Ijraset Journal For Research in Applied Science and Engineering Technology

Abstract

This paper deals with the design and manufacturing of shock absorbers for ATVs (All-Terrain vehicles). For this dual rate coil spring shock absorbers, we have considered an independent type double Wishbone arrangement for required off-road conditions. The purpose of designing and manufacturing this Shock absorber is to optimize the wheel assembly and to manufacture it less expensive, light in weight, and strong as per the off-road condition are addressed. This paper summarizes the design calculation, Analysis of components of shock absorbers, and manufacturing process required for this Suspension System of an ATV.

Introduction

I. INTRODUCTION

The main problem faced by exciting shock absorbers was that they were expensive and couldn’t be customized as per the vehicle requirement.

So, to solve this problem we decided to manufacture custom dual rate shock absorbers. The challenge we faced was finding out the proper material and manufacturing process for shock absorbers. As there were suitable materials available like chromo vanadium but that material, we must import from outside the country which could have increased the price which wasn’t matching our objective.

So that’s why we choose to go with IS4454 Grade 2 cold drawn spring material which had suitably good strength as compared with chrome vanadium. 

The limitation of our shock absorber is that one can use it only for the all-terrain vehicle and it has a cycle life of two years. After that, it won’t be reliable for use. 

The suspension system has a spring, a damper, and dual wishbones. The energy stored by the road shock causes the springs to respond in an expansion and contraction response.

These expansions and contraction responses are restricted to a reasonable level by the damper which is more commonly called a shock absorber.

The vehicle suspension system is responsible for vehicle control, driving comfort, and safety as the suspension carries the vehicle body and transmits all the forces between the rod and the body. The springs can take any shape and form depending upon the road conditions.

The helical springs are made up of wire in the form of a helix size and are primarily intended for compression or tension loads. The cross-section of wire from which the spring is made is Square and grounded type.

II. LITERATURE REVIEW

1. From our First reference, we got to know about the spring calculation required for designing spring. 
2. From this knew how we perform damper calculations to find the force acting inside the dampers. 
3. We understood how to prepare an experimental setup for the Shock absorbers and which point should be fixed and how to apply load on the setup. 
4. This paper provided us with the inside layout of the hydraulic shock absorbers and helped to choose the appropriate type of shock absorber. 

III. DESIGN PROCEDURE

Chart 3.1 Design procedure 

IV. SHOCK ABSORBER

A.  Methodology 

The shock absorber is an important part of automotive that influences ride characteristics such as ride comfort and driving safety. There are different kinds of automotive shock dampers such as moment-sensitive damping, acceleration-sensitive damping, and continuous damping control. The displacement & movement shock absorber has a similar structure compared to the conventional passive shock absorber. Damping qualities of automobiles can be analysed by considering the performance of displacement & movement-sensitivity shock absorbers for ride comfort. 

B. Function 

Vibration dampers are arranged parallel to the vehicle suspension and have the following tasks: to dampen vibrations of the vehicle’s body caused by uneven roads or driving conditions and to quickly reduce and eliminate the road-induced wheel and axle vibration to provide constant contact between the tire and the roadway.

C. Shock Absorber Selection 

The shock absorbers are one of the fundamental elements of a vehicle suspension system. Its function is to stop spring oscillation providing control, grip, stability, and control to the occupant of the vehicle. The shock absorber is a hydraulic device that works with mainly two types: 

1. Monotube hydraulic shocks 
2. Twin tube hydraulic shocks

Fig. 4.1:   Major Components of a Mono-Tube Damper [4] 

So, choose a monotube shock absorber over a twin tube shock absorber as per the given suitable condition for off-road which is as follows: 

1. As temperature increases, oil can release heat with less effort. 
2. Zero restrictions on installation angles. 
3. Larger oil capacity and greater heat dissipation allow for a stable damping force that is continuous. 
4. 100% efficiency overall temps. 
5. The piston valve is bigger and wider in a mono-tube design which allows for a wider area of pressure. In return, this means that the shock can create even a subtle dampening force precisely.

D. Components of shock absorbers

1. Shock Absorber Fluid Study: [4] Damper oil is usually a selected light mineral oil, sometimes instead of synthetic oil which is more expensive but may have reduced variation of viscosity with temperature. The usual mineral oil contains sulfurized compounds, giving it a persistent noxious scent. So, as per the given condition, we choose Sasol 57 oil and nitrogen gas of 25-30 bar pressure for a quick rebound for our shock absorber. The properties of the damping fluid, normally a mineral oil with some additives, can be classified under several headings, mainly chemical, mechanical, thermal, and other.
2. Material Selection: For manufacturing shock absorbers, we have used alloy steel material. As it is easily available in the market and easy to manufacture. The floating piston is made up of plastic material. The monotube shock absorber has two compartments, one section is for oil and another for nitrogen chamber and it is separated by a floating piston. 
3. Calculations 

Fig 4.2: Pressure space inside hydraulic mono shock absorbers [4] 

[2] 

???????????????????????????????????????????? = 14 mm 

???????????????????????????????????????????????????????? = 25 mm 

Pressure on the rod: - 

???????????????????????????????? = pressure * area 

???????????????????????????? = (???? ∗ ????????????????????????????????2 /4) 

???????????????????????????? = (???? ∗ 1424) = 153.93 ????????2

???????????????????????????????????????????? = ( ???????????????????????????????? /???????????????????????????? )

???????????????????????????????????????????? = (25 ∗ 9.81153.93) 

???????????????????????????????????????????? = 1.5932 N/ ????????2

The pressure of piston: - 

???????????????????????????????????????? = (???? ∗ ????????????????????????????????2/4) 

???????????????????????????????????????? = (???? ∗ 2524) = 490.87 ????????2

???????????????????????????????????????????????????????? = (???????????????????????????????????????????? / ????????????????????????????????????????)

???????????????????????????????????????????????????????? = (94.5 / 9.81490.87) 

= 1.8885 N/ ????????2 

Pressure during rebound: - 

???????????????????????????????????????????? = ???????????????????????????????????????? - ???????????????????????????? ???????????????????????????????????????????? = 490.87 – 153.93

???????????????????????????????????????????? = 336.94 ????????2

???????????????????????????????????????????????? = (???? 1− ???? 2) * ????????????????????????????????????????????

???????????????????????????????????????????????? = (1.88− 1.59) * 336.94 ???????????????????????????????????????????????? = 70.75 N 

Gas pressure: - 

???????????????????????????????? = ???????????????????????????????????????????? * ????????????????????????????

???????????????????????????????? = 25 * 153.93 

???????????????????????????????? = 3848.25 N

V. SPRINGS

A. Function 

The purpose of a spring is to cushion, absorb, or controlling of energy arising due to shock and vibration. It is also used for control of motion, storing energy, and measuring forces. 

B. Objective 

So, we are using two springs in series. The biggest advantage of a coil-over style shock absorber is as follows. The machined component design makes them easily adjustable, replaceable, and tuneable. The ability to fit a wide variety of coil spring rates and sizes makes them ideal for both supporting the vehicle’s weight and absorbing the inconsistencies on the road. Also, you can properly tune as per your coils and shock tuning is concerned to give you the utmost performance out of your suspension. 

Fig 5.2: Side view of shock absorbers with Dual coil spring 

The dual rate coil spring provides variable spring rates, which can be used to improve traction and handling in off-road conditions.

C. Material 

There are given below following materials that can be used for off-road vehicle shock absorbers. Mainly the good and highly chosen material for springs is chromo vanadium ASTM A231 because of its high strength and shock absorbing capacity go with IS4454 cold drawn spring steel which has moderate qualities as compared to chromo vanadium material. 

D. Calculations 

Characteristics of cold drawn steel IS4454 grade 2:

Min. tensile strength=1290 Mpa 

Modulus of rigidity (G) = 73000 Mpa FOS=1.5 

Tensile strength=1290 N/mm 

Shear stress=0.6*1290=774/FOS =516 N/mm 

Required travel of spring front = 4 inches 

1. Primary Spring 

[1] Force, P = 2100 N 

Wahl’s Stress factor (K) = 

K = ((4 ???? −1/4 ???? −4) – (0.615/????)) = 1.23 

Shear stress (????????) = 

???????? = K (8 ∗ ???? ∗ ????/???? ∗ ????2) 

????2 = (8 ∗ ???? ∗ ????/???? ∗ ????????) 

d = 9 mm 

Diameter of Wire coil = 9mm 

Diameter of spring, D 

D = Cd = 59 mm

Deflection of the spring, ???? 

???? = (8 ∗ ???? ∗ D3 ∗ ????/???? ∗ ????4) 

N = (???? ∗ ????4 ∗ 8 ∗ ???? ∗ ???? 3 ∗ ????) = 9 

Total no. coil, ???????? 

???????? = N + 2 = 11 

Solid length = ???????? * d = 99 mm 

Actual deflection of the spring, ???? 

???? = (8 ∗ ???? ∗ D3 ∗ ????/???? ∗ ????4) = 64.83 mm 

Gap = (???????? −1) ∗ 2 = 20 ???????? 

Free length = Solid length + ???? + Gap 

Free length = 183.83 mm 

The pitch of coil = (???????????????? ????????????????????? /???????? −1) =18.38 mm

Spring rate, ????1 = (????????) = 39.37 N/mm 

Actual spring rate, ???? 1 

????1 = (???? ∗ ????4 /8 ∗ D3 ∗ ????) = 40.36 N/mm

2. Secondary Spring 

[1] Force, P = 1500 N 

Wahl’s Stress factor (K) = 

K = ((4 ???? −1/4 ???? −4) – (0.615/????)) = 1.208 

Shear stress (????????) = 

???????? = K (8 ∗ ???? ∗ ????/???? ∗ ????2) 

????2 = (8 ∗ ???? ∗ ????/???? ∗ ????????) 

d = 8 mm 

Diameter of Wire coil = 9mm 

Diameter of spring, D 

D = Cd = 57 mm 

Deflection of the spring, ???? 

???? = (8 ∗ ???? ∗ D3 ∗ ????/???? ∗ ????4) 

N = (???? ∗ ????4 ∗ 8 ∗ ???? ∗ ???? 3 ∗ ????) = 9 

Total no. coil, ????????

???????? = N + 2 = 7 

Solid length = ???????? * d = 56 mm 

Actual deflection of the spring, ???? 

???? = (8 ∗ ???? ∗ D3 ∗ ????/???? ∗ ????4) = 37.16 mm 

Gap = (???????? −1) ∗ 2 = 12 ???????? 

Free length = Solid length + ???? + Gap 

Free length = 105.16 mm 

The pitch of coil = (???????????????? ????????????????????? /???????? −1) =17.52 mm 

Spring rate, ????1 = (????????) = 39.37 N/mm 

Actual spring rate, ???? 1 

????1 = (???? ∗ ????4 / 8 ∗ D3 ∗ ????) = 40.36 N/mm

3. Calculations to check to buckle of Primary spring 

[5] K = (???? ∗ ????/ 8 ∗ ????3 ∗ ????) 

N = (???? ∗ ???? 8 ∗ ????3 ∗ ????) = 9 

Pitch = 18.38 mm 

Checking torsional shear stress 

Considering static failure 

Let static shear stress factor, ???????? 

???????? = 1 + (0.5 ????/????) = 1.076 

Static shear stress, ???????? 

???????? = ???????? (8 ∗ ???? ∗ ????/???? ∗ ????3) = 465.68 N/mm 

By considering the curvature effect, 

???????? = ((4 ???? −1/4???? −4) – (0.615/????)) = 1.23 

The shear stress induced by the curve effect is given by.

???????? = ???????? (8 ∗ ???? ∗ ????/???? ∗ ????3) = 532.33 N/mm 

Check for buckling of the two ends of the fixed spring

( ???????????? ) ≤ 5.2 

3.55 ≤ 5.2 

So, the bucking will not occur this spring.

4. Calculations to check to buckle of Secondary spring 

[5] K = (???? ∗ ????/ 8 ∗ ????3 ∗ ????) 

N = (???? ∗ ???? 8 ∗ ????3 ∗ ????) = 8

Pitch = 17.52 mm 

Checking torsional shear stress considering static failure 

Let static shear stress factor, ???????? 

???????? = 1 + (0.5 ????/????) = 1.070 

Static shear stress, ???????? 

???????? = ???????? (8 ∗ ???? ∗ ????/???? ∗ ????3) = 56.83 N/mm 

By considering the curvature effect, ???????? = 

???????? = ((4 ???? −1/4???? −4) – (0.615/????)) = 1.208 

The shear stress induced by the curve effect is given by.

???????? = ???????? (8 ∗ ???? ∗ ????/???? ∗ ????3) = 64.16 N/mm 

Check for buckling of the two ends of the fixed spring

(????????????) ≤ 5.2 

3.62 ≤ 5.2 

So, the bucking will not occur this spring.

E.  Manufacturing 

We have done two major processes while manufacturing that is winding machine and finishing process of springs. 

Fig 5.2: After spring got manufactured 

1. Winding Machine Process: To start with spring manufacturing, you must have a winding machine. A winding machine is a machine that will pull your wire around and make it coil up into a spring shape. What kind of winding machine you'll need depends on what size wire you'll be working with, and, how many springs you want to make. 
2. Finishing Process: After coiling your springs and forming the ends, you will need to get rid of the stress that folding the wire has caused. To do this, an oven is needed. Your oven temperature depends on what material you use for your spring.

VI. FEA ANALYSIS

Fig 5.2: a sectional view of shock absorbers

The Designing has been done in Solid works software and its finite element analysis has been done in Ansys software. The analysis has been done by considering off-road condition forces to test the factor of safety in the worst situation during bumps. The shock absorber mounting points were constrained and force was applied at the bottom of the shock absorber as per the actual vehicle working scenario. 

A.  Fine Meshing 

Fig 6.1.: After Fine meshing shock absorbers

No. of Nodes = 107918 

No. of Elements = 58460 

Element Quality = 0.8484 

Mesh type = 3D (Tetra-Hedrons) 

B. Maximum Stress 

Fig 6.2.: Max. stress analysis 

C. Deformation 

Fig 6.3.: Deformation analysis 

D. Results

Maximum stress occurring in knuckle is 700.02 Mpa and deformation is 60.30mm having FOS 1.84. 

VII. RESULTS VALIDATION

Fig 7.1: Test conducted on UTM of shock absorbers

[3] We performed an experimental study for design validation. Physical testing on the Dual rate coil spring shock absorber was done by Compression Testing. The testing was done by a 10-ton universal testing machine along with a load cell having a load carrying capacity of 1000 kg as in figure 7.1. The Entire Shock absorber with springs was tested at a time. The tested shock absorbers were mounted both at the top and bottom. After that shock absorber with springs got compressed for deflections 4 inches and applied a load of 2100N which is the total weight of the vehicle using the load cell. And we found out that our manufactured component got zero failure and it is safe to use in All-terrain vehicles. 

Conclusion

In ATV shock absorbers deal with unexpected situations like road shocks, bumps, etc. so, the basic point of designing and manufacturing this was as follows: - 1) Provides great articulation to the vehicle • It is comfortable in complicated road conditions. 2) Variable spring rate improves traction and handling of the vehicle. As compared to other commercial stiff and expensive shock absorbers this is leak-proof at a high damping, soft while bumps and easily manufactured at low cost. And we also proved that our shock absorber didn’t get any breakage at the universal testing machine as well as during the FEA test. So, we conclude that this experiment of designing and manufacturing custom shock absorbers is successful and can be used for all-terrain vehicles.

References

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Copyright

Copyright © 2022 Ravi Thakur, Shrinath Kulkarni. 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.