stress analysis of impeller using ansys simulation

8/18/2019 Stress Analysis of Impeller Using Ansys Simulation

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STRESS ANALYSIS OF IMPELLER USING

ANSYS SIMULATION

MODULE

Scope of Work

Based on the finite element analysis software ANSYS Workbench, studied the

Numerical simulation of the centrifugal impeller with the finite element method. The

eui!alent stress distribution of the impeller, which caused by the centrifugal load, the

coupling effect of centrifugal load and aerodynamic load, is analysed. Based on the fluid

components transport theory, the distribution of the flow field inside the impeller is analysed,

and discussed the influence of the stress distribution. Design and validation of animpeller rotating with various RPM such as 1050 RPM, 1250 RPM , 1450RPM . "ost processing shows the stress and deformation results at each node. Which isanalysed to check whether the results are in safe limit or not.

PROBLEM DESCRIPTION

The problem is based on the #$ model of impeller blade .The %&A analysis techniue is

employed to determine the load carrying performance of the impeller.


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METHODOLOGY


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'(&AT)N* +,$&- )N 'AT)A

)+",(T)N* T.& 'AT)A +,$&- )NT, ANSYS W,(/B&N'.

+&S.)N* ,% *&,+&T()' +,$&-

A""-)'AT),N ,% STAT)' -,A$ AN$ B,0N$A(Y ',N$)T),N

STAT)' ST(0'T0(A- ANA-YS)S

S,-0T),N

(&S0-T 1A-)$AT),N

GENERAL SET UP

1. et up la!out "


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#eometr! "

The 'A$ model is imported into the geometry module of the workbench and geometrical

operations are applied such as slicing to get a better mesh.

Mesh Model "

The impeller blade model is meshed and he2a mesh is obtained by gi!ing body si3ing andedge si3ing.


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$oundar! %onditions "

0sing the following boundary conditions static structural analysis is performed.

CASE 1- With 1! RPM


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As per static structural analysis the (otational !elocity is applied to all bodies is 4565 ("+ ,

%i2ing condition is applied as (emote displacement that is (otation in 7 direction is free and

other $egree of freedom is fi2ed. The other end of the shaft is fi2ed. This remote

displacement support is applied on the circumference of the one end of the shaft.

Rotational &elocit! "

Pressure at suction side " '.45 ( 10)2 MPa

Pressure outer side " *.** ( 10)2 MPa


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Pressure on top side " 0.15 MPa

Remote Displacement "


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otal Deformation)

+-uivalent &on)Misses tress "

Observation-

• he ma(imum total deformation of 0.005 mm is within

safe limit and can e considered safe.

• he ma(imum &on Misses stress value of 10.*5 MPa is less

than the allowale limit and hence the impeller can e

considered as safe.

C"#e $ % 1$! RPM


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/or case 2 all the oundar! conditions are similar as case 1

e(cept the rotational velocit! which is 1250 RPM.

Rotational &elocit!) 1250 RPM

Results –

otal Deformation "



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Observation-

• he ma(imum total deformation of 0.005' mm is within


• he ma(imum &on Misses stress value of 1.052 MPa is

less than the allowale limit and hence the impeller can

e considered as safe.

C"#e & % 1'! RPM

/or case all the oundar! conditions are similar as case 1

e(cept the rotational velocit! which is 1450 RPM.

Rotational &elocit!) 1450 RPM


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otal Deformation "


Observation-

• he ma(imum total deformation of 0.00*' mm is within


• he ma(imum &on Misses stress value of 15.*4 MPa is

less than the allowale limit and hence the impeller can

e considered as safe.

on!lusion –


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/rom the aove cases it can e concluded that the impeller

lade is safe under rotational velocit! of 1050 RPM, 1250 RPM

and 1450 RPM.

stress analysis of impeller using ansys simulation

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