AVC GOLLEGE OF
ENGINEERING.
MANNAMPANDAL.
DEPARTMENT OF MECHANICAL
ENGINEERING
1
VIBRATION ANALYSIS OF DOUBLE
IMPELLER MARINE PUMP USING
FEA METHOD
GUIDED BY
Mr.S.VIJAYARAJ.M.E.,
ASST.PROFESSOR,
DEPT OF MECHANICAL ENGG
PRESENTED BY
P.J SENTHIL KUMAR
R.NATARAJAN
T.BALAKRISHNAN
K.JEGADESH
2
COMPANY PROFILE
 COMPANY NAME
 PLACE
: MACRO ENGINEERING
PVT LTD
: CHENNAI.
 YEAR OF ESTABLISHED: 2003
 PRODUCT DESCRIPTION :DESIGN & ANALYSIS
PUMPS
On the basis of transfer of mechanical energy, the
pumps can be broadly classified as,
 Positive displacement Pumps
 Roto dynamic Pumps
 The centrifugal pump of today is made by
250 years old evolution.

It has now attained a new degree of
perfection It is widely used as it can be coupled
directly to electric motors, steam turbines etc.
DOUBLE IMPELLER MARINE PUMP
 It is a contrivance to boost up liquids
in the pipe line by creating the
required pressure with the help of
centrifugal action.
 In general it can be defined as a
machine which increases the pressure
energy of a fluid, as a pump may not
be used to lift water at all, but just to
boost the pressure in a pipe line
MARINE PUMP
APPLICATIONS
 To pump the salt water from sea to ship
for process.
 To boost up the working fluid between
two tanks
 To pump the back water in the
seashore.
 To pump the water in power plant
industries.
PROBLEM DESCRIPTION
 Vibration is the major problems of all machines
and rotating components. In marine pumps It
affects the over all efficiency of the pump.
Prevention and control of vibrations in pumps is
more important point to increase the efficiency
of the marine pumps. So it is necessary to find
out the vibrations during its operating condition.
 Determination of the stress and deformation of
the already designed double impeller marine
pump due to vibrations in the pump if any as
prevention control of vibration of machines
structure is an important design consideration.
 For this reason, capacity, head, power
consumption are the essential points in double
impeller marine pump design.
8
METHODOLOGY
 MODELLING – PRO-E WILD FIRE 3.0
 MESHING -
HYPERMESH 9.0
 ANALYSIS -
ANSYS 10.0
9
HARDWARE AND SOFTWARE
DESCRIPTION:
The following virtual validation is carried
on the following hard ware
Hardware:
 HP xw8200 Workstation
 Processor-Two 64-bit Intel® Xeon™
processor(s) with Hyper-Threading
Technology
 Memory-7 GB of ECC DDR2 400 MHz
SDRAM
 Graphics-NVIDIA Quadro FX 1400 (PCIe)
10
Software:
 Preprocessing :
 Solver
:
 Post processing :
Hypermesh9.0
ANSYS 10.0
ANSYS 10.0
11
INTRODUCTION OF FEA
 Finite element analysis is a process, which can be
used to predict deflection and stress on a structure.
 In finite element model, the structure is divided in to
number of grids, which is called as elements.
 Each of the elements has a simple shape (such as
square or triangle) for which the finite element
program has information to write the governing
equations in the form of stiffness matrix for the entire
model.
 This stiffness matrix is solved for the unknown
displacements at the nodes, the stresses in each
element can be calculated.
12
INTRODUCTION OF FEA
 The finite element is derived by assuming a
form of the equation for the internal strains.
 The equilibrium equation between the
external forces and the nodal
displacements can be written.
 There will be one equation for each degree
of freedom for each node of the element.
 The equation is [K] [U] = [F]
13
OBJCTIVE OF THE PROJECT
 Build a detailed finite element model
of the impeller assembly
 Carry out a static Analysis with a
single time step
 Dynamic analysis with response
spectrum behavior using corrugated
load case.
14
INPUT DATA
 CAD data: 3D Models of pump
impeller and the assembly files of
ProE wildfire3.0
 Loading, boundary conditions and
material properties as available in
FIAT-GM Power train Italia standards.
METHODOLOGY
 The model of marine pump was designed
by using pro-E software .
 The designed part assembly is saved as in
IGES format
 The IGES file was imported to hyper mesh .
 Now the assembled model is ready to be
used with hyper mesh for meshing
 The IGES format meshed model is
imported to ansys for taking analysis.(static
& Dynamic
16
PRO-E MODEL PUMP
SIDE VIEW OF MARINE PUMP
SPECIFICATIONS OF MARINE PUMP
Pump size
6”
Pump type
Radial flow
Pump speed (n)
1470 rpm
No. of stages (N) 2 stages
Discharge (Q)
114 kg/s
Actual head (H)
105 m
Motor rating
200 KW
Motor type
Wet
Voltage
415v
19
Shaft And Impeller Assembly
20
STEPS INVOLVED IN MESHING








Model input
Problem definition
Geometry cleanup
Element shape
No. of nodes and elements
Meshing
Preview of meshing
Checking of quality index
22
Material & Loads:
Material
YST310
Young’s
Modulus
Density
Kgf/mm2
g/cc
21000
7.85
Poisson
Ratio
0.3
Yield stress
σy
Kgf/mm2
45.0
LOAD
Speed = 1470rpm
Angular Velocity = 2x3.14x1470/60
= 153.86 rad/sec
23
STATIC ANALYSYS
Deformation-mm
Usum - Shaft
Ux – Impeller and Shaft
Deformation-mm
Uy – Impeller and Shaft
Uz – Impeller and Shaft
Deformation-mm
Usum – Impeller
Ux – Impeller
Deformation-mm
Uy – Impeller
Uz – Impeller
Deformation-mm
Usum – Shaft
Ux – Shaft
Deformation-mm
Uy – Shaft
Uz – Shaft
Stress-Kgf/mm^2
Principle Stress – Shaft
Stress-Kgf/mm^2
Von Mises Stress – Impeller
Von Mises Stress – Impeller
Part
Shaft
Impeller
Deformation-mm
Usum
Ux
Uy
Uz
0.06861
3.94
0.264e-3
0.1277
0.06861
3.939
0.926e-3
3.872
Note: Usum, Ux, Uy, Uz are Resultant
deformation & deformation in X, Y & Z
direction.
DYNAMIC ANALYSYS
MODAL ANALYSIS
Frequency - Hz
1st Freq – Hz - Shaft
Vertical Bend - Shaft
2nd Freq - Hz- Shaft
Vertical Bend - Shaft
2nd Freq – Hz - Shaft
Z- Bend - Shaft
3rd Freq - Hz- Shaft
Vertical Bend - Shaft
4th Freq – Hz - Shaft
Z- Bend - Shaft
5th Freq - Hz- Shaft
Local Bend - Shaft
6th Freq – Hz - Shaft
Local Bend - Shaft
1st Freq – Hz- Impeller & Shaft
Vertical Bend - Shaft
4th Freq – Hz- Impeller & Shaft
Vertical Bend - Shaft
5th Freq – Hz- Impeller & Shaft
Z Bend - Impeller
6th Freq - Hz
Twist - Impeller
MODAL ANALYSIS RESULTS
FOR 6 MODES
FREQUENCY HZ Deformation
mm minimum
Deformation
mm maximum
162.796
1.878 mm
16.904
162.796
1.878 mm
16.904
435.475
-11.466
15.34
435.475
-11.466
15.34
775.88
8.765
78.885
775.88
8.765
78.885
MODAL ANALYSIS RESULTS
 In modal analysis results the above following we find,
various set of frequencies for shaft with impeller at a
speed of 1470 rpm. The frequency ranges from 162.796
to775.88. It does not exceed 1KH .
 The deformation value is not getting increased beyond
78.885mm with higher frequencies than 775.88Hz
Hence the obtained range of vibrations
is lesser
So that, the performance of the pump will
not affected by vibrations.
HARMONIC RESPONSE ANALYSIS
Deformation Plot
Deformation – Usum
Deformation – Ux
HARMONIC RESPONSE ANALYSIS
Deformation Plot
Deformation – Uy
Deformation – Uz
HARMONIC RESPONSE ANALYSIS
Deformation Plot
Deformation – Usum - Shaft
Deformation – Uy - Shaft
HARMONIC RESPONSE ANALYSIS
Stress Plot
Equivalent Stress - Shaft
Equivalent Stress - Shaft
HARMONIC RESPONSE ANALYSIS
Stress Plot
Equivalent Stress - Impeller
Equivalent Stress - Impeller
Part
Impeller + Shaft
Deformation-mm
Usum
Ux
Uy
Uz
0.411e-3
0.845e-4
0.411e-3
0.206e-5
Note: Usum, Ux, Uy, Uz are Resultant deformation & deformation in X, Y &
Z direction.
Part
Stress- kgf/mm^2
Shaft
0.0072
Impeller
0.01712
Yield Stress
45
FOS
2.628
Note: σe – Stress Based on Energy theory (Von Misses Theory);
FOS = σy / σe
Design FOS 2.00< 2.628
Hence the design is safe in Dynamic load
HARMONIC RESPONSE ANALYSIS
Frequency – Hz Vs Amplitude -mm
RESPONSE ANALYSIS
1.00E-02
9.00E-03
8.00E-03
AMPLITUDE
7.00E-03
6.00E-03
MASS-1
5.00E-03
MASS-2
4.00E-03
3.00E-03
2.00E-03
1.00E-03
0.00E+00
0
50
100
150
200
FREQ
250
300
350
Conclusions:
From the foregoing FE analyses & results, the
following conclusions are drawn.
The result of static analysis under the self weight +
speed (1470rpm) are tabulated. It is seen that
maximum stresses in the impeller notch.
Maximum stresses are within material yield, Design
FOS = 2.0, Minimum factor of safety is 2.14.
In the dynamic analysis the frequencies
ranges from 124.42Hz to 775.88Hz. It does
not exceed 1 kHz. So the Obtained frequencies
during the analysis are within the limit.
Hence the obtained range frequency of
vibrations is less. So that, the performance of the
pump will not be affected by vibrations.
Finally the design is found to be safe
from the static and dynamic conditions are
well within material yield and meet the
design requirements. The analysis is carried
out using ANSYS software.
52
THANK YOU
53