1. Introduction

WJM

World Journal of Mechanics

2160-049X

Scientific Research Publishing

10.4236/wjm.2018.84010

WJM-84295

Articles

Engineering Physics&Mathematics

Static and Vibration Analysis of an Aluminium and Steel Bus Frame

Fatma

Rebaïne

¹^*Mohamed

Bouazara

¹Ahmed

Rahem

¹Lyne

St-Georges

Department of Applied Sciences, University of Quebec at Chicoutimi, Chicoutimi, Quebec, Canada

* E-mail:fatma.rebaine@uqac.ca(FR);

02042018

080411213520, March 201827, April 2018 30, April 2018

2014

This work is licensed under the Creative Commons Attribution International License (CC BY). http://creativecommons.org/licenses/by/4.0/

The transport sector is increasing day by day to satisfy the global market requirement. The bus is still the main mode of intercity transportation in Canada. Despite, an essentially unchanged conception, the total weight of the bus has increased by over 25% during the last three decades. To solve this problem, industrialists have moved to the use of light metals in the transportation field. Therefore, use of lightweight materials, such as aluminum is essential to reduce the total weight of bus. In this study, the focus is on the bus frame as it represents 30% of the total weight and it is the most stressed part of the bus. Its life duration is more important compared to that of all other elements. Thus, a study of the static and vibratory behavior would be very decisive. In this article, two types of analysis are carried out. First is the modal analysis to determine the natural frequencies and the mode shapes using a developed dynamic model of the bus. Because if any of the excitation frequencies coincides with the natural frequencies of the bus frame, then resonance phenomenon occurs. This may lead to excessive deflection, high stress concentration, fatigue of the structure and vehicle discomfort. In this case, the results analysis shows that the natural frequencies are not affected by the change of material. The second type of analysis is the linear static stress analysis to consider the stress distribution and deformation frame pattern under static loads numerically. For the numerical method, the frame is designed using SolidWorks and the analysis is made using Ansys WorkBench. The maximum Von Mises stress obtained for the static loading is in the same order for the three chassis frames studied. But in the case of the aluminium frame, the weight of 764 kg was reduced.

Bus Frame Aluminum Steel Modal Analysis Static Stress Analysis

1. Introduction

A bus frame represents the most stressed section in terms of excitation from the road or in terms of its main function of supporting structure. There have been several recent studies carried out at the level of this supporting structure, whether for car, truck, or bus. The focus of this different study was on design, geometry, static analysis, modal, and dynamic analysis. As for the work on design, different digital tools were used as Abaqus, Ansys, Catia, and SolidWorks. The most recent analyses were applied using the Ansys Workbench interface. The use of such finite element tools helps in accelerating design by minimizing the number of physical tests, thereby reducing the cost and the time.

Several static and modal studies have been established to evaluate the performance of the chassis. Among these works, M. Chandrasekar et al. [1] carried out an improved design of a ladder truck chassis using FE analysis under static and modal conditions. The results, obtained by using Ansys, show that shifting the third cross member away from the second gives better results. Mukesh Patil et al. [2] made a static and modal analysis by using Ansys Workbench for a tanker truck chassis to be able to evaluate maximum stress and natural frequencies of the frame. The results show that the maximum stress exceeds the ultimate tensile strength indicating that the structure is not safe. In this case, more investigations should be applied regarding design and load caring. Udhay Kiran S. et al. [3] present a linear static analysis of leader truck chassis by using Catia and Nastran Patran Workbench. Stress analysis is carried out on the chassis to find the critical point of maximum stress. In order to improve performance, geometry has to be modified. Manpreet Singh Bajwa et al. [4] performed a static load analysis and stress optimization of a tata super ace chassis using standard techniques of vehicle modification. Two methods of optimisation were used, mainly boxing and reinforcement techniques. The reinforcement technique using Ansys simulator at the highly stressed regions is found to be the most effective technique. There is also study of the vibration characteristics of the truck chassis and the stress distribution under various loading conditions presented by Teo Han Fui et al. [5] . The mode shape results determine the suitable mounting location of engine and suspension system. Another work regarding truck chassis is presented by Roslan Abd Rahman et al. [6] for the stress analysis of a heavy truck chassis loaded by static forces using Abaqus. The results show that the critical point of stress is significant as the value of safety factor is below the recommended value. In this case, more investigations should be performed to improve this result. Another work of structural static analysis of the truck chassis using Ansys workbench is presented by Vijaykumar V. Patel et al. [7] . A comparison between analytical and numerical results was presented. The numerical simulation obtained by Ansys for the Von Mises and shear stress was bigger 10% than result of the analytical calculation. This static analysis was performed to obtain the maximum stress and shear deformation of the chassis using static loading to be able to evaluate the capacity of the total frame.

Regarding the modal analysis [1] [2] [5] [8] , these studies were joined with the static analysis. It consists of calculating and representing the natural frequencies and mode shapes of the chassis. For the work presented by Kallappa Khannukar [8] , the modal analysis was carried out using both analytical and FEA techniques. The chassis is optimized by varying the design parameters with the help of the acceleration response of the system. Regarding other studies, the static analysis was used to evaluate the possibility of chassis weight reduction [9] [10] [11] . M. Ravi Chandra et al. [9] have presented the modeling of an existing heavy vehicle chassis with three different composite materials subjected to the same pressure as that of steel. They are made to be able to evaluate the reduction of the weight which is now the main issue in automobile industries. The results show that there is a reduction in weight of 73% to 80% compare to the steel frame, but the natural frequency is different. The work of Akshay Jain et al. [10] shows the possibility of reducing stress developed in the chassis frame and increase load carrying capacity. The study focused on the static load analysis with different thickness of chassis frame. The results show a weight reduction of about 1.2% and an increase in capacity by 40%. For the study presented by Patel Vitaykumar V. et al. [12] , a sensitive analysis was also carried out regarding the weight reduction by varying frame web height and thickness using FE analysis in Ansys Workbench. The results show a weight reduction by 6.68% of the chassis frame.

The variation of chassis member thickness was also used [12] [13] [14] to reduce weight, stress or to carry loads beyond the payload [15] . The chassis section was also varied in the work of Abhishek Singh et al. [16] to evaluate which section is more strength full than the other sections. The different sections are C, I, rectangular box (hollow) and rectangular box (intermediate). From simulations, it is observed that the rectangular box (intermediate) represents the more strength full section. The material was also varied [17] [18] to evaluate the variation in stress and deformation of the chassis frame.

2. Bus Frame Model

This study focuses on the static and vibration analysis of aluminium and steel chassis of the bus. The frame or chassis is the most significant part used for supporting the bus structure as it is subjected to several of both dynamic and static forces. In this section, the chassis specification, the frame loading and the different frame motion are presented.

2.1. Frame Specification

The bus frame model specified for this study consists of a single axle in front and tandem axles at the back with total length of 10.02 meters. Figure 1 present the bus frame model components and dimensions. It is the most common chassis used in buses. It has two long side members (longitudinal beams) and 5 cross members (transversal beams) joined together by welding.

The dimensions of the longitudinal and the transversal beams constituting the frame chassis are presented in Figure 2. It is a “C” channel section which is used for these beams; it has a good resistance to bending [15] .

To be able to reduce the weight of the existing standard steel frame (steel 1018-HR, steel 710C), the 6061-T6 aluminum alloy material was selected for this study. The characteristics of this aluminum alloy made it useful in the automotive field. The properties of the three materials are shown in Table 1. The vibration analysis and static loading of the frames made with these three materials are presented in this work.

2.2. Frame Loading

Regarding the loading, Quebec ministry of transportation [20] guideline states that in the case of this specified frame, the standard of the loads limits is equal to 18,000 kg. This value represents the sum of the allowable loads for each category

Table 1 Properties of the three materials

Properties	Aluminium 6061-T6	Steel 1018-HR	Steel 710C
Young’s modulus	7.31 × 10¹⁰ N/m²	210 × 10¹⁰ N/m²	207 × 10¹⁰ N/m²
Density	2700 kg/m³	7800 kg/m³	7800 kg/m³
Poisson ratio	0.33	0.28	0.30
Tensile strength	310 MPa	475 MPa	620 MPa
Elastic limit	275 MPa	275 MPa	550 Mpa

of axles. The mass of the major considered elements for this study are presented in Table 2.

For the case of an aluminum frame, the total static loading Q_s is equal to:

Q s = 18000 − ( Q 3-1 + Q 4 + Q 5 + Q 6 ) = 15087 kg (1)

Q s = 148003.5 N

For the tank and engine loads, they are applied separately then,

Q s 1 = Q s − ( Q 1 + Q 2 ) = 13 0 81 kg = 128324 . 64 N (2)

This static loading is applied on the longitudinal beam. There are two longitudinal beams, then Q s 1 is divided by two and it is uniformly distributed on each beam.

Load acting on the single beam:

128324.64 2 = 64162.32 N / beam (3)

・ Beam pressure

P beam = Q beam S beam = 100253.62 N / m 2 (4)

・ Tank pressure

P tank = Q tank S tank = 4248.92 N / m 2 (5)

・ Engine pressure

P engine = Q engine S engine = 5299.89 N / m 2 (6)

For the steel frame, the load acting on the single frame is equal to 60,419.80 N/beam and the beam pressure is equal to 94,217.50 N/m².

2.3. Dynamic Frame Motion

The frame is subjected to different motions as shown in Figure 3. The roll angle represents motion along the longitudinal axis. This motion is generated by the forces that are acting on the frame side. The pitch angle represents motion along

Table 2 Mass of the considered elements of this study

Elements	Mass (kg)
Filled tank (Q₁)	476
Engine (Q₂)	1530
Aluminum frame (Q_3-1)	404
Steel frame (Q_3-2)	1167
Front axle (Q₄)	724
Rear axle 1 (Q₅)	1224
Rear axle 2 (Q₆)	561

the transverse axis; it is a top downward motion. The yaw angle represents the motion along the vertical axis. This yaw angle is not predominant compared to the pitch and roll angles. Therefore, in this study the focus was set on pitch and roll angles only. The vertical motion was also studied.

3. Three-Dimensional Dynamic Frame Model

To be able to evaluate the motion of the bus frame, a three-dimensional dynamic model of the frame was developed. This model is presented in Figure 4; it is composed of six suspensions. This model has nine degrees of freedom; the first three degrees of freedom are related to the vertical motion, the pitch motion, and the roll motion in the bus. The other six-left degrees of freedom represent the vertical motion of the six suspensions.

The different parameters involved in this model are presented as follows:

Y 1 , 2 , 3 , 4 , 5 , 6 : Vertical motion of the six suspensions.

Y 7 : Vertical motion of the bus.

θ 7 : Pitch bus rotating angle.

∅ 7 : Roll bus rotating angle.

U i : Input excitation at the wheel i.

The different parameters values of this model are shown in Table 3.

Table 3 Three-dimensional model parameters

Definition	Symbol (Unit)	Value
Bus mass	m 7 ( kg )	15,491.5
Pitch moment	I θ ( kg ⋅ m 2 )	149,951.42
Roll moment	I ∅ ( kg ⋅ m 2 )	20,000.64
Distance (center gravity-wheel 1)	l 1 ( m )	2.25
Distance (center gravity-wheel 2)	l 2 ( m )	0.81
Distance (center gravity-wheel 3)	l 3 ( m )	2.25
Lateral distance	l 4 ( m )	1.25
Suspension rigidity for 1 and 4	k 1 , 4 ( N / m )	374,000
Suspension rigidity for 2, 3, 5 and 6	k 2 , 3 , 5 , 6 ( N / m )	435,000
Suspension damping i	b i ( N ⋅ s / m )	12,850
Tire rigidity i	k r i ( N / m )	2,800,000
Suspension mass for 1 and 4	m 1 , 4 ( kg )	362
Suspension mass for 2 and 5	m 2 , 5 ( kg )	611.83
Suspension mass for 3 and 6	m 3 , 6 ( kg )	280.42

3.1. Equation of Motion

The equations of motion of the bus frame are written separately for the six wheel assemblies and later for the total frame.

1) Wheel assembly 1: equation of motion

This case represents a single degree of freedom, because there is only vertical motion possible. Then, the equation of motion can be written using Newton’s second law as follows, where i is the number of axle.

∑ F = m i y ¨ i (7)

For positive displacement of the masses 1 and 7 and for positive rotation by pitch angle θ 7 and roll angle ∅ 7 , the forces acting on the front side of the frame at the wheel 1 are represented in Figure 5. U 1 and y 1 represent the input excitation to the wheel 1 and the vertical motion of the axle 1 respectively.

・ Tire equation

F k r 1 = k r 1 ( y 1 − U 1 ) (8)

・ Suspension equation

F k 1 = k 1 [ y 1 − ( y 7 + l 1 θ 7 + l 4 ∅ 7 ) ] (9)

F b 1 = b 1 [ y ˙ 1 − ( y ˙ 7 + l 1 θ ˙ 7 + l 4 ∅ ˙ 7 ) ] (10)

All the forces opposing the motion are negative.

m 1 y ¨ 1 = − k r 1 ( y 1 − U 1 ) − k 1 [ y 1 − ( y 7 + l 1 θ 7 + l 4 ∅ 7 ) ] − b 1 [ y ˙ 1 − ( y ˙ 7 + l 1 θ ˙ 7 + l 4 ∅ ˙ 7 ) ] (11)

The same procedure as the wheel assembly 1 was used to develop the different equations of motion for the wheel assemblies 2, 3, 4, 5 and 6.

2) Total frame: equation of motion

The frame of the bus, shown in Figure 4, is a rigid body with three degrees of freedom, namely, a bounce, a roll and a pitch. Consequently, the second law of Newton must be applied separately for each kind of motion:

∑ F = m 7 y ¨ 7 , ∑ M θ = I θ 7 θ ¨ 7 , ∑ M ∅ = I ∅ 7 ∅ ¨ 7 (12)

・ Bounce motion of the frame

For a positive vertical motion of the bus, all the suspensions elements act against it. Therefore, these forces are negative and the equation of bounce motion can be given by:

m 7 y ¨ 7 = − k 1 [ ( y 7 + l 1 θ 7 + l 4 ∅ 7 ) − y 1 ] − b 1 [ ( y ˙ 7 + l 1 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 1 ] − k 2 [ ( y 7 − l 2 θ 7 + l 4 ∅ 7 ) − y 2 ] − b 2 [ ( y ˙ 7 − l 2 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 2 ] − k 3 [ ( y 7 − l 3 θ 7 + l 4 ∅ 7 ) − y 3 ] − b 3 [ ( y ˙ 7 − l 3 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 3 ] − k 4 [ ( y 7 + l 1 θ 7 − l 4 ∅ 7 ) − y 4 ] − b 4 [ ( y ˙ 7 + l 1 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 4 ]

− k 5 [ ( y 7 − l 2 θ 7 − l 4 ∅ 7 ) − y 5 ] − b 5 [ ( y ˙ 7 − l 2 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 5 ] − k 6 [ ( y 7 − l 3 θ 7 − l 4 ∅ 7 ) − y 6 ] − b 6 [ ( y ˙ 7 − l 3 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 6 ] (13)

・ Pitch motion of the frame

For a positive pitch motion of the bus, all the suspension elements act against it. Therefore, these forces are negative and the equation of pitch motion can be given by:

I θ 7 θ ¨ 7 = − l 1 k 1 [ ( y 7 + l 1 θ 7 + l 4 ∅ 7 ) − y 1 ] − l 1 b 1 [ ( y ˙ 7 + l 1 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 1 ] − l 2 k 2 [ ( y 7 − l 2 θ 7 + l 4 ∅ 7 ) − y 2 ] − l 2 b 2 [ ( y ˙ 7 − l 2 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 2 ] − l 3 k 3 [ ( y 7 − l 3 θ 7 + l 4 ∅ 7 ) − y 3 ] − l 3 b 3 [ ( y ˙ 7 − l 3 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 3 ]

− l 1 k 4 [ ( y 7 + l 1 θ 7 − l 4 ∅ 7 ) − y 4 ] − l 1 b 4 [ ( y ˙ 7 + l 1 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 4 ] − l 2 k 5 [ ( y 7 − l 2 θ 7 − l 4 ∅ 7 ) − y 5 ] − l 2 b 5 [ ( y ˙ 7 − l 2 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 5 ] − l 3 k 6 [ ( y 7 − l 3 θ 7 − l 4 ∅ 7 ) − y 6 ] − l 3 b 6 [ ( y ˙ 7 − l 3 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 6 ] (14)

・ Roll motion of the frame

For a positive roll motion of the bus, all the suspension elements act against it. Therefore, these forces are negative and the equation of roll motion can be given by:

I ∅ 7 ∅ ¨ 7 = − l 6 k 1 [ ( y 7 + l 1 θ 7 + l 4 ∅ 7 ) − y 1 ] − l 6 b 1 [ ( y ˙ 7 + l 1 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 1 ] − l 6 k 2 [ ( y 7 − l 2 θ 7 + l 4 ∅ 7 ) − y 2 ] − l 6 b 2 [ ( y ˙ 7 − l 2 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 2 ] − l 6 k 3 [ ( y 7 − l 3 θ 7 + l 4 ∅ 7 ) − y 3 ] − l 6 b 3 [ ( y ˙ 7 − l 3 θ ˙ 7 + l 4 ∅ ˙ 7 ) − y ˙ 3 ]

− l 6 k 4 [ ( y 7 + l 1 θ 7 − l 4 ∅ 7 ) − y 4 ] − l 6 b 4 [ ( y ˙ 7 + l 1 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 4 ] − l 6 k 5 [ ( y 7 − l 2 θ 7 − l 4 ∅ 7 ) − y 5 ] − l 6 b 5 [ ( y ˙ 7 − l 2 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 5 ] − l 6 k 6 [ ( y 7 − l 3 θ 7 − l 4 ∅ 7 ) − y 6 ] − l 6 b 6 [ ( y ˙ 7 − l 3 θ ˙ 7 − l 4 ∅ ˙ 7 ) − y ˙ 6 ] (15)

By making the change of variables as presented below:

x 1 = y 1 , x 2 = y ˙ 1 , x 3 = y 2 , x 4 = y ˙ 2 , x 5 = y 3 , x 6 = y ˙ 3 , x 7 = y 4 , x 8 = y ˙ 4 , x 9 = y 5 , x 10 = y ˙ 5 , x 11 = y 6 , x 12 = y ˙ 6 , x 13 = y 7 , x 14 = y ˙ 7 , x 15 = θ 7 , x 16 = θ ˙ 7 , x 17 = ∅ 7 , x 18 = ∅ ˙ 7 (16)

The state system of the three-dimensional frame dynamic model has been developed. It is composed of eighteen unidentified variables. This system was solved using the Matlab software and the transfer functions were calculated. The parameters x 1 , x 3 , x 5 , x 7 , x 9 and x 11 represent the vertical motion of the six suspensions of the frame. The vertical, the pitch and roll motions of the frame corresponding to the transfer functions are related to the parameters x 13 , x 15 and x 17 . The corresponding matrix is presented below.

( x ˙ 1 x ˙ 2 x ˙ 3 x ˙ 4 x ˙ 5 x ˙ 6 x ˙ 7 x ˙ 8 x ˙ 9 x ˙ 10 x ˙ 11 x ˙ 12 x ˙ 13 x ˙ 14 x ˙ 15 x ˙ 16 x ˙ 17 x ˙ 18 ) = [ 0 1 0 0 0 0 ( − k r 1 − k 1 ) / m 1 ( − b 1 ) / m 1 0 0 0 0 0 0 0 1 0 0 0 0 ( − k r 2 − k 2 ) / m 2 ( − b 2 ) / m 2 0 0 0 0 0 0 0 1 0 0 0 0 ( − k r 3 − k 3 ) / m 3 ( − b 3 ) / m 3 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 ( k 1 ) / m 7 ( b 1 ) / m 7 ( k 2 ) / m 7 ( b 2 ) / m 7 ( k 3 ) / m 7 ( b 3 ) / m 7 0 0 0 0 0 0 ( k 1 l 1 ) / I 7 ( b 1 l 1 ) / I 7 ( k 2 l 2 ) / I 7 ( b 3 l 3 ) / I 7 ( k 3 l 3 ) / I 7 ( b 3 l 3 ) / I 7 0 0 0 0 0 0 ( k 1 l 4 ) / I 8 ( b 1 l 4 ) / I 8 ( k 2 l 6 ) / I 8 ( b 2 l 4 ) / I 8 ( k 3 l 4 ) / I 8 ( b 3 l 4 ) / I 8 ] [ 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 1 0 0 0 0 ( − k r 4 − k 4 ) / m 4 ( − b 4 ) / m 4 0 0 0 0 0 0 0 1 0 0 0 0 ( − k r 5 − k 5 ) / m 5 ( − b 5 ) / m 5 0 0 0 0 0 0 0 0 0 0 0 0 ( − k r 6 − k 6 ) / m 6 ( − b 6 ) / m 6 0 0 0 0 0 0 ( k 4 ) / m 7 ( b 4 ) / m 7 ( k 5 ) / m 7 ( b 5 ) / m 7 ( k 6 ) / m 7 ( b 6 ) / m 7 0 0 0 0 0 0 ( k 4 l 1 ) / I 7 ( b 4 l 1 ) / I 7 ( k 5 l 1 ) / I 7 ( b 5 l 1 ) / I 7 ( k 6 l 1 ) / I 7 ( b 6 l 1 ) / I 7 0 0 0 0 0 0 ( k 4 l 4 ) / I 8 ( b 4 l 4 ) / I 8 ( k 5 l 4 ) / I 8 ( b 5 l 4 ) / I 8 ( k 6 l 4 ) / I 8 ( b 6 l 4 ) / I 8 ]

| 0 0 ( k 1 ) / m 1 ( b 1 ) / m 1 0 0 ( k 2 ) / m 2 ( b 2 ) / m 2 0 0 ( k 3 ) / m 3 ( b 3 ) / m 3 0 0 ( k 4 ) / m 4 ( b 4 ) / m 4 0 0 ( k 5 ) / m 5 ( b 5 ) / m 5 0 0 ( k 6 ) / m 6 ( b 6 ) / m 6 0 1 ( − k 1 − k 2 − k 3 − k 4 − k 5 − k 6 ) / m 7 ( − b 1 − b 2 − b 3 − b 4 − b 5 − b 6 ) / m 7 0 0 ( − k 1 l 1 − k 2 l 2 − k 3 l 3 − k 4 l 1 − k 5 l 2 − k 6 l 3 ) / I 7 ( − b 1 l 1 − b 2 l 2 − k 3 l 3 − b 4 l 1 − b 5 l 2 − b 6 l 3 ) / I 7 0 0 ( − k 1 l 4 − k 2 l 4 − k 3 l 4 − k 4 l 4 − k 5 l 4 − k 6 l 4 ) / I 8 ( − b 1 l 4 − b 2 l 4 − b 3 l 4 − b 4 l 4 − b 5 l 4 − b 6 l 4 ) / I 8 |

| 0 0 ( k 1 l 1 ) / m 1 ( b 1 l 1 ) / m 1 0 0 ( − k 2 l 2 ) / m 2 ( − b 2 l 2 ) / m 2 0 0 ( − k 3 l 3 ) / m 3 ( − b 3 l 3 ) / m 3 0 0 ( k 4 l 1 ) / m 4 ( b 4 l 1 ) / m 4 0 0 ( − k 5 l 2 ) / m 5 ( − b 5 l 2 ) / m 5 0 0 ( − k 6 l 3 ) / m 6 ( − b 6 l 3 ) / m 6 0 0 ( − k 1 l 1 + k 2 l 2 + k 3 l 3 − k 4 l 1 + k 5 l 2 + k 6 l 3 ) / m 7 ( − b 1 l 1 + b 2 l 2 + k 3 l 3 − b 4 l 1 + b 5 l 2 + b 6 l 3 ) / m 7 0 1 ( − k 1 l 1 2 + k 2 l 2 2 + k 3 l 3 2 − k 4 l 1 2 + k 5 l 2 2 + k 6 l 3 2 ) / I 7 ( − b 1 l 1 2 + b 2 l 2 2 + b 3 l 3 2 − b 4 l 1 2 + b 5 l 2 2 + b 6 l 3 2 ) / I 7 0 0 ( − k 1 l 1 l 4 + k 2 l 2 l 4 + k 3 l 3 l 4 − k 4 l 1 l 4 + k 5 l 2 l 4 + k 6 l 3 l 4 ) / I 8 ( − b 1 l 1 l 4 + b 2 l 2 l 4 + b 3 l 3 l 4 − b 4 l 1 l 4 + b 5 l 2 l 4 + b 6 l 3 l 4 ) / I 8 |

+ ( 0 k r 1 0 k r 2 0 k r 3 0 k r 4 0 k r 5 0 k r 6 0 0 0 0 0 0 ) ( 0 U 1 0 U 2 0 U 3 0 U 4 0 U 5 0 U 6 0 0 0 0 0 0 ) (17)

3.2. Vibration Results

Generally, the range of frequencies in the field of road vehicles varies between 1 and 20 Hz. In the case of this study, by using the developed 3D model of the bus frame, the resonant frequencies were obtained. These frequencies are obtained with the bode diagram for the case of materials shown in Table 1. The results obtained for these three cases are presented below.

・ Aluminum 6061-T6 bus frame

The results of the resonance frequencies obtained in the case of the aluminum frame are presented in this section. Figure 6 shows bode diagram for the wheel assembly 1 of the frame. Bode diagram has two graphs, the first one is the amplitude as a function of the frequency; the second is the phase as a function of the frequency. Resonance occurs when the amplitude reaches to maximum and the phase is equal to π/2 (90˚). Thus, in this case, the resonant frequency of the wheel assembly 1 is equal to 14.35 Hz.

Figures 7-9 show the bode diagrams obtained for the total frame respectively in the case of bounce, pitch, and roll motion. For all three cases, the resonance frequency is equal to 1.80 Hz. These frequency results are less than 20 Hz, which corresponds to what is found in the literature [21] .

・ Steel 1018-HR and 710C bus frame

The comparison of the frequencies’ resonance results obtained for the designed frame with different materials presented in Table 4 shows a very great similarity. Therefore, the material does not affect the resonant frequencies in this study case. This assumes that the use of aluminum instead of steel in the frame design does not affect the resonant frequencies of the bus frame.

4. Structural Analysis

A structural analysis of the frame chassis is presented in this section. This analysis includes a static study as well as a vibratory study. The materials used for this study are aluminum 6061-T6, steel 1018-HR and steel 710C. This analysis is

necessary to know the capacities of the aluminum chassis in comparison with those made of steel. The use of aluminum in the transport sector would make it possible to have a great advantage in terms of weight reduction, energy consumption and even durability [17] [18] . The design of the chassis was first realized on SolidWorks, subsequently the structural analyzes were done with the

Table 4 Frequency results of the bus frame for the three materials

Frequency	Aluminum 6061-T6	1018-HR	710C
Wheel assembly 1 (Hz)	14.35	14.40	14.40
Bounce (Hz)	1.80	1.75	1.75
Pitch (Hz)	1.80	1.75	1.75
Roll (Hz)	1.80	1.75	1.75

tool of ANSYS Workbench. Many recent structural studies have been done using this software [1] [2] [4] [7] [9] , which is why in this case the ANSYS tool was used.

・ Frame mushing

In simulations, the first step consists in the choice of the material, subsequently the generation of the mesh followed by the boundary conditions and the loading part. It is the same mesh that is used for the three materials to be able to compare the results at the end.

The total frame is mushed with a tetrahedral element (Tet 10). In total, there is 1025281 elements and the number of nodes is equal to 1,738,446. Figure 10 present the frame meshing.

・ Loading and boundary conditions

The loading and boundary conditions of the aluminum and steel frames are presented in Figure 11. The loading conditions are assumed to be the same for steel and aluminum to be able to compare the results. In the case of aluminum frame, it is possible to add more weight (764 kg) to reach the maximum allowable loading limits. The static loads are assumed as a uniform distributed on the

two longitudinal beams obtained from the maximum admissible loading of the Quebec Ministry of transportation for this frame category. There are six boundary conditions in this model. All these boundary conditions are applied on the well axles of the frame. Two are on the front and the four others in the rear.

4.1. Static Analysis

This study was carried out to compare the mechanical strengths due to the static loading of the aluminum frame with those designed in steel. For this, an analysis of the maximum stresses undergone by the chassis; evaluations of the total displacement as well as the stresses due to the shearing were realized.

・ Aluminum 6061-T6

The static analysis of 6061-T6 aluminum frame is presented in this section. The values of the loads applied on the aluminum frame are presented in the section 2.2. For this static analysis, the maximum Van Mises stress equals to 195.30 MPa as shown in Figure 12(a) and Figure 12(b) is obtained near to the front axle. This value is overestimated du to the boundary conditions applied on the six axles locations. Another point is that the static loading applied during the simulation represents the maximum admissible loads allowed by Quebec ministry of transportation. The total displacement of aluminum frame presented in Figure 12(c) is equal to 0.038 m and the maximum shear stress presented in Figure 12(d) is equal to 102.50 MPa. The location of the maximum shear stress is the same as for the maximum Van Mises equivalent stress.

・ Steel 1018-HR and 710C frames

Table 5 presents the comparison between static analysis results of aluminum and steel frames. The comparison shows that there is a small difference between aluminum and steel frame results. Then, the aluminum frame can be used as same as the steel frame.

The static analysis results obtained for the 1018-HR steel frame are presented in Figure 13. The same results were obtained for the 710C steel frame. If the safety factor F_s is considered for the 6060-T6 aluminum and 1018-HR steel, the results will be:

F s = Elastic limit σ e Maximum stress σ max (18)

For aluminum and steel frames, the safety factor is eqal respectively to 1.41 and 1.39. This means that there no a big difference between the capacity of these two material in case of the static loading.

4.2. Modal Analysis

In this section, the static analysis of the frames made by the three different materials was presented to evaluate the capacity of the aluminum frames compared to those made of steel that is used now in transportation. Another important case to evaluate, is the modal analysis. For this modal analysis, all degrees of

Table 5 Static analysis results of the bus frame for the three materials

Static analysis	6061-T6	1018-HR	710C
Equivalent stress (MPa)	195.30	197.00	197.00
Total displacement (m)	0.038	0.013	0.013
Shear stress (MPa)	102.50	103.03	103.03

freedom are free to be able to evaluate the natural response of chassis frame. If one of the natural frequencies coincides with the frequency of the excitation rod, then resonance phenomena may occur with system breaks. Figure 14 shows the first bending and torsion vibration modes obtained for the aluminum frame. The focus was on the frequency between 1 up to 20 Hz approximately. The first mode corresponds to the torsion mode at 1.44 Hz. This result is also obtained by 3-D dynamic model presented in the section 3.2 that was equal to 1.80 Hz corresponding to the roll motion of the total frame. The first and second bending modes of the total are respectively equal to 9.10 Hz and 23.27 Hz.

The comparison of the frequency results for the four first vibration modes of the total frame for the three materials is given in Table 6. For the frames made with the 1018-HR and 710 C steel, the natural frequencies are the same. With the comparison of the aluminum and steel frames frequencies, the differences are small. Then it is possible to conclude that for modal analysis, the use of aluminum instead of steel does not affect the results.

5. Conclusions

Static and vibratory comparisons were made for a bus frame designed using three materials that are 6061-T6 aluminum, 1018-HR steel and 710C steel. The results analysis of the static study shows that the aluminum frame presents

Table 6 Vibration modes aluminum and steel frames

Vibration modes	Frequency (Hz)
Vibration modes	6061-T6	1018-HR	710C
Torsion-1^st mode	1.44	1.46	1.46
Bending-1^st mode	9.10	9.18	9.18
Torsion-2^nd mode	11.71	11.83	11.83
Bending-2^nd mode	23.27	23.51	23.51

stresses in the same order as those of steel. The generated shear and Von Mises stresses are less than the permissible value so the design is safe for all three materials. Knowing that the 6061-T6 aluminum has the same elastic limit stress as the 1018-HR steel which is equal to 275 MPa, both frames will have the same behavior. Then, it is possible to replace the steel frame with that of aluminum, knowing that the latter can fulfill functions equivalent to that of steel in addition to bringing many more advantages such as flexibility, lightness, a gain at the level of the energy consumption in addition to a high resistance to corrosion.

As for the vibratory study, the results also show a very great similarity between the frames designed in aluminum in comparison with those made of steel. This study was carried out dynamically and numerically. So, the change of material does not really affect the vibratory behavior in the design of a frame.

Acknowledgements

The financial support of the Aluminium Research Center (REGAL) is greatly appreciated.

Cite this paper

Rebaïne, F., Bouazara, M., Rahem, A. and St-Georges, L. (2018) Static and Vibration Analysis of an Aluminium and Steel Bus Frame. World Journal of Mechanics, 8, 112-135. https://doi.org/10.4236/wjm.2018.84010

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