Research Article  Open Access
Research on MRD Parametric Model Based on Magic Formula
Abstract
In order to get a better description to the nonlinear characteristics of magnetorheological dampers, the magic formula is introduced into the general method of parametric modelling of magnetorheological dampers to propose a new parameterized model called magic formulahysteresis loop model (MFM). The new model is simple in structure, the physical meaning of each parameter is clear, and the parameter identification is convenient. The fitting and experimental data of MFM and the phenomenon model under different conditions are applied for error analysis and comparison. The results show that the errors of MFM are more accurate and have better fitting and experimental data under different working conditions, which also have better adaptability and versatility.
1. Introduction
Magnetorheological Fluid (MRF) is a new intelligent material composed of nonmagnetic liquid and tiny soft magnetic particles. The particles are featured by high magnetic flux and low hysteresis [1]. This material exhibits low viscosity Newtonian fluid properties at zero magnetic field, but under high magnetic field, it shows high viscosity and low fluidity Bingham fluid characteristics. Under applied magnetic field, MR fluid’s rheological properties such as viscoelasticity, yield strength, and so on can change rapidly (milliseconds) and reversibly [2]. Magnetorheological damper (MRD), which takes magnetorheological fluid as the actuating medium, has many advantages such as high yield stress, high temperature adaptability, short response time, strong stability, low requirement voltage, and convenient semiactive control, etc [3]. It has drawn more and more attention in the fields of automobile [4], architecture [5], aviation [6], and other fields that require vibration control.
By adjusting the damper input current, MRD could change the strength of the magnetic field to control the size of the damping force. Therefore, MRD is often applied in vibration semiactive control. The premise of accurate semiactive control is to establish accurate and reliable MRD model. But the output damping force of MRD, which is influenced by the coupling of external excitation, applied magnetic field, and internal flow field, shows a strong nonlinear character. This results in difficulties of precise MRD modelling. In order to accurately describe the properties of MRD, many MRD models have been established, which are divided into two types: physical model and phenomenological model [7]. Among them, the physical model refers to the use of magnetorheological fluid constitutive model and damper geometry to do the modelling and determine the damping force [8]. Because there are still many assumptions about the mechanism of magnetorheological fluid, the established physical model is not accurate enough. Therefore, the physical model can often be used to guide the damper design but seldom be applied to the control. Phenomenological model is divided into nonparametric model and parametric model. In the nonparametric model, each parameter has no explicit physical meaning and is only used to identify the hysteresis loop that controls damping force, such as fuzzy logic model [9], neural network model [10], and so on. Besides, the parameters in parametric models have comparatively clear physical meaning. The commonly used parametric models are Bingham model [11], nonlinear doubleviscosity model [12], Dahl model [13], Bouc–Wen model [14], and phenomenon model (PM) etc [15].
Among them, PM, which is an improved version based on the Bouc–Wen Model, is a parameterized model that conforms well to the experimental phenomena. It can accurately describe the MRD lowvelocity attenuation, yield characteristic, and hysteresis characteristic, which owns higher precision and incentive adaptability, that is, the model parameters identified by a certain excitation can be applied to a wider range of excitation. Therefore, PM is the most widely used MRD parameter model, and its model expression is listed in the following equation:
However, PM is composed of two differential equations and some absolute and power function terms, which is difficult to establish and to solve by general numerical method [16]. The model needs to identify up to 12 parameters, of which the existing intermediate variable has ambiguous physical meaning; the relationship between other parameters and external incentives is not clear, so it is difficult to determine the initial value or a fixed range of values, and repeated trial and error and iterative calculations to complete the model parameter identification [17–19] are needed. All of these have brought great difficulties to the establishment and use of MRD model. Therefore, in order to describe the dynamic characteristics of MR fluid damper better, it is necessary to establish an MRD parameterization model which is convenient for modelling and solving and easy to identify parameters with high accuracy and strong universality.
The magic formula [20] can get a good approximation to the nonlinear curve through the combination of several trigonometric functions, therefore, is usually used to establish tire mechanics model. The general form of the magic formula is shown in the following equation:
Among them, , , , and are parameters which control the curve shape; is independent variable, and based on the actual situation it can select speed, displacement, deflection angle, and so on. The magic formula can well describe the mechanical characteristics of the tire within the scope of the experimental data. At the same time, the mechanical properties of the tire can still be accurately expressed in a certain range outside the experimental data. That is, the magic formula can predict from the limited working conditions and ensure a high degree of confidence. At the same time, we can see that, as shown in Figure 1, the curve of tire forcedeflection angle is very similar to the plastic fluid curve of MR damper; however, the plastic fluid curve cannot describe the hysteresis characteristics of the magnetorheological damper. Considering that the tire mechanics model has similar nonlinear characteristics with the MRD, the Magic Formula is introduced to the MRD modelling process, and a magic formulahysteresis loop model (MFM) is established. The new model is of simple structure, definite physical parameters and convenient parameters identification. According to the fitting with the experimental data, MFM is compared with PM and error analysis is done. The results prove the accuracy and universality of the new model, which also provide a reference for the application of MRD in vibration control.
2. Magnetorheological Damper Experiment
The general structure of MRD is shown in Figure 2. The magnetorheological fluid is filled in the cavity of MRD. The piston has some fixed damper channels inside, and the coil is wound inside the piston. When an external force acts axially on the piston rod, the piston moves within the MRD cavity, and the magnetorheological fluid flows along the fixed damping channels. When the coil is energized, a magnetic field can be generated, and the properties of the magnetorheological fluid in the damping channels change as the magnetic field changes. The gas compensation chamber at the end of the damper can provide an appropriate compensation force.
An Instron8802 performance testing machine (Figure 3) is used for a type of MRD data test. The main structure parameters of MRD are as follows: the maximum input current of the damper is 3 A, the maximum displacement of the piston is 0.055 m, the length of the damper cylinder is 0.212 m, the outer cylinder diameter is 0.042 m, piston rod’s diameter is 0.01 m, and the weight is 2.3 kg. The sinusoidal signal is used as the excitation to do the test. By changing the amplitude of the sinusoidal signal (0.005 m, 0.01 m, 0.015 m, and 0.02 m), the frequency (0.5 Hz, 1 Hz, 1.5 Hz, and 2 Hz) and the control current (0 A, 0.5 A, 1 A, 1.5 A, 2 A, 2.5 A, and 3 A), the MRD damping force data under different working conditions were obtained. There are too many working conditions, therefore, the working condition = 0.01 m, = 1 Hz in different currents is selected, and the experimental data are collected as shown in Figure 4. It can be seen from Figure 3 that MRD shows obvious yield characteristic and hysteresis characteristic during its working process.
(a)
(b)
3. The Establishment of the Magic Formula Model
By studying the existing MRD parametric model (such as Bouc–Wen Model), the basic principle of parametric modelling is shown in Figure 5. The MRD moves at a speed of under the action of external force at the moment the damping force generated by the damper mainly consisting of three parts: hysteresis element, damping element, and stiffness element. The hysteresis element mainly describes nonlinear characteristics such as yield characteristics and hysteresis characteristics; the damping element describes the viscous damping after yielding; the stiffness element describes the stiffness characteristics of the damper. Part of the damper also needs to add a offset element to represent the fixed compensation force of the damper due to structural problem.
In order to describe the hysteresis characteristic, an absolute value term is introduced, and a complete MRD parametric model is established based on the principle of MRD parametric model modelling to generate the damping force as is shown in the following equation:
In Equation (3), indicates the displacement of damper piston, indicates the speed of damper piston. The other parameters’ definition and the range of their values are in Table 1.

4. Parameter Identification
For the convenience of calculation, = 0.01 m, = 1 Hz is selected as the reference condition for fitting. Curve fitting was performed by a combination of genetic algorithm and nonlinear least square method.
The fitting steps are as follows. Firstly, the range of each parameter obtained from the model establishment process is optimized by genetic algorithm, and approximated global optimum can be obtained quickly by genetic algorithm in this interval, and then the approximate global optimal is taken as the nonlinear least square’s initial value of the input and the accurate global optimum of each parameter can be obtained. The data of fitting are as listed in Table 2.

According to the data in Table 1, to identify each parameter:(1) represents the bias, as a fixed value, taking the average of the current, we can obtain(2), , , , and in this condition can all be fitted as linear function of the current , as shown in Figure 6.
(a)
(b)
(c)
(d)
(e)
The fitting results are shown in the following equations:
When the magnitude of the external excitation frequency changes, the values of , , , , show only minor fluctuations. It can be considered that these parameters do not change with the amplitude of the external excitation frequency.(3), in this condition can be fit into a quadratic function of the current I, shown in Figure 7.
(a)
(b)
By changing the amplitude or frequency, the relationship of and amplitude is indicated in Figure 8(a), the relationship of and frequency is indicated in Figure 8(b).
(a)
(b)
By changing the amplitude or frequency, the relationship of B and amplitude is indicated in Figure 9(a), and the relationship of B and frequency is indicated in Figure 9(b).
(a)
(b)
Therefore, the final fitted , is as follows:
Take Equations (4)–(11) of the recognized parameters in Equation (3) to get a complete model of the MRD magic formula. Numerical simulation is taken when the complete MFM in MATLAB is under different conditions for different current, and it is compared with the experimental data. Because there are so many different working conditions, only a few of them are selected, as shown in Figure 10.
(a)
(b)
It can be seen from Figure 9 that the parameters of MFM under different conditions are in good agreement with the experimental data.
5. Error Analysis and Comparison
5.1. PM Parameter Identification
To further investigate the accuracy and applicability of MFM, MFM is compared with PM. Taking into account the differential equation in PM is more difficult to directly model, therefore, it is chosen to establish the PM in MATLAB/Simulink, as shown in Figure 11.
From previous studies, the parameters, , , and can be expressed as a polynomial function of the current I in PM, and other parameters are constants. The genetic algorithm is used to further identify the parameters in PM based on experimental data. Taking into account the unknown value range of each parameter of PM, the method of continuously narrowing the parameter value interval gradually improves the recognition accuracy of genetic algorithm. The specific method is as follows: set the value range of each parameter as [, ], and identify each parameter by genetic algorithm, respectively, under basic condition ( = 0.01 m, = 1 Hz) and different currents (0∼3 A). The minimum value of each parameter obtained by different current identification is used as the lower limit, and the maximum value is taken as the upper limit, which is reset as the parameter value range and identified by genetic algorithm. After narrowing the parameter interval several times, the final parameter identification result can be obtained (Table 3).
Taking into account many more working conditions, the basic condition = 0.01 m, = 1 Hz is selected to compare their own fitting accuracy; select the condition = 0.02 m, = 2 Hz, which is far away from the basic condition, to do the damping force prediction accuracy comparison. At the two fixed conditions, compare the error of with the error of and the errors of and are defined as follows:
5.2. SelfFitting Accuracy Comparison
MFM and PM are identified under the basic condition = 0.01 m, = 1 Hz, and the average error for different currents under this condition is listed in Table 4. When I = 3 A, the difference in accuracy is the greatest, as shown in Figure 12.

(a)
(b)
It can be seen from the error data and Figure 12 that under the condition = 0.01 m, = 1 Hz, the average error of each equation of MFM is less than 2.5% under different currents, and the average error of MFM under each current is less than the average error of PM at each current, that is, the fitting equation of MFM to the experimental data is higher.
5.3. Prediction Accuracy Comparison
Select the condition = 0.02 m, = 2 Hz, which is the farthest from the basic condition, and compare the prediction accuracy of damping force. Calculate the average error under this condition as listed in Table 5. When I = 1 A, the difference in accuracy is the greatest, as shown in Figure 13.

(a)
(b)
As can be seen from the error data and Figure 13, under the condition = 0.02 m, = 2 Hz, the average error of the equation formula of MFM at each current is increased compared with the condition = 0.01 m, = 1 Hz, and the largest error is only 2.6%, which is still able to meet the accuracy requirements. At this time, the average error of MFM at each current is still less than the average error of PM at each current, indicating that the prediction accuracy of MFM is higher than that of PM.
Based on the above error analysis, it can be seen that compared with PM, MFM has higher accuracy; when the amplitude of the external excitation frequency changes, the magnitude and standardization tendency of the damping force can still be predicted accurately, and the prediction accuracy is higher than the phenomenon model with better applicability.
6. Conclusions
In the modelling process of MRD, MFM is established after magic formula is introduced. Based on the experimental data of MRD, the parameters of the new model are identified, and the accuracy and the error analysis of the fitted MFM are compared with the commonly used PM. Under the basic condition = 0.01 m, = 1 Hz, MFM is more accurate than PM at different currents, and the maximum precision error of MFM is only 2.5%; under the condition = 0.01 m, = 1 Hz, the fitting accuracy of MFM at different currents is also higher than that of PM, and the maximum accuracy error of MFM is only 2.6%. The results show that MFM is simple in form and does not include differential equations and intermediate variables. The physical meaning and range of values of each parameter are clear, and parameter identification and simulation calculations can be performed quickly and easily. The simulation results under different conditions are in good agreement with the experimental data. With high precision and good adaptability, it has great potential in the field of MRD control.
Data Availability
The data used to support the findings of this study are available from the corresponding author upon request.
Conflicts of Interest
The authors declare that there are no conflicts of interest regarding the publication of this paper.
Acknowledgments
Special thanks to my wife Yi Yao, who has been so supportive all the way. This article is dedicated to her as a wedding anniversary gift.
References
 O. Ashour, C. A. Rogers, and W. Kordonsky, “Magnetorheological fluids: materials, characteristics and devices,” Journal of Intelligent Material Systems and Structure, vol. 7, no. 2, pp. 123–130, 1996. View at: Publisher Site  Google Scholar
 J. D. Carlson, D. M. Catanzarite, and K. A. St Clair, “Commercial magnetorheological fluid devices,” International Journal of Modem Physics B, vol. 10, no. 2324, pp. 2857–2865, 1996. View at: Publisher Site  Google Scholar
 J. Rabinow, “The magnetic fluid clutch,” Tehnical News Bulletin, vol. 32, no. 4, pp. 54–60, 1948. View at: Publisher Site  Google Scholar
 X. Dong, S. Peng, and J. Yu, “Study on selfpowered magneto rheological damper characteristics of selfpowered,” Journal of Mechanical Engineering, vol. 52, no. 20, pp. 83–91, 2016. View at: Publisher Site  Google Scholar
 L. I. Hui, M. Liu, J. Ou et al., “Analysis and design of the intelligent damping control system of the cable stayed cables,” China Journal of Highway and Transport, vol. 18, no. 4, pp. 37–41, 2005. View at: Google Scholar
 Y. Yang, Y. U. Peng, and S. Zhu, “Research on magnetorheological damper skyhook control based on the identification model,” Control Engineering of China, vol. 24, no. 8, pp. 1530–1535, 2017. View at: Google Scholar
 K. Esteki, A. Bagchi, R. Sedaghati et al., “Dynamic analysis of electro and magnetorheological fluid dampers using duct flow models,” Smart Materials and Structures, vol. 23, no. 3, Article ID 035016, 2014. View at: Publisher Site  Google Scholar
 Q. H. Nguyen and S. B. Choi, “Dynamic modeling of an electrorheological damper considering the unsteady behavior of electrorheological fluid flow,” Smart Materials and Structures, vol. 18, no. 5, pp. 1–9, 2009. View at: Publisher Site  Google Scholar
 K. C. Schurter and P. N. Roschke, “Fuzzy modeling of a magnetorheological damper using ANFIS,” in Proceedings of Ninth IEEE International Conference on Fuzzy Systems, vol. 1, pp. 122–127, San Antonio, TX, USA, 2000. View at: Google Scholar
 D. H. Wang and W. H. Liao, “Modeling and control of magnetorheological fluid dampers using neural networks,” Smart Materials and Structures, vol. 14, no. 1, pp. 111–126, 2004. View at: Publisher Site  Google Scholar
 X. Zhu, X. Jing, and L. Cheng, “Magnetorheological fluid dampers: a review on structure design and analysis,” Journal of Intelligent Material Systems and Structures, vol. 23, no. 8, pp. 839–853, 2012. View at: Publisher Site  Google Scholar
 R. Stanway, J. L. Sprostona, and N. G. Stevensa, “Nonlinear modeling of an electrorheological vibration damper,” Journal of Electrostatics, vol. 20, no. 2, pp. 167–184, 1987. View at: Publisher Site  Google Scholar
 X. Q. Ma, S. Rakheja, and C. Y. Su, “Development and relative assessments of models for characterizing the current dependent hysteresis properties of magnetorheological fluid dampers,” Journal of Intelligent Material Systems and Structures, vol. 18, no. 5, pp. 487–502, 2007. View at: Publisher Site  Google Scholar
 P. R. Dahl, “Solid friction damping of mechanical vibrations,” AIAA Journal, vol. 14, no. 12, pp. 1675–1682, 1976. View at: Publisher Site  Google Scholar
 B. F. Spencer, S. J. Dyke, M. K. Sain, and J. D. Carlson, “Phenomenological model for magnetorheological dampers,” Journal of Engineering Mechanics, vol. 123, no. 3, pp. 230–238, 1997. View at: Publisher Site  Google Scholar
 T. Sireteanu, M. Giuclea, and A. M. Mitu, “An analytical approach for approximation of experimental hysteretic loops by Bouc–Wen model,” in Proceedings of the Romanian AcademySeries A: Mathematics, Physics, Technical Sciences, Information Science, vol. 10, no. 1, pp. 1–12, Bucharest, Romania, January 2009. View at: Google Scholar
 M. Giuclea, T. Sireteanu, D. Stancioiu, and C. W. Stammers, “Model parameter identification for vehicle vibration control with magnetorheological dampers using computational intelligence methods,” Proceedings of the I MECH E Part I Journal of Systems and Control Engineering, vol. 218, no. 7, pp. 569–581, 2004. View at: Publisher Site  Google Scholar
 N. M. Kwok, Q. P. Ha, M. T. Nguyen, J. Li, and B. Samali, “Bouc–Wenmodel parameter Identification for a MR fluid damper using computationally efficient GA,” ISA Transactions, vol. 46, no. 2, pp. 167–179, 2007. View at: Publisher Site  Google Scholar
 Y. Liu, S. Yang, Y.Y. Liao, and G.N. Zhang, “Parameter identification of Bouc–Wen model for MR damper based on genetic algorithm,” Journal of Vibration and Shock, vol. 30, no. 7, pp. 261–265, 2011. View at: Google Scholar
 H. B. Pacejka, Tyre and Vehicle Dynamics, Elsevier’s Science and Technology Rights Department, Oxford, UK, 2006.
Copyright
Copyright © 2018 Wei Pan et al. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.