
It is required to reduce reaching phase to improve the performance and robustness of the SMC. Reaching time can be successfully reduced in case that sliding surface is rotated orshifted by considering reaching phase. Fig. 12 illustrates two moving patterns of the sliding surface: rotating and shifting. The sliding surface for moving sliding mode controller can be determined as follows:
where
3.6. Fuzzy moving sliding mode controller (FMSMC)
The fuzzy moving sliding mode controller, which can change the coefficients and intercepts of sliding surface by fuzzy tuning which takes into account for location of reaching phase, is developed. Fig. 13 presents the block diagram of the proposed FMSMC. The basic configuration of fuzzy control consists of three components: a fuzzification interface, a decision-making logic and a deffuzification interface. In this study, the coefficient of sprung mass displacement
where
The control input determined from the FMSMC is to be applied to the MR damper depending upon the motion of suspension travel. The detailed control algorithm was described by Cho et al., 2007.
3.7. Semi-active condition
The control input
This semi-active condition can assure the increment of damping characteristic of the suspension system and hence increase the stability of the system.
4.Control performances
Vibration control performances of the quarter vehicle MR suspension system are evaluatedunder two types of excitation (road) conditions. The first excitation, normally used to reveal the transient response characteristic, is a bump described by
where
Fig. 14 shows the experimental apparatus of the quarter vehicle MR suspension system to evaluate and compare the effectiveness of vibration isolation of the proposed control algorithms. The MR suspension (assembly of the MR damper and spring), sprung mass and tire are installed on the hydraulic excitation system. The sprung mass displacement and excitation displacement are measured by LVDT (linear variable differential transformer) and the suspension travel is measured by a wire sensor. The hydraulic system applies the road profile to the MR suspension system. The current amplifier applies the control current determined from the control algorithm to the MR damper.
Fig. 15 presents vertical displacement, vertical acceleration of sprung mass and suspension travel versus time responses of the MR suspension system for the bump excitation. As shown in the Fig., it can obviously be found that unwanted vibrations induced from the bump excitation are well suppressed by adopting the control algorithms in the MR suspension system. Fig. 16 shows the performance comparison of vertical acceleration RMS of the quarter vehicle MR suspension system for the bump excitation. The RMS value is calculated from:
As shown in Fig., skyhook control algorithm shows quite good vibration control performance. Also, Fig. 17 shows the PSD (power spectrum density) of sprung mass acceleration in frequency domain for the random excitation and Fig. 18 shows the performance comparison of vertical acceleration RMS of the quarter vehicle MR suspension system for the random excitation. As expected, the PSD of the vertical acceleration has been
considerably reduced in the neighbourhood of body resonance (1~2Hz) by applying control input. The control results presented in Figs. 15~18 indicate that ride comfort of a vehicle system can be substantially improved by employing the MR suspension system associated with the proposed control algorithms.
5. Conclusion
In this chapter, control algorithms for vibration control of the quarter vehicle MR suspension system were proposed and its effectiveness was experimentally verified and compared. In order to achieve this goal, a cylindrical MR damper was designed and manufactured. After evaluating the field-dependent damping characteristics of the MR damper, a quarter vehicle suspension system was then constructed and its governing equations of motion were derived. In order to obtain a favourable control performance of the MR suspension system, skyhook controller, LQG controller, H∞ controller, sliding mode controller, moving sliding mode controller and fuzzy moving sliding mode controller were designed and experimentally realized to the quarter vehicle MR suspension system. It has been experimentally shown that the proposed control algorithms can reduce the unwanted vibration under bump excitation. In addition, it has been demonstrated that using the proposed control methodologies vibration levels such as sprung mass acceleration under random excitation can be significantly reduced at body resonance region. The results presented here are self-explanatory justifying that the control strategies implemented in this work can produce very similar vibration control performance. This directly indicates that ride comfort of the vehicle system can be substantially improved by adopting the MR suspension system associated with the proposed control strategies.
References
- 1.
Bahram S. Michael H. 1993 )., Prentice Hall,0-13-174061-X New Jersey - 2.
Carlson, J. D., Cantanzarite, D. M. and St.Clair, K. A. ( 1996 ).Commercial Magnetorheological Fluid Devices., Vol.1996, pp. 20-28, ISBN 981-02-2676-4 - 3.
Cho J. W. Pang Y. S. Choi S. B. Kim K. S. (2007 978-9-81277-119-3 Lake Tahoe, USA - 4.
Choi S. B. Han S. S. Kim H. K. Cheong C. C. (1999 9 9 3 271 286 ,0957-4158 - 5.
Choi S. B. Choi Y. T. Park D. W. 2000 A Sliding Mode Control of a Full-Car Electrorheological Suspension System Via Hardware in-the-Loop Simulation. ,122 1 114 121 ,0022-0434 - 6.
Choi S. B. Lee S. K. Park Y. P. (2001 2001).A Hysteresis Model for the Field-Dependent Damping Force of a Magnetorheological Damper.,245 2 375 383 ,0002-2460 x - 7.
Choi S. B. Lee H. S. Park Y. P. (2002 38 38 5 341 360 ,0042-3114 - 8.
Du H. Yim S. K. Lam J. (2005 Semi 283 283 3 5,981 996 ,0002-2460 x - 9.
Guo D. Hu H. (2005 40 40 3 241 249 ,0092-4090 x - 10.
Hong S. R. Wereley N. M. Choi Y. T. Choi S. B. (2008 312 312 3 399 417 ,0002-2460 x - 11.
Kamath G. M. Wereley N. M. Jolly M. R. (1998 1998 356 377 356377 0027-7786 x - 12.
Kim J. H. Kang B. W. Park K. M. Choi S. B. Kim K. S. 2002 MR Inserts For Shock Wave Reduction in Warship Structures. ,13 10 661 666 ,0104-5389 x - 13.
Lee H. G. Sung K. G. Choi S. B. Park M. K. Park M. K. 2011 Performance Evaluation of a Quarter-Vehicle MR Suspension System with Different Tire Pressure.,12 2 203 210 ,1229-8557 - 14.
Liu B. Li W. H. Kosasih P. B. Zhang X. Z. (2006 15 15 6 1960 1966 ,0964-1726 - 15.
Ok S. Y. Kim D. S. Park K. S. Koh H. M. 2007 Semi-Active Fuzzy Control of Cable-Stayed Bridges Using Magneto-Rheological Dampers.,29 5 776 788 ,0141-0296 - 16.
Pranoto T. Nagaya K. (2005 161 161 1 2,146 150 ,0924-0136 - 17.
Seong M. S. Choi S. B. Han Y. M. (2009 18 18 7 1 13 ,0964-1726 - 18.
Shen Y. Golnaraghi M. F. Heppler G. R. (2007 Load 45 45 4 297 312 ,0042-3114 - 19.
Spencer Jr B. F. Dyke S. J. Sain M. K. Carlson J. D. (1997 123 123 3 230 238 ,0733-9399 - 20.
White F. M. 2003 (Fifth Edition), Mcgraw-Hill,0-07240-217-2 York - 21.
Yu M. Liao C. R. Chen W. M. Huang S. L. 2006 Study on MR Semi-Active Suspension System and its Road Testing. ,17 8 9,801 806 ,0104-5389 x - 22.
Yu M. Dong X. M. Choi S. B. Liao C. R. 2009 Human Simulated Intelligent Control of Vehicle Suspension System with MR Dampers.,319 3 5,753 767 ,0002-2460 x