DESIGN AND FABRICATION OF MECHANICAL VIBRATION … · requirements toward designing mechanical vibration exciter which can be used as an input device for analyzing vehicle behavior

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International Journal of Mechanical Engineering and Technology (IJMET) Volume 7, Issue 6, November–December 2016, pp.58–75, Article ID: IJMET_07_06_007

Available online at

http://www.iaeme.com/ijmet/issues.asp?JType=IJMET&VType=7&IType=6

Journal Impact Factor (2016): 9.2286 (Calculated by GISI) www.jifactor.com

ISSN Print: 0976-6340 and ISSN Online: 0976-6359

© IAEME Publication

DESIGN AND FABRICATION OF MECHANICAL

VIBRATION EXCITER

Aditya Pawar, Sumit Vajre, Shubham Patil, Ashish Badade and Kamlesh Sasane

Fr. Agnel Institute of Technology, India.

ABSTRACT

A vibration exciter is a machine which produces mechanical vibratory motion to provide forced

vibration to a specimen on which modal analysis and testing is to be performed. This article

presents the design & construction of a mechanical vibration exciter which ha s a cam and follower

mechanism used to generate uniaxial vibrations. The exciter is designed to produce displacement

through a given range of frequencies. The construction of working device and its important parts

and the results obtained from FFT analyser are described here.

Key words: Mechanical, Vibration.

Cite this Article: Aditya Pawar, Sumit Vajre, Shubham Patil, Ashish Badade and Kamlesh Sasane,

Design and Fabrication of Mechanical Vibration Exciter. International Journal of Mechanical

Engineering and Technology, 7(6), 2016, pp. 58–75.

http://www.iaeme.com/ijmet/issues.asp?JType=IJMET&VType=7&IType=6

1. INTRODUCTION

A vibration exciter is a force generator that provides vibration, shock, or modal excitation source for

testing and analysis produces mechanical vibratory motion to test object. The exciters are designed to

produce a given range of harmonic or time dependent excitation force and displacement through a given

range of frequencies. These machines can be mechanical, electro-hydraulic or electro-dynamic in nature.

Vibration exciters are used for development, simulation, production, studying the effects of vibration, and

simulate the shock or vibration conditions found in aerospace, construction, agricultural, automobile, etc. [1]

After invention of vehicles, advancement in each section has been in full force in improving the

performance of the vehicle like vibration isolation, ride comfort, stability and efficiency. Ride comfort

problems mainly arise from vibrations of the vehicle body, which may be induced by a variety of sources,

including surface irregularities, aerodynamic forces, vibrations of the engine and driveline, and imbalances

of the tire against assembly. Usually, surface irregularities excite the vibration of the vehicle body.

Vibration exciter acts as an input to the designed models of vehicle and those models can be analyzed by

different ways to improve vibration behavior of vehicle. [2,3]

Design and Fabrication of Mechanical Vibration Exciter


1.1. LITERATURE SURVEY

The literature survey has been done for collecting information regarding the design and fabrication of

mechanical vibration exciters. Our literature survey is based on: a] design b] type of exciter c] type of input

d] type of testing.

S. H. Sawant et al[4]

have designed a vibration exciter for the analysis of a quarter car model. They

have mentioned that their analysis is based on the fact that a road can be considered as an infinite cam with

wavy profile of harmonic waves and the wheel of quarter car model as follower. As the road is considered

as cam which will give harmonic road excitation to vehicle an eccentric cam can be used as exciter for

vibration analysis. Their experimental setup has been studied which was used for this purpose. It consists

of a shock absorber attached to a compression spring. The load equal to sprung weight is applied by

tightening nut on it. An eccentric cam is used to provide excitation is placed at the bottom of shock

absorber, which is connected to shaft of an electric motor. The displacement of shock absorber due to cam

rotation is measured by FFT analyzer by mounting accelerometer at upper mount of shock absorber. Thus,

the experimental setup used here, can be used for a single type of motion.

Brain Wallace and Brandon Dawe [5]

have designed a vibration exciter table for beam and plate

vibrations for laboratory demonstration. Their primary objective was to perform experiments like

excitation of beams, round plates, square pates and rectangular plates and slip tables, of different materials.

They have mentioned that the stroke range was 3.18mm. However, for slip table application, it was capable

of providing a stroke of 70mm. On examining their report, it was found that they used cam and follower

mechanism to provide the required vibrations. The cam profile selected for desired results was S.H.M

profile. The roller used was a sealed roller bearing type, from Detroit Ball Bearing (p/n SSRI-814). In

order to determine the frequency at which the shaker was operating, a reflective photo-transistor and a

frequency to voltage converter was used. A Hewlett Packard Dynamic Signal Analyzer (model # 35670A)

and ICP Sensor Power Unit (model # 480E09) were used to capture the data from the accelerometer. The

Digital Signal Analyzer was used to output the operating frequency of the shaker as well as acceleration.

This frequency output allowed for proper calibration of the photo-transmitter. Their results show that cam

and follower mechanism can be used for simple harmonic motion.

Nitinkumar Anekaret al [6]

have designed an exciter machine for experimentation purpose and testing

products at different frequencies. They have designed the exciter taking both static and dynamic load

conditions. It is observed that they considered spring as an important part in the design and hence,

designed it under static and dynamic conditions to check under surging and fatigue. The exciter consisted

of five main parts: base frame, drive system (motor), eccentric mass, spring& top plate. The exciter was

mainly made of mild steel, except elements like disc attached to motor, which was made of aluminum. The

base frame was made of channel. The drive system includes a permanent magnet type DC motor with

variable speed. The disc with eccentric mass was attached to motor shaft at one end. This system was fixed

to top plate which is also used to hold the samples. To achieve different excitations, the variable speed

knob was attached to DC motor to control both speed and excitations. The drive system achieved a speed

between 0 rpm to 1440 rpm. Thus, their exciter simply uses an eccentric mass to provide forced vibrations.

L.A.B. Equipment, Inc. [7]

, published online catalogue having specification mentioning frequency,

dimension of shaker table, amplitude for given payload. For example, for a payload of 91kg, frequency is 8

Hz to 60 Hz, displacement is 1.3 mm, table size is 610 x 610 mm.

Essential components have been discussed in literature survey. Available literature fulfills our

requirements toward designing mechanical vibration exciter which can be used as an input device for

analyzing vehicle behavior.



1.2. Aim and Objective

Vibration exciter is an important device that is used for testing of structures that are subjected to cyclic

loading. It acts as an external source of vibration, to simulate conditions in which the specimen under test

will be working. Mechanical vibration exciters are of lower cost than other types and can be used for

laboratory experiments.

Thus, the aim and objective of our project is to design and fabricate mechanical vibration exciter for

providing S.H.M. and sudden jerk motion.

1.3. Problem Definition

Mechanical vibration exciters can accommodate only a single type of output like SHM. These

conventional cam profiles cannot provide shocks and sudden jerks. V.Ryan [8]

has mentioned model of

snail/drop cam which can be used for providing a sudden jerk motion. So it was planned to fabricate a

vibration exciter with multiple output using cams of different profiles. Hence the problem definition is

“Design and development of mechanical vibration exciter with multiple outputs.”

1.4. Scope of the Project

The scope of our project work includes design of mechanical vibration exciter using cam and follower

mechanism. Two types of motions will be provided using S.H.M. profile and drop profile of cam. The

scope also includes selection of materials, fabrication and testing of the exciter using FFT analyzer.

In order to design vibration exciter, its components like cam, follower, shaft and springs have to be

designed, which are discussed in the next chapter.

CHAPTER 2

2. DESIGN AND DEVELOPMENT

The previous chapter gave an introduction to the concept of the project and literature review help in

deciding the components to be used and parameters that can affect the results of the project.

This chapter will include the discussion regarding the layout of the project and design considerations

based on calculations. The experimental layout, components and their functions are explained in figure 2.1.

2.1. Proposed layout of Mechanical Vibration Exciter

The layout consists of four cams, two of each type, mounted on the shaft symmetrically as shown in figure

2.1. The follower body is threaded so that only two cams of same type are in contact at a time.

Figure 2.1 Proposed design of Mechanical Vibration Exciter



2.2. Components of Mechanical Vibration Exciter

This section will show the various components that will be incorporated in this project along with their

brief description.

• Cam and Follower: The cam and follower mechanism will be used for providing the vibrations. Two

types of cam profiles will be used for two different outputs, namely: S.H.M profile and Snail/Drop

profile.

• Spring: Coil springs of ASTM A228 will be used to maintain the contact between the cam and the

follower.

• Bearing: Bearings will be used to provide support to the shaft.

• Shaft: The shaft will be connected the motor and will carry the cams on it. A keyway will be provided

on the shaft so as to fix the cams on it.

• Jaw Coupling: The motor shaft will be connected to the shaft carrying the cams via anJaw coupling.

• Motor: A motor of 1 HP power rating will be used to drive the shaft.

2.3. Design Calculations

The design calculations for shaft, cams and follower, key and springs are given below. These calculations

were done with the help of design criteria mentioned in the reference book and the design data book. [9][10]

2.3.1. Shaft

The design power for shaft is taken as 2kW considering factor of safety. The motor speed is taken to be

1000rpm.

Data:

Let �� = 2 ��, = 1000 ��

The Eq. (1) will give the torque acting on the shaft

� = ��/(�� ) = 19.1 � (1)

1. V.F.D

∑ �� = 0,

∴ � + �" = 1000

# $ = 0 500 × 160 + 500 × 240 = �" × 400

∴ �" = 500

∴ � = 500

2. V.B.M.D $) = $* = 80000 ��


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Figure 2.2 shows the shear forc

Figure

Let, �, = �- = 2

The Eq. (2) will give the equivalent moment acting on the shaft

$, = .(2$/)� + (The Eq. (3) will be used to find out the diameter of shaft

�τ� = 12345*6 = 81 /

Let, 7 = 30 ��

Thus, the diameter of shaft is 30 mm.

2.3.2. Cam and Follower (SHM Motion)

Generally, mechanical exciters provide displac

the maximum rise of cam. Base circle radius is taken as 40mm and the width as 20mm.


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shows the shear force and bending moment acting on the shaft.

Figure 2.2 Force and moment acting on shaft

The Eq. (2) will give the equivalent moment acting on the shaft

(2�)�

∴ $, = 164.5 × 109 ��

The Eq. (3) will be used to find out the diameter of shaft

/��

∴ 7 = 22 ��

Thus, the diameter of shaft is 30 mm.

Cam and Follower (SHM Motion)

Generally, mechanical exciters provide displacement up to 30mm. For our project, we have taken 10mm as



[email protected]

(2)

(3)

ement up to 30mm. For our project, we have taken 10mm as




Figure 2.3 shows the forces acting on cam and the symbols used for various dimensions of the cam and

the follower.

Figure 2.3 Forces acting on cam and follower

Data:

Maximum lift,ℎ; = 10 �� - = 40 ��, < = 20 �� = 1000 ��, � = 400 ,σ>, = 400 /��

Ɵ- = Ɵ@ = 150°,Ɵ* = 60°

Design of cam: -

rC = 40 + 10 = 50 ��

The Eq. (4) will give the value of angular velocity of cam

ω = �� = 105 E7/F (4)

The Eq. (5) will give the value of linear velocity of cam

G = H�I�J (sin �N

J ) (5)

AtO = 0°and O = P we will get G = 0

O = J� , G = G; Q ,

G; Q = ℎRω2P = 0.63 �/F

E@ = R�O� × ℎ;2 × S� = 79.38 �/F�

E; Q = 79.38 �/F�

� = ℎ; = 10 ��



The Eq. (6) will give radius of curvature of cam surfa

) = U V@WX>YZX(@WX>)ZX�( [\)Z]

The Eq. (7) will give contact stresses between cam and follower

(σ)) = 189.8^_`- (a

Thus, the induced stress value is less than the design value of contact stres

Follower body:

The follower body dimensions are based on the dimensions of the roller, which has diameter of 20 mm

and width of 20 mm.

Thread: $46 × 2

Design of Roller pin:

The roller pin is designed to withstand the double shear failure.

The Eq. (8) will give the value for diameter of roller pin

�; Q = 2π c*WZd e �τ�

Let, 7C = 8 ��

Thus, the safe value of roller pin is 8 mm.

Figures 2.4 & 2.5 shows the cam and follower mode

calculations & its behaviour shown in Figure 2.6


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�; Q = �; = 400

adius of curvature of cam surface

Y Xf[ɷhZ

](@WX>)iZɷZ

j6Z = 53.7 ��

ontact stresses between cam and follower

a@ + a

@k) = 222.75 /�� l 1130 /��

Thus, the induced stress value is less than the design value of contact stress.


7 = 46 ��


�τ� = 45 /��

The Eq. (8) will give the value for diameter of roller pin

c e � � = 400

∴ 7C = 3 ��

Thus, the safe value of roller pin is 8 mm.

Figures 2.4 & 2.5 shows the cam and follower models prepared on Autodesk Inventor as per the design


Figure 2.4 Inventor Model of SHM Cam


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(6)

(7)

s.


(8)

ls prepared on Autodesk Inventor as per the design



Blue – displacement, Yellow

2.3.3. CAM and Follower (SNAIL CAM)

After designing the SHM profile cam, the second type, i.e., drop cam is designed. Its maximum

10mm and base circle radius is taken as 40mm and the width as 20mm.

Data: -

Maximum lift, ℎ; = 10 �� - = 40 ��, < = 20 �� = 1000 ��, � = 400 ,σƟ- = 270°,Ɵ@ = 0°, Ɵ* = 90°Design of cam: -


Displac

ement,

Velocit

y,

Acceler

ation


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Figure 2.5 Inventor Model of Follower

displacement, Yellow – velocity, Red- acceleration

Figure 2.6 Graphs for SHM cam

(SNAIL CAM)

After designing the SHM profile cam, the second type, i.e., drop cam is designed. Its maximum

ase circle radius is taken as 40mm and the width as 20mm.

σ>, = 400 /��

°

rC = 40 + 10 = 50 ��


Angular Displacement


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acceleration

After designing the SHM profile cam, the second type, i.e., drop cam is designed. Its maximum rise is



ω = �� = 105 E7/F (9)

The Eq. (10) will give the value of linear velocity of cam

G = H�I�J (sin �N

J ) (10)

At O = 0° and O = P we will get G = 0

O = J� , G = G; Q ,

G; Q = ℎRω2P = 0.35 �/F

Em = R�O� × ℎ;2 × S� = 24.5 �/F�

E; Q = 24.5 �/F�

� = ℎ; = 10 ��

�; Q = �; = 400

The Eq. (11) will give the value of radius of curvature of cam

) = U V@WX>YZXf[ɷhZ

(@WX>)ZX�( [\)Z](@WX>)iZɷZ

j6Z = 62.31 �� (11)

The Eq. (12) will give the value of contact stresses between cam and follower

(σ)) = 189.8^_`- (a@ + a

@k) = 218.14 /�� l 1130 /�� (12)

Thus, the induced stress value is less than the design value of contact stress.

Follower body: -


and width of 20 mm. 7 = 46 ��

Thread: $46 × 2

Design of Roller pin:


�τ� = 45 /��

The Eq. (13) will give the value of diameter of roller pin

�; Q = 2π c*WZd e �τ� = 400 (13)

∴ 7C = 3 ��

Let, 7C = 8 ��

Thus, the safe value of roller pin is 8 mm



Figures 2.7 & 2.8 shows the cam and follower models prepared on Autodesk Inventor as per the design


Fig

Blue – displacement, Yellow

Displac

ement,

Velocit

y,

Accele

ration


IJMET/index.asp 67

shows the cam and follower models prepared on Autodesk Inventor as per the design


Figure 2.7 Inventor Model of Snail Drop Cam

Figure 2.8 Inventor Model of Follower

displacement, Yellow – velocity, Red- acceleration.

Figure 2.9 Graphs for snail cam

Angular Displacement


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shows the cam and follower models prepared on Autodesk Inventor as per the design

acceleration.



2.3.4. Spring

The spring design is based on fatigue loading. �; Q = 400 , δ; Q = 10 ��, o = 6

Material: ASTM A228 p = 79.3 p�E, qr, = 1800 /��,

�τ� = 504 /��

The Eq. (14) will give the value of Wahl stress factor

�s = fd)]ad)]dh = 1.2525 (14)

The Eq. (15) will give the value of wire diameter of the spring

τ = �s(t_)�*Z) (15)

7 = 4 ��

u = 24 ��

Hence, the wire diameter is 4 mm and the coil diameter is 24 mm

The Eq. (16) will give the value of number of coil

� = _viwxviw = 40/�� = y × *t )6z (16)

∴ (Eo{|G}) ~ = 7

({�{E�)~` = ~ + 2 = 9 Thus, the total number of turns is 9.

The Eq. (16) will give the value of solid length of spring

�� = (~ + 2)7 = 36 �� (17)

The Eq. (18) will give the value of free length of spring

�" = �� + δ; Q + (~` − 1) × 1 = 54 �� (18)

The Eq. (19) will give the value of pitch of spring

Lf = pn+2d (19)

∴ p = 6.6 mm

Thus the value of pitch is 6.6mm.

2.3.5. Key

The key will be subjected to shear and crushing stresses. So it is designed to withstand these stresses.

7� = 30 ��

The Eq. (20) will give the value of width of key

� = *�d = 9�d (20)

∴ � = 7.5 ��

The width of key is 7.5 mm.

The Eq. (21) will give the value of height of key



ℎ = �9 × � = 5 �� (21)

The height of key is 5 mm.

� = 30 ��

The Eq. (22) will give the value of force acting on key

� = �� = d�.��×a�6

a� = 3184 (22)

�τ� = 45 /��

�σ)@� = 135 /��

The Eq. (23) will give the actual value of shear stress

(τ) = _s × � = 14.15 /�� (23)

The Eq. (24) will give the actual value of crushing stress

(σ)@) = _H × � = 21.23 /�� (24)

Thus, the actual crushing stress is less than the permissible value of crushing stress.

Thus, the dimensions of the keys that are found out are safe.

The design of shaft, cams, follower, key and springs is done and their calculated stress values are

within the specified limit, so these parts can be taken for manufacturing; hence in next chapter a complete

part list can be discussed.

CHAPTER 3

3. FABRICATION OF VIBRATION EXCITER

3.1. Fabrication of Vibration Exciter

In this chapter, different components of vibration exciter are described in terms of their dimensions given

in Table 3.1. The shaft was fabricated on lathe machine. The cams were made on VNC machine. The IGES

files of the cams were opened in Master Cam software to get the co-ordinates for VNC machining. The

follower was made using lathe and VNC machine. Internal threading in plate was done by tapping. Deep

groove ball bearings and springs were directly purchased from the market. The fabricated parts of vibration

exciter such as shaft, SHM cam, Jerk cam and follower are shown in diagram 3.1, 3.2, 3.3, 3.4 and 3.5

respectively.

Table 3.1 Part list with dimensions.

Sr.

No. Component Dimensions

Material

Quantity

1. Shaft Diameter: 30 mm

Length: 700 mm

EN 19 1

2. SHM Cams

Base circle radius: 40mm

Maximum rise: 10mm

Width: 20 mm

EN 24 2

3. Drop Cams Base circle radius: 40mm

Maximum rise: 10mm

EN 24 2



Figure 3.1Shaft used in Mechanical Vibration Exciter

Figure 3.2 S.H.M Cam

Width: 20 mm

4. Follower

Roller radius: 20 mm

Roller width: 20 mm

Roller pin diameter: 8mm

Body diameter: 42 mm

Body length: 150 mm

MS 4

5. Key

Height: 5 mm

Width: 7.5 mm

Length: 20 mm

MS 4

6. Deep groove ball bearing

ID: 30 mm

OD: 62mm

Width: 16mm

2

7. Plate

Length: 600 mm

Width: 600 mm

Thickness: 6 mm

MS 1



Figure 3.3 Snail/Drop Cam

Figure 3.4 Threaded follower

Figure 3.5 Vibration exciter plate with reinforcement

In vibration exciter there is a provision of two SHM cams and two Snail cams, while hence fabrication

of shaft has four key slots to incorporate all four cams. To avoid linear motion of cams on shaft, circular

circlips are accommodated along with cams. Threaded followers with roller at its one end is to make line

contact with cam simultaneously other end which is threaded is used for easy engagement of any one type

of input profile like SHM or Jerk. The M.S. top plate works as an actuator to facilitate movement of



threaded follower reinforcement is attached with four equidistant threaded holes. .A complete assembly is

shown in Figure 3.6.

Figure 3.6 Complete Assembly of Vibration Exciter

Assembly of vibration exciter with its all the components and input as 1 HP motor with variable speed

is need to be tested and its output at vibration exciter plate has to be analyzed, the same is discussed in next

chapter.

CHAPTER 4

4. RESULT AND ANALYSIS OF VIBRATION EXCITER

4.1. Results

The mechanism used to operate one type of input at one time in vibration exciter having two different type

of cam profile on same shaft is represented in fig. 4.1 and 4.2 as SHM input and jerk input. It’s been shown

in both the figures, two types of cams consider type A and type B. Where type A has jerk type motion and

those cams are mounted on the shaft at the outer ends, where as type B has SHM type motion and those

cams are mounted on the shaft at the central portion. The output is measured by using FFT analyzer i.e.

output/amplitude in frequency domain. For Jerk motion and SHM motion, output is shown in Figure 4.3

and 4.4 respectively.

Figure 4.1 Schematic Diagram for Jerk Motion.

Follower

Drop

cam

SHM

cam



Figure 4.2

For jerk type, the input is provide

recorded in figure 4.3 acts as 2 cm maximum

direction.

-2

-1.5

-1

-0.5

0

0.5

1

1.5

2

2.5

0

Dip

lace

me

nt

(cm

)

-15

-10

-5

0

5

10

15

0.192

Dip

lace

me

nt

(cm

)

Follower


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Figure 4.2 Schematic Diagram for SHM Motion.

Figure 4.3 Output for jerk motion

the input is provided as 1 cm as a jerk with periodic up and down movement,

4.3 acts as 2 cm maximum in upward direction and -1.6cm min

Figure 4.4 Output for SHM motion

0.5 1 1.5

Time (sec)

Jerk Motion

0.225 0.258 0.292

Time (sec)

SHM Motion

SHM

cam


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as 1 cm as a jerk with periodic up and down movement, but output

1.6cm minimum in downward

2

Drop

cam



For SHM type input with 1cm amplitude, a peak of 1.14 cm is observed in upward direction and 1.28

cm is observed in downward direction as shown in figure 4.4.

4.2. Analysis

The graphs obtained by FFT analyzer with the help of accelerometer are slightly out of range due to

following reasons-

• Insufficient damping as the setup is not fixed to the ground.

• Required contact stresses between follower roller and cams cannot be measured.

• Friction between roller and roller pin is causing slight slipping of the roller initially.

Based on results obtained, the conclusion of the project is discussed in next chapter.

CHAPTER 5

5. CONCLUSION

In chapter 4, the results obtained from the FFT analyzer are discussed. The time vs amplitude graph shows

that both the types of output waveforms—SHM and sudden jerk, are achieved with the cam and follower

mechanism. The exciter can be used for rpm value of the motor up to 1000 rpm. The variation in the

amplitude indicates that the damping provided by external weights is insufficient. By fixing the frame to

the ground or by using vibration dampening pads, sufficient damping can be provided, which will give

better accuracy. Use of ball bearing as roller in the roller follower will reduce the friction between the

roller and cams and also reduce the stress on the roller pin. This will increase the life of both the roller and

the cams.

REFERENCE

[1] http://www.globalspec.com/learnmore/sensors_transducers_detectors/acceleration_vibration_sensing/sh

akers_vibration_shock_testing.

[2] D. Dorugade, (2012), “Suspension modeling, analysis and optimization of SUV using Matlab”,

ME Dissertation Report.

[3] Wong J. Y, (2001), “Theory of Ground Vehicles”, 3-ed. John Wiley & Sons.558 p.

[4] S. H. Sawant, Mrunalinee V. Belwalkar, Manorama A. Kamble, Pushpa B.Khot & Dipali D. Patil,

“Vibrational Analysis Of Quarter Car Vehicle Dynamic System Subjected To Harmonic Excitation

By Road Surface”, Mechanical Engineering Department, Dr. J. J.Magdum College of Engineering,

Jaysingpur.

[5] Brian Wallace, Brandon Dawe, “Design of a Vibration Exciter Device”, Mechanical Engineering Senior

Design Project, Honors Theses, Paper 1913, Western Michigan University.

[6] Nitinkumar Anekar, V.V. Ruiwale, Shrikant Nimbalkar, Pramod Rao, “Design and Testing of

Unbalanced Mass Mechanical Vibration Exciter”, IJRET, pISSN:2321-7308.

[7] L.A.B. Equipment, Inc., Online Catalogue

[8] V. Ryan, “Snail/Drop Cams”, World Association of Technology Teachers, 2009.



[9] R.S. Khurmi& J.K. Gupta, “A Text Book of Machine Design”. Pg 509-557,820-884.

[10] PSG, “Design Data Book”, p4.13, p.7.21, p7.22, p7.100, p7.110, p7.113-p7.116.

[11] Ameya R. Salunke and Prof. Nishant S. Kulkarni, Analysis of Friction Induced Vibration during

Engagement of Clutches. International Journal of Mechanical Engineering and Technology (IJMET), 7(

3 ), 2016, pp. 2 85 – 298 .

[12] Prof. Dr. Zena K. Kadhim and Hadi O. Mery . Free Convection From Optimum Sinusoidal Surface

Exposed To Vertical Vibrations, International Journal of Mechanical Engineering and Technology

(IJMET), 7 ( 1 ), 201 6 , pp. 214 - 22 4 .

Documents

DESIGN AND FABRICATION OF MECHANICAL VIBRATION … · requirements toward designing mechanical vibration exciter which can be used as an input device for analyzing vehicle behavior