AVC GOLLEGE OF ENGINEERING. MANNAMPANDAL. DEPARTMENT OF MECHANICAL ENGINEERING

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AVC GOLLEGE OF ENGINEERING.MANNAMPANDAL.
DEPARTMENT OF MECHANICAL ENGINEERING
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VIBRATION ANALYSIS OF DOUBLE IMPELLER MARINE PUMP
USING FEA METHOD

• GUIDED BY
  PRESENTED BY
• Mr.S.VIJAYARAJ.M.E., P.J
  SENTHIL KUMAR
• ASST.PROFESSOR,
  R.NATARAJAN
• DEPT OF MECHANICAL ENGG
  T.BALAKRISHNAN
• 
  K.JEGADESH

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COMPANY PROFILE

• COMPANY NAME MACRO ENGINEERING
  PVT LTD
• PLACE CHENNAI.
• YEAR OF ESTABLISHED 2003
• PRODUCT DESCRIPTION DESIGN ANALYSIS

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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.

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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

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MARINE PUMP
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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.

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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.

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METHODOLOGY

• MODELLING PRO-E WILD FIRE 3.0
• MESHING - HYPERMESH 9.0
• ANALYSIS - ANSYS 10.0

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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)

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• Software
• Preprocessing Hypermesh9.0
• Solver ANSYS 10.0
• Post processing ANSYS 10.0

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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.

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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

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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.

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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.

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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

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PRO-E MODEL PUMP
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SIDE VIEW OF MARINE PUMP
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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
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Shaft And Impeller Assembly
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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

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Material Loads
Material Youngs Modulus Density Poisson Ratio Yield stress sy
Material Kgf/mm2 g/cc Poisson Ratio Kgf/mm2
YST310 21000 7.85 0.3 45.0

• LOAD
• Speed 1470rpm
• Angular Velocity 2x3.14x1470/60
• 153.86 rad/sec

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STATIC ANALYSYS
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Deformation-mm
Usum - Shaft
Ux Impeller and Shaft
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Deformation-mm
Uz Impeller and Shaft
Uy Impeller and Shaft
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Deformation-mm
Ux Impeller
Usum Impeller
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Deformation-mm
Uz Impeller
Uy Impeller
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Deformation-mm
Usum Shaft
Ux Shaft
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Deformation-mm
Uy Shaft
Uz Shaft
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Stress-Kgf/mm2
Principle Stress Shaft
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Stress-Kgf/mm2
Von Mises Stress Impeller
Von Mises Stress Impeller
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Part Deformation-mm Deformation-mm Deformation-mm Deformation-mm
Part Usum Ux Uy Uz
Shaft 0.06861 0.264e-3 0.06861 0.926e-3
Impeller 3.94 0.1277 3.939 3.872
Note Usum, Ux, Uy, Uz are Resultant deformation
deformation in X, Y Z direction.
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DYNAMIC ANALYSYS
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MODAL ANALYSIS Frequency - Hz
1st Freq Hz - Shaft
2nd Freq - Hz- Shaft
Vertical Bend - Shaft
Vertical Bend - Shaft
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2nd Freq Hz - Shaft
3rd Freq - Hz- Shaft
Z- Bend - Shaft
Vertical Bend - Shaft
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4th Freq Hz - Shaft
5th Freq - Hz- Shaft
Z- Bend - Shaft
Local Bend - Shaft
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6th Freq Hz - Shaft
1st Freq Hz- Impeller Shaft
Local Bend - Shaft
Vertical Bend - Shaft
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5th Freq Hz- Impeller Shaft
4th Freq Hz- Impeller Shaft
Vertical Bend - Shaft
Z Bend - Impeller
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6th Freq - Hz
Twist - Impeller
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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
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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.

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HARMONIC RESPONSE ANALYSIS Deformation Plot
Deformation Usum
Deformation Ux
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HARMONIC RESPONSE ANALYSIS Deformation Plot
Deformation Uy
Deformation Uz
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HARMONIC RESPONSE ANALYSIS Deformation Plot
Deformation Usum - Shaft
Deformation Uy - Shaft
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HARMONIC RESPONSE ANALYSIS Stress Plot
Equivalent Stress - Shaft
Equivalent Stress - Shaft
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HARMONIC RESPONSE ANALYSIS Stress Plot
Equivalent Stress - Impeller
Equivalent Stress - Impeller
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Part Deformation-mm Deformation-mm Deformation-mm Deformation-mm
Part Usum Ux Uy Uz
Impeller Shaft 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/mm2
Shaft 0.0072
Impeller 0.01712
Yield Stress 45
FOS 2.628
Note se Stress Based on Energy theory (Von
Misses Theory) FOS sy / se
Design FOS 2.00lt 2.628 Hence the design is safe
in Dynamic load
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HARMONIC RESPONSE ANALYSIS Frequency Hz Vs
Amplitude -mm
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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.
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• 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.

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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.
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THANK YOU