The optimization of the parameters of the energy recovery device from vibration of a vehicle suspension
Wojciech Skarka^{1} , Mateusz Tyczka^{2} , Piotr Przystałka^{3}
^{1, 2, 3}Institute of Fundamentals of Machinery Design, Faculty of Mechanical Engineering, Silesian University of Technology, Gliwice, Poland
^{1}Corresponding author
Vibroengineering PROCEDIA, Vol. 3, 2014, p. 233237.
Accepted 14 September 2014; published 10 October 2014
The paper presents the numerical optimization model of the energy recovery system from a suspension of a racing vehicle. The system is based on the recovery of energy lost in the classical solutions in the viscous damper. The suspension system should provide adequate comfort to a driver, while allowing recovery of the maximum amount of energy. The goal of the research is to draw general conclusions about the optimal parameters for similar systems. The parameters selection for the energy recovery system is a difficult task. For this reason, it has been decided to build a simulation model that allows the selection of the optimal parameters of the system. The fitness function of the model is the amount of energy recovered from the system. The amount of recovered energy should be as high as possible, while ensuring a good comfort for a driver, which is necessary, to recognize the result as valid. During the optimization each set of parameters has been simulated for different road profiles with different road surface quality. The model has been prepared for the racing car, but its universality allows for the selection of optimal parameters of energy recovery system for other vehicles.
Keywords: multidisciplinary design optimization, energy recovering, damper, vehicle suspension.
1. Introduction
Decreasing amount of fossil fuels makes it necessary to constantly increase the effectiveness of their use. This also applies to vehicles. One of the possibilities to improve the efficiency of cars is recovering energy from the vehicle’s suspension. The idea of recovering energy from the suspension is not brand new. Energy recovery from the suspension, means replacing the classical shock absorbes with the element, that allows for the recovery of dissipated energy. There are many possible solutions. The most popular are the solutions using electrohydraulics energy recovery [1, 2]. Other solution is to use a linear electric motor [3]. A large group of solutions is based on electromechanical system and a DC motor as a power generator [4, 5]. As in the case of [4], the authors have decided to use a rack gear and the DC motor as a generator for energy recovery. In addition, it has been decided to introduce a mechanism guaranteeing a constant direction of rotation of the motor shaft and the additional multiplication speed of the motor shaft. Determination of optimal parameters for energy recovering system is difficult. In this paper the focus is to define the general conclusions concerning the parameters of this type of energy recovery unit. For this purpose, a mathematical model of system has been determined and then implemented in MATLAB SIMULINK® calculation software. For calculation has been used a numerical model of a racing car [6, 7] (Fig. 1), prepared to take part in competitions Shell EcoMarathon [8]. The research has a preliminary nature. It was decided to use the popular vehicle quarter car model [9, 10]. Due to the large number of possible combinations the genetic algorithm, has been used, which has already been applied in similar studies [10, 11], to calculate the optimal parameters. In addition to energy recovery, which is the main criterion of the optimization, also verified the comfort of the driver has been included, which is a secondary criterion due to the nature of the example. Range of parameters has been chosen based on previous studies on the use of energy recovery from a suspension and the vehicle energy model of a similar vehicle [1215].
Fig. 1. Racing vehicle prepared for Shell Ecomarathon [7]
Fig. 2. Structure of the simulation model
2. Simulation model
In order to determine the optimal parameters, it was necessary to create a mathematical model of the vehicle. Due to the nature of the initial research, it has been decided only to verify driver comfort. Adequate to do this is the quarter car model [9, 10]. The model consists of unsprung mass representing the weight of the wheel and sprung mass which is one quarter of the weight of the vehicle body and the driver. The tire of the vehicle has been described by parallelconnected spring and damping elements with fixed parameters. The suspension has been defined by the spring element of constant parameters. In the equations the damping force has been introduced arising from the generation of energy through energy recovery system. Additionally, the impact of the suspension arm used in the vehicle has been taken into account. In the case of the car for which studies were performed the simple suspension arm was used, which allowed the introduction of simple mathematical relations. Energy recovery system consists of a mechanical system and a DC motor working as a generator. The mechanical system has the task of maintaining a constant direction and speed multiplication of the motor shaft. The mathematical equations describing the model are shown below:
where: subscript is 1 for sprung mass and 2 is for unsprung mass, $m$ is for mass, $x$ is for displacement, $w$ is for road profile, $c$ is for spring rate, $b$ is for damping factor, $F$ is damping force arising from the energy generator, apostrophe like ${x}_{2}^{\text{'}}$ is function of displacement arising by suspension arm, ${R}_{z}$ is for external resistance, $r$ is total ratio of the mechanical system, $R$, ${K}_{1}$, ${K}_{2}$, $L$ are parameters of DC engine used for generating energy, $n$ is efficiency of mechanical system.
In order to determine the optimal parameters, the system has been modeled in the MATLAB SIMULINK® software. The input to the model is the road profile. The road profile has been generated at random, based on the PSD [1618] in accordance with the standard [18]. 10 cases have been verified. For each, three types of surfaces of different quality have been tested. The model has been divided into blocks. The mechanical system and generator are blocks responsible for energy recovery system. The transition function is the block responsible for calculating displacement which takes into account the suspension arm. A schematic structure of the model is shown in Fig. 2.
3. Optimization task
The main purpose of the optimization process is to adjust parameters such as ${c}_{1}$, ${z}_{1}$, ${z}_{2}$, ${z}_{3}$, $p$ and to find suitable type of a motor in order to minimize the cost of function $U$, which can be formulated taking into account the following two criteria. The first criterion is to recover maximal quantity of the energy, whereas the second one is to minimize the influence of car vibrations. The authors propose to use the global criterion method [19] in which two objectives are combined. One of the most general indirect utility functions at this matter can be expressed in its simplest form as the weighted exponential product:
where $\mathbf{q}=\left[{c}_{1}{z}_{1}{z}_{2}{z}_{3}pMotorID\right]$, ${w}_{1}$ and ${w}_{2}$ denote weights indicating the relative significance of the criterion functions, $H$ is the Heaviside step function, $\u03f5$ is a threshold corresponding to the EU rules, $\delta $ is a penalty component (it is equal to 1E6 if ${z}_{2}$ and ${z}_{3}$ are simultaneously even or odd), ${P}_{j}$ is the estimation of the recover power, $r$ is the number of the road surface types, $N$ is the number of samples corresponding to the length of the simulation. Parameters $p$, ${z}_{1}$, ${z}_{2}$, ${z}_{3}$ describe the mechanical system of energy recovery system. The influence of the vibration of the vehicle on a driver is evaluated using the estimation of the root mean square of the acceleration signal of the car suspension [20, 21]:
A large number of algorithms can be used for solving the problem stated above. However, standard optimization methods e.g. gradientbased approaches cannot be adopted in this context, mainly due to the form of the cost function (Eq. (1)) and because there are continuous and discrete independent variables in the vector $\mathbf{q}$. For these reasons, the authors decided to apply evolutionary optimization algorithms which are based on the natural selection process that mimics biological evolution. Wellknown genetic operators for singleobjective optimization are used to guarantee the convergence of a solution [19].
4. Result
In the present study, the optimization process was carried out using MATLAB® with Genetic Algorithm and Direct Search toolbox. The behavioural parameters of the evolutionary algorithm were chosen according to the guidelines suggested in the literature [22]. The fitness function was based on the metacriterion (Eq. (5)), wherein the weights were the same for both criteria (${w}_{1}=$0.5, ${w}_{2}=$0.5) and the parameter $\u03f5=$3.25 (taking into account restrictions in the UE law) [23]. Due to the preliminary results of the simulation it was decided that the upper and lower limits of the variables ${c}_{1}$, ${z}_{1}$ etc. were chosen taking into account typical and normalized elements and according to parameters of the race car. It was determined that individuals in the population would be composed of genes representing real numeric and integer values. Genes in the chromosome corresponds to the values of the elements of the vector $\mathbf{q}$. The feasible population method was adapted to create a random welldispersed initial population that satisfies all bounds. The ranking method was used to scale the fitness function and the roulette method was employed to choose parents creating new individuals for the next generation. Reproduction was carried out applying the elite count method (the number of individuals equal to 2) and crossover as well as mutation operators. In the paper, the heuristic crossover was realized with a probability of 0.8. The remaining individuals were processed using an adaptive feasible mutation function. The maximum number of generations was chosen as the criterion for stopping the algorithm. It was experimentally established that, the population size would equal to 60 and a maximum number of generations would equal to 200. The optimization procedure was realized ten times to obtain averaged results which are presented in Table 1. The best trial was achieved in the case of ProfileID $=$ 08. Fig. 2 presents the convergence of the optimization algorithm for this case.
Table 1. Results of the optimization process for different variants of the surface of the road
Profile ID

${c}_{1}$

${z}_{1}$

${z}_{2}$

${z}_{3}$

$p$

Motor ID

$U$

00

9000

17

63

38

150

28 (${K}_{1}=$56, ${K}_{2}=$170, $R=$ 10, $L=$2.62, $J=$ 122)

202

01

19400

29

70

25

150

35 (${K}_{1}=$39.5, ${K}_{2}=$242, $R=$ 3.9, $L=$2.83, $J=$ 560)

98

02

11500

24

70

25

100

35 (${K}_{1}=$39.5, ${K}_{2}=$242, $R=$ 3.9, $L=$2.8, $J=$ 560)

91

03

18500

17

48

17

150

5 (${K}_{1}=$56, ${K}_{2}=$170, $R=$ 9.97, $L=$2.62, $J=$ 120)

90

04

8900

17

35

18

150

28 (${K}_{1}=$56.2, ${K}_{2}=$170, $R=$ 10.2, $L=$2.62, $J=$ 122)

167

05

8800

17

62

17

150

29 (${K}_{1}=$44.7, ${K}_{2}=$214, $R=$ 16, $L=$4.14, $J=$ 124)

80

06

17600

17

68

25

150

28 (${K}_{1}=$56.2, ${K}_{2}=$170, $R=$ 10.2, $L=$2.620, $J=$ 122)

89

07

15000

22

70

17

150

27 (${K}_{1}=$69.7, ${K}_{2}=$137, $R=$ 6.61, $L=$1.7, $J=$ 123)

82

08

11700

17

70

23

150

35 (${K}_{1}=$39.5, ${K}_{2}=$242, $R=$ 3.9, $L=$2.83, $J=$ 560)

60

09

13000

17

69

28

150

28 (${K}_{1}=$56, ${K}_{2}=$170, $R=$ 10.2, $L=$2.62, $J=$ 122)

165

Fig. 3. Mean and best fitness function values vs. the number of function evaluations
a)
b)
5. Conclusions
The best result of fitness function has been achieved for the case of 8. Because the road profiles were generated at random, while retaining a similar road standard, it cannot be concluded that this is the best set of parameters for each surface. However, based on other results, it is possible to draw some general conclusions. The first of the conclusions is the striving for high gears at speed multiplication on the shaft of the generator. This is proved by the results of gear ratios ($p$ parameter). Most of them is 150 which is maximum possible value. On the basis of the parameters ${z}_{1}$, ${z}_{2}$, ${z}_{3}$ (number of gear teeth of a mechanical system) similar conclusions can be drawn. In 9 out of 10 cases, as the optimal engine, a powerful engine has been calculated (150 to 200 W). This indicates that the generator should use a highpower engine. The damping force values obtained from energy recovery system proved to be low. This demonstrates the need for duplication of energy recovery system or using an additional damping system, if used in the vehicle. The research had preliminary nature. Before using the system in the vehicle, further studies are necessary and verification of numerical results for real energy recovery system. The current results are encouraging for further work.
References
 Zhang Y., Zhanga X., Zhana M., Guoa K., Zhaoc F., Zongwei L. Study on a novel hydraulic pumping regenerative suspension for vehicles. Journal of the Franklin Institute, in press, 2014. [Search CrossRef]
 Li Ch., Zhu R., Liang M., Yang S. Integration of shock absorption and energy harvesting using a hydraulic rectifier. Journal of Sound and Vibration, Vol. 333, Issue 17, 2014, p. 39043916. [Search CrossRef]
 Suda Y., Nakadai S., Nakano K. Hybrid suspension system with skyhook control and energy regeneration (development of selfpoweredactive suspension). Vehicle System Dynamics, Vol. 29, 1998, p. 619634. [Search CrossRef]
 Zhang G. G., Cao J. Y., Yu F. Design of active and energy regenerative controllers for DCmotorbased suspension. Mechatronics, Vol. 22, 2012, p. 11241134. [Search CrossRef]
 Li Z. J., Zuo L., Luhrs G., Lin L. J., Qin Y. X. Electromagnetic energyharvesting shock absorbers design, modeling and road. IEEE Transactions on Vehicular Technology, Vol. 62, 2013, p. 10651074. [Search CrossRef]
 Cholewa A., Skarka W., Sternal K., Targosz M. Electric vehicle for the students’ shell ecomarathon competition. Design of the Car and Telemetry System, Telematics in the Transport Environment, 12th International Conference on Transport Systems Telematics, KatowiceUstroń, Poland, Communications in Computer and Information Science, Springer, Vol. 329, 2012, p. 2633. [Search CrossRef]
 Smart Power team website, http://mkm.polsl.pl. [Search CrossRef]
 Shell Eco marathon website, http://www.shell.com/global/enviromnentsociety/ecomarathon.html. [Search CrossRef]
 Kanjanavapastita A., Thitinaruemitb A. Estimation of a speed hump profile using quarter car model. Social and Behavioral Sciences, Vol. 88, 2013, p. 265273. [Search CrossRef]
 Gündoğdu Ö. Optimal seat and suspension design for a quarter car with driver model using genetic algorithms. International Journal of Industrial Ergonomics, Vol. 37, Issue 4, 2007, p. 327332. [Search CrossRef]
 Alkhatiba R., Nakhaie Jazarb G., Golnaraghia M. F. Optimal design of passive linear suspension using genetic algorithm. Journal of Sound and Vibration, Vol. 275, Issues 35, 2004, p. 665691. [Search CrossRef]
 Skarka W., Tyczka M. The numerical model of the energy recovery of the racing vehicle. Mechanik, Vol. 87, Issue 2, (in Polish). [Search CrossRef]
 Przystałka P., Skarka W., Szumowski M., Targosz M. Velocity planning of an electric vehicle using an evolutionary algorithm, activities of transport telematics. 13th International Conference on Transport Systems Telematics, KatowiceUstroń, Poland, Communications in Computer and Information Science, Springer, Vol. 395, 2013, p. 171177. [Search CrossRef]
 Skarka W. Application of numerical inverse model to determine the characteristics of electric race car. Tools and methods of competitive engineering. TMCE 2014 Symposium, Budapest, Hungary, 2014, p. 263274. [Search CrossRef]
 Targosz M., Skarka W., Przystalka P. Simulation and optimization methodology of prototype electric vehicle. Proceedings of the 13th International Design Conference, 2014, p. 13491360. [Search CrossRef]
 OstadAhmadGhorabi M. J., Arghavan A., RezaKashyzadeh K. Investigation effect of velocity on the transfer function values under road roughness. International Journal of Emerging Technology and Advanced Engineering, Vol. 2, Issue 5, 2012, p. 914. [Search CrossRef]
 Feng T., YuFen H., ShunHsu T., Wes S. J. Generation of random road profiles. Journal of Advanced Engineering, Vol. 4, 2009, p. 151156. [Search CrossRef]
 International Standards Organisation. Mechanical vibration – road surface profiles – reporting of measured data, ISO 8608, 1995. [Search CrossRef]
 Marler R. T., Arora J. S. Survey of multiobjective optimization methods for engineering. Structural and Multidisciplinary Optimization, Vol. 26, 2004, p. 369395. [Search CrossRef]
 Uys P. E., Els P. S., Thoresson M. Suspension settings for optimal ride comfort of offroad vehicles travelling on roads with different roughness and speeds. Journal of Terramechanics, Vol. 44, 2007, p. 163175. [Search CrossRef]
 International Standards Organisation. Mechanical vibration and shock – Evaluation of human exposure to wholebody vibration – Part 1: General requirements, ISO 26311, 1997. [Search CrossRef]
 Rutkowski L. Methods and Techniques of Artificial Intelligence. PWN, Warsaw, 2005, (in Polish). [Search CrossRef]
 Griffin M. J. Minimum health and safety requirements for workers exposed to handtransmitted vibration and wholebody vibration in the European Union; a review. Occupational and Environmental Medicine, Vol. 61, Issue 5, 2004, p. 387397. [Search CrossRef]