 Open Access
 Total Downloads : 755
 Authors : Mihir Joshi
 Paper ID : IJERTV3IS071382
 Volume & Issue : Volume 03, Issue 07 (July 2014)
 Published (First Online): 31072014
 ISSN (Online) : 22780181
 Publisher Name : IJERT
 License: This work is licensed under a Creative Commons Attribution 4.0 International License
Design of Permanent Magnet Suspension Systems for 2 WheelersTVS Star Bike
Mihir Joshi
(Mechanical Engineering Department, Walchand Institute of Technology, Solapur)
ABSTRACT : The suspension of a motorcycle contributes to vehicles handing and braking in such a way that it isolates the passengers from bumps, vibrations in order to provide comfort.Suspensions are categorized as Front Fork and Rear Cushion Suspensions. We however are particularly interested in the most common form of front suspension for a modern motorcycle i.e. a telescopic fork suspension.Shock absorbers consist of a spring which determines posture and cushioning buffer action a damper which reduces vibration.Our purpose is to obtain natural frequency of vibration of the damper system.The experimental setup of FFT analyzer is connected to suspension system and modes of vibration are extracted from the unit. The traditional choice in motorcycle front suspension systems is the telescopic fork. Although after many decades of development the performance of such systems is often already adequate, the design inherit disadvantages are still present. With the help of experimental analysis in realtime condition the time domain and frequency domain values are obtained. This paper reviews the topic in a way of aiming to develop a methodology for a quick andeffective diagnostic procedure that could be carried out in any repair facility
Keywords Damping, FFT Analyzer,Mode Shapes, Natural Modes of Frequencies, Suspension System.
INTRODUCTION:
This paper addresses the issue of vibration analysis of suspension system with use of experimental setup.The frequencies at which vibration naturally occurs, and the modal shapes which the vibrating system assumes are properties of the system, and can be determined analytically using Modal Analysis. Our involvement here is in obtaining values of mode shapes from experimental setup of FFT analyzer. The Fast Fourier Transform (FFT) and the power spectrum are powerful tools for analyzing and measuring signalsfrom plugin data acquisition (DAQ) devices. For example, we can effectively acquire time domain signals, measure the frequency content, and convert the results to realworld units and displays as shown on traditional benchtop spectrum and network analyzers. The basic functions for FFTbased signal analysis are the FFT, the Power Spectrum but additional measurement functions such as frequency response,impulse response, coherence, amplitude spectrum, and phase spectrum. It involves the marking of certain positions on
the suspension bar, keeping required points fixed and attaching the accelerometer sensors to other positions, collectively taking the readings to obtain mode shape frequencies

INTRODUCTION TO THE PROBLEM Shock absorbers are an important part of automobile and motorcycle suspensions, aircraft landing gear, and the supports for many industrial machines. The shock
absorbers duty is to absorb or dissipate energy. One design consideration, when designing or choosing a shock absorber, is where that energy will go. The suspension used here is of motorcycle TVSStar. Five points were marked over the length of suspension bar, and the sensors were fixes to one of the points in order to fix its single degree of freedom. Impact Hammer was used in order to excite the particles of the bar, and readings are obtained in Data Acquisition System.
Positioning of Sensors and Excitation by Hammer:
The whole length of the Telescopic Suspension was mainly divided into 5 parts depending upon the convenience of sensor positioning. The surface of the suspension is cleaned so as to remove all oil traces and remove all the dust from it, So as to position the sensor properly and acquire the proper grip on it. The Sensors are positioned alternatively at position 1, 3, 5 and simultaneously the excitation was done using impact hammer at all positions except at that where the sensor is mounted. Corresponding readings are taken from the Data Acquisition System and NaturalFrequency and mode shapes are plotted and calculated from the plots obtained.
Fig. (I)
Impact Hammer:

DYTRAN Impact Hammer 1pc
Impact hammer is basically used for transient excitation. The Impact Hammer test has very distinct advantage. The input spectrum from the impact is
flat out to the rolloff the frequency with no holes in the spectrum. It is very convenient technique and is
used for lightly damped linear test structures and very high quality Frequency Response Function (FRF).
Accelerometer Sensors:

Accelerometer Sensors 2pc
The accelerometer generates an output signal that is proportional to the acceleration of the vibrating mechanism. The accelerometers are light in
weight, compact and capable of measuring vibrations at specified points. The output produced from the accelerometer depends upon the sensitivity moreover it does not need any structural loading. However accelerometer mounting, interconnection cables are the critical factors to look for while analysis.
Accelerometer Sensors are used to obtain frequency values and pass it to the Data Acquisition System for analysis, Accelerometer sensors are connected at points where the vibrations are to be sensed, which are caused due the help of excitation made by Impact Hammer.


INDENTATIONS AND EQUATIONS The two working conditions are as:

FreeFree Condition

Fixed Condition
The first paragraph under each heading or subheading should be flush left, and subsequent paragraphs should have a fivespace indentation. A colon is inserted before an equation is presented, but there is no punctuation following the equation. All equations are numbered and referred to in the text solely by a number enclosed in a round bracket (i.e., (3) reads as "equation 3"). Ensure that any miscellaneous numbering system you use in your paper cannot be confused with a reference [4] or an equation (3) designation.


FIGURES AND TABLES:
Free Free Condition:
The FreeFree condition is required in Modal analysis,
4
50
Phase (Â°)
50
150 Marker4 ( 20.9375 Hz: 23.27 Â° )
250
350
6
Marker6 ( 309.063 Hz: 256.74 Â° )
5
Marker5 ( 772.5 Hz: 214.15 Â° )
however the condition is difficult to achieve. So the
0 200 400 600 800 1 k
Frequency (Hz)
Suspension system is generally conditioned using Soft Spring of negligible mass and good stiffness value. The freefree condition once achieved produces displacement when any external force acts on it.The excitation was done as stated earlier and the data was collected for further analysis.
The FreeFree Condition is as shown:
7
1.6
(Acceleration)/(Force) ((g)/(N))
1.4
1.2
1
800 m Marker7 ( 25 Hz: 140.7 m(g)/(N) )
600 m
400 m
200 m
1 2 3
Marker1 ( 803.125 Hz: 1.548 (g)/(N) )
Marker2 ( 861.875 Hz: 491 m(g)/(N
Marker3 ( 975 Hz: 137 m(g)/(N) )
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 1.2(a)
1
Phase (Â°)
50
Marker8 ( 434.375 H
50
9 8 2
150 Marker4 ( 20.9375 Hz: 48.48 Â° )
250
350
Marker9 ( 402.5 Hz: 719.71 Â°z:) 719.56 Â° )
Marker5 ( 772.5 Hz: 490.06 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
6 7
1.6
(Acceleration)/(Force) ((g)/(N))
1.4
3 4 5
Marker1 ( 803.125 Hz: 1.158 (g)/(N) )
1.2
1
p>800 m Marker7 ( 25 Hz: 111.7 m(g)/(N) )
600 m
400 m
Marker8 ( 305.313 Hz: 2.158 (g)/(N) )
Marker2 ( 861.875 Hz: 532 m(g)/(N
Marker3 ( 975 Hz: 306.2 m(g)/(N)
200 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig 1.3(b)
Fig. (II)
1
Phase (Â°)
600
Marker8 ( 434.375 H
200
9 8 2
200 Marker4 ( 20.9375 Hz: 449.17 Â° )
600
Marker9 ( 402.5 Hz: 359.66 Â°z:) 357.31 Â° )
Marker5 ( 772.5 Hz: 399.74 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
6 7
2.5
3 4 5
Marker1 ( 803.125 Hz: 1.622 (g)/(N) )
(Acceleration)/(Force) ((g)/(N))
2
Fig. (III) Fig. (IV)
1.5
1
Marker7 ( 25 Hz: 227.5 m(g)/(N) )
Marker8 ( 305.313 Hz: 2.144 (g)/(N) )
Marker2 ( 861.875 Hz: 653 m(g)/(N
Marker3 ( 975 Hz: 360.4 m(g)/(N)
500 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig 1.4(c)
Fig. (V)
The graphs of the FreeFree Conditions obtainedFrom FFT Analyzer are:
1
Phase (Â°)
600
Marker8 ( 434.375 H
200
9 8 2
Phase (Â°)
600
200
1
Marker5 ( 772.5 Hz: 209.88 Â° )
200
600
Marker4 ( 20.9375 Hz: 552.95 Â° )
Marker9 ( 402.5 Hz: 183.05 Â° )z: 186.4 Â° )
Marker5 ( 772.5 Hz: 117.62 Â° )
200
600
0 200 400
Frequency (Hz)
600 800 1 k
0 200 400 600 800 1 k
Frequency (Hz)
5
2.5
)/(N) )
Marker1 ( 803.125 Hz: 938 m(g
2 3 4
6 7
2.5
(Acceleration)/(Force) ((g)/(N))
2
3 4 5
Marker1 ( 803.125 Hz: 227.7 m(g)/(N) )
2
(Acceleration)/(Force) ((g)/(N))
1.5
z: 302.5 m(g)/
1.5
1
Marker7 ( 25 Hz: 130.5 m(g)/(N) )
Marker8 ( 305.313 Hz: 2.331 (g)/(N) )
Marker2 ( 861.875 Hz: 67.2 m(g)/(
Marker3 ( 975 Hz: 14.99 m(g)/(N)
1
500 m
Marker2 ( 861.875 H
Marker8 ( 305.313 Hz: 1.53 (g)/(N) )
Marker3 ( 975 Hz: 29.99 m(g)/(N)
500 m
0 200 400 600 800 1 k
Frequency (Hz)
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 3.4(g)
1
Fig 1.5(d)
600
Phase (Â°)
200
200
Marker5 ( 772.5 Hz: 390.34 Â° )
1
Phase (Â°)
600
Marker8 ( 434.37
200
9 8 2
600
0 200 400 600 800 1 k
Frequency (Hz)
200
600
Marker4 ( 20.9375 Hz: 282.21 Â° )
Marker9 ( 402.5 Hz: 0.03 Â°5) Hz: 1.54 Â° )
Marker5 ( 772.5 Hz: 246.88 Â° )
5
2.5
2 3 4
0 200 400 600 800 1 k
(Acceleration)/(Force) ((g)/(N))
Frequency (Hz) 2
Marker1 ( 803.125 Hz: 301.3 m(g)/(N) )
2.5
(Acceleration)/(Force) ((g)/(N))
2
1.5
1
6
Marker7 ( 25 Hz: 211.1 m(g)/(N) )
7
Marker8 ( 305.313 Hz: 3.616 (g)/(N) )
3 4 5
Marker1 ( 803.125 Hz: 1.163 (g)/(N) )
Marker2 ( 861.875 Hz: 609 m(g)/(N
Marker3 ( 975 Hz: 227.5 m(g)/(N)
1.5
1
500 m
Marker8 ( 305.313 Hz: 1.94 (g)/(N) )
Marker2 ( 861.875 Hz: 116.9 m(g)/
Marker3 ( 975 Hz: 16.94 m(g)/(N)
500 m
0 200 400 600 800 1 k
Frequency (Hz)
0 200 400 600 800 1 k
Frequency (Hz)
Fig 3.5(g)
1
600
Fig 3.1(e)
1
200
Phase (Â°)
200
600
Marker5 ( 772.5 Hz: 584.22 Â° )
600 0 200 400 600 800 1 k
Phase (Â°)
Frequency (Hz)
200
200
600
Marker5 ( 772.5 Hz: 682.31 Â° )
5
2.5
2 3 4
Marker1 ( 803.125 Hz: 490 m(g)/(N) )
(Acceleration)/(Force) ((g)/(N))
0 200 400 600 800 1 k 2
Frequency (Hz)
5
2.5
(Acceleration)/(Force) ((g)/(N))
2
1.5
2 3 4
Marker1 ( 803.125 Hz: 1.205 (g)/(N) )
Marker2 ( 861.875 Hz: 590 m(g)/(N
1.5
1
500 m
Marker8 ( 305.313 Hz: 2.701 (g)/(N) )
Marker2 ( 861.875 Hz: 270.3 m(g)/
Marker3 ( 975 Hz: 79.6 m(g)/(N) )
1
500 m
Marker8 ( 305.313 Hz: 383.4 m(g)/(N) )
Marker3 ( 975 Hz: 310.2 m(g)/(N)
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 5.1 (h)
0 200 400 600 800 1 k
Frequency (Hz)
Fig 3.2(f)
Phase (Â°)
600
200
200
600
1
Marker5 ( 772.5 Hz: 42.16 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
5
2.5
2 3 4
(Acceleration)/(Force) ((g)/(N))
Marker1 ( 803.125 Hz: 630 m(g)/(N) )
2
1.5
Marker2 ( 861.875 Hz: 317.6 m(g)/
Marker8 ( 305.313 Hz: 379.4 m(g)/(N) )
1
Marker3 ( 975 Hz: 161.8 m(g)/(N)
500 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig 5.2(i)
Phase (Â°)
600
200
200
1
Marker5 ( 772.5 Hz: 403.8 Â° )
600
0 200 400 600 800 1 k
Frequency (Hz)
Fig. (VI)
5
2.5
2 3 4
(Acceleration)/(Force) ((g)/(N))
Marker1 ( 803.125 Hz: 404.8 m(g)/(N) )
2
1.5
Marker2 ( 861.875 Hz: 84.7 m(g)/(
Marker8 ( 305.313 Hz: 2.808 (g)/(N) )
1
Marker3 ( 975 Hz: 72.9 m(g)/(N) )
500 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 5.3 (j)
Phase (Â°)
600
200
200
600
1
Marker5 ( 772.5 Hz: 149.02 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
5
2.5
2 3 4
(Acceleration)/(Force) ((g)/(N))
Marker1 ( 803.125 Hz: 426.8 m(g)/(N) )
2
1.5
Marker2 ( 861.875 Hz: 162 m(g)/(N
Marker8 ( 305.313 Hz: 1.326 (g)/(N) )
1
Marker3 ( 975 Hz: 56.8 m(g)/(N) )
Fig. (VII)
500 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig 5.4 (k)
Fixed Condition:
In fixed condition the Telescopic Suspension was placed in the Jaws of chuck and it was placed vertically.
The excitation was done as stated earlier and the data was collected for further analysis. The setup made for the Fixed Condition is as follows:
Fig.(VIII)
Phase (Â°)
600
200
200
600
1
Marker1 ( 73.4375 Hz: 148.24 Â° )
2
Marker2 ( 227.5 Hz: 717.48 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
6 5 3 4
450 m
Marker6 ( 27.8125 Hz: 168.8 m(g)/(N) )
(Acceleration)/(Force) ((g)/(N))
400 m
350 m
300 m
250 m
200 m
150 m
100 m
50 m
Marker5 ( 76.5625 Hz: 209.1 m(g)/(N) )
Marker3 ( 745.625 Hz: 260.6 m(g)/(N) )
Marker4 ( 864.688 Hz: 474.9 m(g)/(N) )
0 200 400 600 800 1 k
Frequency (Hz)
Fig:1.3 (m)
Phase (Â°)
600
200
200
600
2 43
Marker2 ( 171.875 Hz: 719.5 Â°)
Marker3 ( 275.313 Hz: 719.92 Â°)
Marker4 ( 269.375 Hz: 717.65 Â°)
0 200 400 600 800 1 k
Frequency (Hz)
Fig. (IX)
The graphs of the Fixed Conditions Obtained from FFT Analyzer are:
450 m
(Acceleration)/(Force) ((g)/(N))
400 m
350 m
1
Marker1 ( 286.25 Hz: 417.3 m(g)/(N) )
5 7 6
Marker7 ( 856.875 Hz: 597 m(g)/(N) )
Phase (Â°)
600
200
200
1
Marker1 ( 43.75 Hz: 19.7 Â° )
2
Marker8 ( 267.5 Hz: 719.04 Â° )
300 m
250 m
200 m
150 m
Marker5 ( 759.375 Hz: 252.3 m(g)/(N) )
Marker6 ( 913.438 Hz: 228.9 m
600
0 200 400 600 800 1 k
Frequency (Hz)
100 m
50 m
Marker4 ( 26.875 Hz: 144.8 m(g)/(N) )23.9 m(g)/(N)
) Marker7 ( 270.313 Hz: 81.5 m(g)/(N) )
Marker2 ( 845 Hz: 440.9 m(g)/(N) )
5 4 6 3
450 m
(Acceleration)/(Force) ((g)/(N))
400 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 1.4 (n)
350 m
300 m
5 4
600
Marker3 ( 75.625 Hz: 2
250 m
200 m
200 Marker5 ( 195.938 Hz: 700.76 Â° )
Phase (Â°)
200
600
Marker4 ( 268.438 Hz: 708.02 Â° )
150 m
0 200 400 600 800 1 k
Frequency (Hz)
100 m
50 m
0 200 400 600 800 1 k
Frequency (Hz)
250 m
(Acceleration)/(Force) ((g)/(N))
200 m
2 1 3
Marker1 ( 856.875 Hz: 265.6 m(g)/(N Marker2 ( 802.188 Hz: 115.9 m(g)/(N) )
Fig. 1.2 (l)
150 m
100 m
50 m Marker3 ( 960.31 Hz: 132 m(g)/(N) )
0 200 400 600 800 1 k
Frequency (Hz)
5
Phase (Â°)
100
100
300
500
Marker5 ( 26.875 Hz: 27.02 Â° )
Fig 1.5 (o)
6
Marker6 ( 277.188 Hz: 12.49 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
1
1.2
2 3 4
Marker1 ( 312.188 Hz: 1.131 (g)/(N) )
(Acceleration)/(Force) ((g)/(N))
1 Marker2 ( 809.063 Hz: 881 m(g)/(N) )
800 m
600 m
Marker3 ( 920.625 Hz: 568
400 m
Marker4 ( 993.13 Hz: 332.3 m(g)/(N) )
200 m
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 3.1 (p)
5
Phase (Â°)
600
200
200
600
Marker5 ( 26.875 Hz: 126.44 Â° )
6
Marker6 ( 277.188 Hz: 315.29 Â° )
5
Phase (Â°)
600
200
200
600
Marker5 ( 26.875 Hz: 554.78 Â° )
6
Marker6 ( 277.188 Hz: 322.1 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
0 200 400 600 800 1 k
Frequency (Hz)
1.8
(Acceleration)/(Force) ((g)/(N))
1.6
1.4
1.2
1
Marker1 ( 312.188 Hz: 35.47 m(g)/(N) )
2 3 4
Marker2 ( 809.063 Hz: 400 m(g)/(N) )
1
(Acceleration)/(Force) ((g)/(N))
200 m
150 m
Marker1 ( 312.188 Hz: 31.16 m(g)/(N) )
2 3 4
Marker2 ( 809.063 Hz: 102.4 m(g)/(N) )
1
800 m
600 m
400 m
200 m
Marker3 ( 920.625 Hz: 428
Marker4 ( 993.13 Hz: 245.1 m(g)/(N) )
100 m
50 m
Marker3 ( 920.625 Hz: 45.
Marker4 ( 993.13 Hz: 32.82 m(g)/(N) )
0 200 400
Fig 3.2 (q)
Frequency (Hz)
600 800 1 k
0 200 400 600 800 1 k
Frequency (Hz)
Fig 5.1 (t)
5
Phase (Â°)
600
200
200
600
Marker5 ( 26.875 Hz: 36.38 Â° )
6
Marker6 ( 277.188 Hz: 219.27 Â° )
5
Phase (Â°)
600
200
200
Marker5 ( 26.875 Hz: 375.53 Â° )
6
Marker6 ( 277.188 Hz: 650.27 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
600
0 200 400 600 800 1 k
Frequency (Hz)
1.8
(Acceleration)/(Force) ((g)/(N))
1.6
1.4
1.2
1
Marker1 ( 312.188 Hz: 678 m(g)/(N) )
2 3 4
Marker2 ( 809.063 Hz: 672 m(g)/(N) )
1
Marker1 ( 312.188 Hz: 3.473 m(g)/(N) )
Marker2 ( 809.063 Hz: 145.9 m(g)/(N) )
Marker3 ( 920.625
Marker4 ( 993.13 Hz: 88.1 m(g)/(N) )
200 m
2 3 4
1
800 m
600 m
400 m
200 m
Marker3 ( 920.625 Hz: 202
Marker4 ( 993.13 Hz: 65.2 m(g)/(N) )
150 m
(Acceleration)/(Force) ((g)/(N))
100 m
50 m
Hz: 116
0 200 400 600 800 1 k
Frequency (Hz)
Fig. 3.4 (r)
0 200 400 600 800 1 k
Frequency (Hz)
5
Phase (Â°)
100
100
300
500
Marker5 ( 26.875 Hz: 57.21 Â° )
6
Marker6 ( 277.188 Hz: 271.26 Â° )
5
Phase (Â°)
600
200
200
Marker5 ( 26.875 Hz: 30.28 Â° )
Fig 5.2 (u)
6
Marker6 ( 277.188 Hz: 81.97 Â° )
0 200 400 600 800 1 k
Frequency (Hz)
600
0 200 400 600 800 1 k
Frequency (Hz)
1.8
(Acceleration)/(Force) ((g)/(N))
1.6
1.4
1.2
1
Marker1 ( 312.188 Hz: 51.6 m(g)/(N) )
2 3 4
Marker2 ( 809.063 Hz: 203.2 m(g)/(N) )
1
(Acceleration)/(Force) ((g)/(N))
200 m
150 m
Marker1 ( 312.188 Hz: 19.63 m(g)/(N) )
2 3 4
Marker2 ( 809.063 Hz: 119.6 m(g)/(N) )
1
800 m
600 m
400 m
200 m
0 200 400
Frequency (Hz)
Marker3 ( 920.625 Hz: 79.
Marker4 ( 993.13 Hz: 63.8 m(g)/(N) )
600 800 1 k
100 m
50 m
0 200 400
Frequency (Hz)
Marker3 ( 920.625 Hz: 54.
Marker4 ( 993.13 Hz: 18.52 m(g)/(N) )
600 800 1 k
Fig 3.5 (s)
Fig. 5.3 (v)
5
Phase (Â°)
600
200
200
600
Marker5 ( 26.875 Hz: 18.24 Â° )
6
Marker6 ( 277.188 Hz: 2.21 Â° )
REFERENCES
0 200 400 600 800 1 k
Frequency (Hz)

The Fundamentals of FFTBased Signal Analysis and
Marker1 ( 312.188 Hz: 37.28 m(g)/(N) )
Marker2 ( 809.063 Hz: 272.6 m(g)/(N) )
Marker3 ( 920.625
Marker4 ( 993.13 Hz: 83.6 m(g)/(N) )
1
(Acceleration)/(Force) ((g)/(N))
200 m
150 m
100 m
50 m
2 3 4
Hz: 17
Measurement Michael Cerna and Audrey F. Harvey

The thesis of selected mountain bike front suspension forks on handlebar vibration and ground reaction forces Marnie Laser lakehead University

A Multibody virtual dummy for vibrational analysis in car and motorcycle environments LMS International nv, Simulation Division, Belgium

Analysis of Alternative Front Suspension Systems for
0 200 400 600 800 1 k
Frequency (Hz)
Fig 5.4 (w)
Realtime analysis output


TABLES &RESULTS
Motorcycles BasileiosMavroudakis, Peter Eberhard Institute of Engineering and Computational Mechanic, University of Stuttgart, Germany

Analysis of Automotive Damper Data and Design of a PortableMeasurement System Grant A. Malmedahl Ohio State university

MagnetoRheological Dampers for Supersport Motorcycle Applications John W. Gravatt Virginia Polytechnic Institute and State University
CONCLUSION:
Sr. No. 
Condition 
Measured Length 
1 
Suspension Length when its fixed on bike 
34.2 cm 
2 
Reading taken when bike is loaded 
31.6 cm 
3 
Free length of suspension after removing it from bike 
35.2 cm 
Table of Displacement data:
Sr. No. 
Natural Frequency (Hz) 
1. 
269.5 
2. 
312.188 
3. 
759.625 
4. 
846.688 
5. 
960.31 
6. 
933.13 
7. 
1025.32 
8. 
1205.42 
9. 
1365.42 
10. 
1493.62 
11. 
1678.2 
12. 
1998.72 
13. 
2105.12 
14. 
2321.21 
15. 
2457.32 
16. 
3215.32 
Loading Load (Y) 
Deform 
Deform 
Avg 
(X) 
Disp 

1 
2.25 
35.45 
35.45 
35.45 
33.65 
1.55 
2 
12.25 
34.75 
34.45 
34.6 
32.8 
2.4 
3 
20 
32.1 
32.3 
32.2 
30.4 
4.8 
4 
30 
30 
30 
30 
28.2 
7 
5 
40 
28.9 
28.9 
28.9 
27.6 
8.1 
6 
50 
27.7 
27.5 
37.6 
25.8 
9.4 
7 
60 
26.6 
26.6 
26.6 
24.8 
10.4 
8 
70 
26 
26 
26 
24.2 
11 
9 
80 
26 
26 
26 
24.2 
11 