Identification of Response Behavior for Wagon-R Car during Road Irregularities by Performing Dynamic Simulation Using Quarter Car Model in Adams

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Identification of Response Behavior for

Wagon-R Car during Wagon-Road Irregularities by Performing

Dynamic Simulation Using Quarter Car Model

in Adams

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Utsav D. Gadhia , 2Dr. Veera Darji , 3Dr. Divyang Pandya

1_{Reserch Scholar, Mechanical Engineering Department,}2_{Professor & Head., Mechanical Engineering Department.} 1,2_{C.U. Shah University, Wadhwan,Surendranagar, Gujarat, India}

3_{Head of Mechanical Dept., LDRP Institute of Technology and Research, Kadi sarva Vishwavidyalaya}

Gandhinagar, India.

Abstract— The comfort of passenger and stability of a vehicle are the key objective of any passenger car. Stability of the vehicle should not be provided at a cost a passenger’s comfort level. The purpose of this paper is to find out the response behavior for wagon-r car during road irregularities by performing quarter model dynamic simulation in ADAMS. The work represents a response of existing suspension system in various weight and bump height condition. To conclude Eighteen simulations were conducted for different weight and for various bump heights, as a result, seventy-two graphs show the overall results with different criteria. Novelty of this paper is presented in its response pattern, results and conclusion for various inputs. In the end, results show whether the response pattern of the wagon-r car is proper or it needs some improvisation to achieve better results.

Keywords

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Response behavior of passenger car; ADAMS Simulation; Indian Hatchback; Wagon-R Car Suspension; Quarter car model,Dynamic simulation; Passenger Cars; Car suspension; suspension of hatchback car;

I. INTRODUCTION

The suspension is a key element in a vehicle that performs a important role. The study of suspension system is a key factor for vehicle design. [1] Absorption of road vibration is a main function for any of the suspension., not only that the design of it is also done in a way that it improves tyre friction, stability of the vehicle in any condition that associated with accelerating, braking, or turning. Hence analysis of the suspension becomes crucial and must be analyze with a proper tool before implementing it in a vehicle. Poor design of suspension will result in jerky and uncomfortable ride, it may become a cause of accident also. Many of the researchers have performs various studies that are indicated below.

the design and analysis of a hydro-pneumatic limited bandwidth of active suspension system defined by Crola and Abdel Haleem. A quarter body is use to compare a performance with active and passive system. [2]. A comparative study of simple passive suspension is performed by Smith-Wang by using quarter and full body model of car [3]. A chaos due to road surface was demonstrated by Melnikov criterion by Litak et. al., M. Borowies, M. Friswell and K. Szabelski [4]. A benefits of semi active suspension oer passive suspension using a quarter car model is demonstrated by Sammier, Sename, & Dugard to improve the passenger comfort. Using non liner model. [5]. Three different optimization algorithms are used to perform a comparative study of a quarter-car model for a balance design of suspension. The algoritms are presented by Chi, He and Natere in 2008, tire damping was neglected. [6]. A Quarter -car model (Non- linear) was used to measure random road excitation for presenting an optimization method on suspension damping and stiffness. Methods was presented in the year of 2006. [7].

A Quarter- car model of suspension is presented with a fuzzy logic to control damping of suspension system. All the results were in the form of velocity and displacement graphs which were compared with PID controllers results [8].To find excitation from a road profile using an LQR controller a mathematical model of active and passive suspensions are presented by Agharkakli, Chavan, and Phvithran in 2012. [9]. A quarter-model for a passenger car is presented by Utsav Gadhia and Sumant Patel in 2012. A simulation is performed in ADAMS for measuring a reaction of car in terms of wheel deflection vs time graph. Tire damping was neglected during simulation. [10]. A Power and acceleration driven damper were presented using a quarter model with three control approaches using a MATLAB-Simulink by Gasemalizadeh et. al.[11]. A quarter car model is presented by Tiwari & Mishra to study active control of vehicle suspension with the use of PID controls During simulation tyre damping was neglected. [12].

II. ANALYSIS OF SUSPENSION SYSTEM

For analysis of suspension system quarter car-model is used, where a simplified understanding of the system can be understood by the figure 1. Which is used to simulate the suspension system. The dynamic equation of the simplified model is presented by Fateh and Alavi in [13], The proposed equation is on the basis of analytical solution which might have been used in our ADAMS simulation. For an unforced damped Single DOF system, the general equation of motion becomes,

𝑚𝑥̈ + 𝑐𝑥̇ + 𝑘𝑥 = 0

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Figure 1: simplified quarter car model

Figure 2: data of wagon-r car suspension collected by precision measurement tool (digital Vernier caliper) As for simulation the data is needed, which is collected here by precision measuring tools, as shown in figure 3. The data collected from the experiment for spring and shock absorber is Kerb weight of the body (M) = 960kg, free length (Lf)= 225

mm, Ls= 125mm, wire diameter (d) = 10.82mm, Mean diameter (D) = ({Outer diameter(Do)–(d)}={133.55-10.82})

122.73mm, Bush Length(Lb) = 60mm, No of active coil(n’) =4, Total no of coil (n) = 6, From this data the following data will

be derived spring stiffness (k)= 34.25 N/mm, damping coefficient (C) = 2.151 N-s/mm. From the derived data the simulation will analyze the model and result will be generate. For getting the perfect result certain procedure have to be followed in ADAMS.

A. Analysis procedure in ADAMS

ADAMS as multibody dynamics software requires a CAD model which is to be analyze. Figure 2 explains the complete procedure for analysis in ADAMS

Figure 3: procedure to perform analysis in ADAMS For analysis of suspension following inputs were selected for certain reasons.

Table 1: Various input describing road conditions. Bump height Description

50 Small potholes, unfinished road surface, patchy road surface, etc, 100 Normal bump height, etc,

150 Elevated bumps, off-road condition, etc

Plot the graphs of the result using post processor.

Perform dynamic analysis for kerb weight and all passengers while applying various wheel deflactions Apply body weight and measure intial deflaction

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For stability of quarter- car model in ADAMS connection have to be done with transitional joint for simulation purpose. Connection detail of model is given in table 3 [10] Figure 4 indicates a cad model imported for simulation purpose.

Figure 4: quarter car model for simulation in ADAMS

III. SIMULATION RESULTS AND DISCUSSION

The series of simulations of quarter-car model performed in ADAMS. The simulation is performed for kerb weight and for each 5 passengers (As per AIS 68 kg per person) and for three different bump heights. Total 18 simulations were performed from that 72 different graphs were plotted. The results are in the form of graphs of forces vs time, body displacement vs time, body velocity vs time and phase portrait. These graphs give better understanding about the behavior of suspension of wagon-r car.

A. Simulation results for 50 mm of bump height for kerb weight and all 5 passengers

Figure 5: Force V/s Time graph of wagon-r suspension for 50 mm of bump height

Figure 6: Body displacement V/s Time graph of wagon-r car suspension for 50 mm of bump height

Figure 7: Body Velocity V/s Time graph of wagon-r car suspension for 50 mm of bump height

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B. Simulation results for 100 mm of bump height for kerb weight and all 5 passengers

Figure 9:Force V/s Time graph of wagon-r car suspension for 100 mm of bump height .

Figure 12 Phase portrait (body velocity V/s Displacement) graph of wagon-r car suspension for 100 mm of bump

height

C. Simulation results for 150 mm of bump height for kerb weight and all 5 passengers

Figure 13: Force V/s Time graph of wagon-r car suspension for 150 mm of bump height

Figure 16: Phase portrait (body velocity V/s Displacement) graph of wagon-r car suspension for 150 mm of bump

height

IV. CONCLUSION

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of the vehicle. Figure 17 shows the body displacement graph for 150 mm of bump height with 5 passengers, which indicates bouncier and less stable behavior. In this condition a car is safe to drive but passenger feels discomfort during the ride due to wavy motion.

Figure 17: Body displacement graph of wagon-R Car suspension showing wavy motion and residual underdamped

motion

Table2: Numerical data of body displacement for wagon-r car for 5 passenger and 150 mm of bump height.

Wagon -R Under damped wave 1st Wave 2nd Wave 3rd Wave 4th Wave T im e ta ke n t o st ab il iz e (s ec ond ) N o o f w ave be fo re bo dy st abi li za ti o n al ti tud e di ff er en ce ( m m ) al ti tud e di ff er en ce ( m m ) a lt it ude di ff er en ce ( m m ) a lt it ude di ff er en ce ( m m ) During

Heave 4 120.42 32 8.03 1.66 1.75

During Pot-hole

4 114.8 30 7 1 1.76

As shown in Table 2, There are two altitude differences are provided, one for heave and another for pot hole condition. IN both the cases a body motion extends up to 4 wave which is a clear indication of wavy and unstable body behavior of wagon-r cawagon-r due to existing suspension system. Fowagon-r stabilization and comfowagon-rt puwagon-rpose a wagon-reseawagon-rchewagon-r has a scope of wowagon-rk, which may optimize the results of the wagon-r car and passengers may ride more comfortably in future.

REFERENCES

[1] Don Knowles “AUTOMOTIVE SUSPENSION AND STEERING SYSTEM” published by Delmar Cengage Learning

Chapter 1. ISBN-13: 978-1-4354-8115-2,

[2] Abdelhaleem and D. Crolla, "Analysis and design of limited bandwidth active hydropneumatic Vehicle Suspension System", SAE Technical Paper 2000-01- 1631, 2000.

[3] M. Smith and F. Wang, "Performance benefits in passive vehicle suspensions employing inerters", Vehicle System Dynamics, vol.42, no.4, pp.235-257, 2004.

[4] G. Litak, M. Borowies, M. Friswell and K. Szabelski, "Chaotic vibration of a quarter-car model excited by the road surface profile", arXiv:nlin/0601030V1, 14 January, pp.1-18, 2006.

[5] D. Sammier, O. Sename and L. Dugard, "Skyhook and H∞ control of Ssemi-active suspensions: Practical

aspects",Vehicle System Dynamics, vol.39, no.4, pp.278-309, 2003.

[6] Z. Chi, Y. He and G. Naterer, "Design optimization of vehicle suspensions with a quarter-vehicle model", Transactions of the CSME/dela SCGM, vol.32, no.2, pp.296-313, 2008.

[7] G. Verros, S. Natsiavas and C. Papadimitriou, "Design optimization of quarter-car Mmodels with passive and semi-active suspensions under random road excitation", Journal of Vibration and Control, vol.11, pp.581-606, 2005.

[8] N. Changizi and M. Rouhani, "Comparing PID and fuzzy logic control a quarter-car suspension system", The Journal of Mathematics and Computer Science, vol.2, no.3, pp.560-565, 2011.

[9] A. Agharkakli, U. Chavan and S. Phvithran, "Simulation and analysis of pasive and active suspension system using quarter-car model for nonuniform road profile", International Journal of Engineering Research and Applications, vol.2, no.5, pp.900-906, 2012.

[10] Utsav Gadhia, Sumant Patel, “Quarter Model Analysis of Wagon-R car’s Rear Suspension using ADAMS, International Journal of Engineering Research and Technology, Vol. 1 (02), 2012, ISSN 2278 – 0181.

[11] O. Ghasemalizadeh, S. Taheri, A. Singh and J. Goryca, "Semi-active suspension control using modern methodology: A comprehensive comparison study", NDIA Ground Vehicle Systems Engineering and Technology Symposium, Novi, Michigan, 12-14 August, 2014.

[12] P. Tiwari and G. Mishra, "Simulation of quarter-car model", JOSR Journal of Mechanical and Civil Engineering, vol.11, no.2, pp.85-88, 2014.