Inte rnatio nal Jo urnal o f Sc ie ntific & Eng inee ring Re se arc h, Vo lume 3, Issue 2, February -2012 1
ISS N 2229-5518
Conceptual Framework of Centrifugal Pumps towards Industrial Revolution
SELVARASU.A,KANTHAVEL.K,KRISHNARAJ.R,KARPAGARAJAN.S,RAVI.G, RAMESH.R
modif ication the vane angle through CFD analysis has consideration to elaborate the conceptual f rame w ork of a centrif ugal pu mps.
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These pr essur e pulsations can interact with pr essur e waves caused for example by fast valve closing AhNemdlh.Dieter-Heinz Hellmann(1999) stated the application of a centr ifugal pump for desalination and
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Kanthavel.K, Assistant professor, Department of Mechanical
Engineering,Anna University of Technology, Coimbatore, India
Krishnaraj.R, JRF(professional), Department of Mechanical
Engineering,AnnaUniversityof Technology, Coimbatore, India
pow er plants, and the ener gy usage and the maintenance costs dur ing the operation of the pump w as r educed
.Daniel Wolfram(2010)observed that low circumfer ential Mach number the sound of isolated centr ifu gal fan impellers was dominated by distinctive tones at blade passing fr equency (BPF) and integer multiples. This led to the pr eliminary conclusion that the BPF r elated tones ar e exclusively flow-induced. Based on hot-wir e and blade pr essur e fluctuation measur ements and a subsequent corr elation analysis, coher ent flow str uctur es differ ent fr om those associated w ith the pr incipal azimuthal flow pattern due to the blades w er e detected. Mor e likely the vortex structur e detected her e is r elated to the dr aft tub e vortex found in w ater turbines or in the intake of pumps. PunitSingh (2010)concluded that a methodological approach has to be employed for using the optimization r outine in field pr oj ects and to collect accurate operational data. R.Barrio (2011) experienced a significant radial load when operating at off-design conditions. Its average magnitude can be r easonably estimated at the design stage by existing formulas.The total radial load on the impeller of centr ifugal pumps under differ ent operating conditions can be r easonably estimated by means of the numer ical simulation of the unsteady flow w ith an appr opriate CFD code. It was observed that the maximum amplitudeof the unsteady tor que can r each a magnitude of about 45% of theaverage value when operating at the lower flow r ates). Ramazanbavindir (2011) explained the design of water pumping control system in the pr oduction plants and implemented an exper imental setup in a laboratory. These plants contain harsh environments in which chemicals, vibrations or moving parts exist that could potentially damage the cabling or wir es that ar e part of the contr ol system.The pr oposed architectur e and r esults demonstrate the feasibility of using IW LAN pr otocols to communicate effectively w ith PLCs. The system was tested using an industr ial application and it had a very satisfactory per formance. R. Spence(2009) pr oposed numerical model
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Inte rnatio nal Jo urnal o f Sc ie ntific & Eng inee ring Re se arc h, Vo lume 3, Issue 2, February -2012 2
ISS N 2229-5518
of an entir e double entry, double volute centr ifuge pump to conduct a par ametr ic study cover ing four main geometr ic parameters.
10
8
NO OF 6
PAPER 4
2
0
These ar e solved using a commercial CFD package Fluent
4[10]
The hydraulic efficiencies w her e
=1- [54]
the pump efficiency determined was changes of fluid viscosity with the normal par ameter s
η
The per formanceflows a significant r ole in or der to plot the efficiency curve in order to compar e the theor etical and experimental calculating consider ing var ious losses J.P. Boylan(1998)innovated solar pump system using a modular centr ifugal pump w ith var iable speed and number of activated stages (DSP) has been pr oposed [34]. . Khin Cho Thin (2008) et al showedlooses of centr ifugal pump with the valuesQ and H deter mine var ious operating points. Centr ifugal pumps ar e fluid-kinetic machines designed for pow er incr ease within a r otating impeller Somelooses of centr ifugal pump with the values Q and H ar e determined for the var ious operating points. [54]. P. Thanapandi and Rama Prasad(1995) studied to theor etical and experimental on the tr ansient character istics of a centr ifugal pump during starting and stopping periods. Which experiments w er e conducted on a volute pump for normal starting and stopping transients for two cases. Dynamic character istics of the pump dur ing the operating transients have been studied and the natur e of change of parameters during tr ansients was conducted [11]. Wen- GuangLi(2000)tested centrifugal pump per formances using water and viscous oil as w or king fluids of w hich centr ifugal
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Inte rnatio nal Jo urnal o f Sc ie ntific & Eng inee ring Re se arc h, Vo lume 3, Issue 2, February -2012 3
ISS N 2229-5518
pump's per for mance goes down when the pump handles
high viscosity wor king fluid. The flow patter ns near the
impeller outlet ar e less affected by the viscosity of the fluids in best efficiency and part loading points, but the flow patter ns near the impeller inlet ar e gr eatly affected by the viscosity’s.*20+. TahsinEngin(2006) et al designed to thr ee centr ifugal fan impeller s made of ceramic mater ials
Exper iments have been conducted on a specifically designed test facility allowing that gases w ith t emperatur es up to 1050 ºC. The effect of impeller geometry, shaft speed, gas temper atur e, and the tip clearance on the overall per formance of the tested impellers have been investigated [55].
head is deter mined fr om zer o to maximum theor etically attainable flow using.[54]
The theor etical head: Hth = 1/gU2Vu2 (27)
wher eU2and Vu2 ar e outlet tangential velocity and whirl
velocity. Whirl velocity: Vu2 = U2 – Vm2 cotβ2 (28)wher eVm2andβ2 ar e outlet flow velocity and outlet blade angle.
If the slip factor is known, the net theor etical head may be obtained fr om Euler ’s head. It is possib le to r elate thetheor etical char acter istic obtained fr om Euler ’s equation
to theactual character istic for var ious losses r esponsible for thediffer ence. The use of the slip factor which varies with flow rate enables the net theor etical head curve to obtained. Atflow r ates below design flow rate, separation occurs on thesuction side of the blade.
The net theor etical head is calculated by:
H
The whir l velocity at the outlet is;
Vu2 = U2σ – Vm2 cotβ2 (30)
wher e, σ is the slip value. Slip value is obtained by using the follow ing equation Specific speed is used to classify impellers on the basis of their per for mance, and pr oportions r egar dless of their actual size or the speed at which they oper ate.[54]
Specific Speed: =3.65n
failur e of tw o counter shafts used in centr ifugal pumps for lifting slurry thus Chemical analysis, micr ostr uctural char acterization, fact gr aph, hardness measur ement, tensile and Charpy impact t ests w er e used for the analysis wher e shafts "consisting of ferrite-pearlite for A and temper ed bainite for B w er e made of EN13 steel The mater ials did not show significant inclusions or segr egation but Shaft B impr oper heat tr eatment r esulted in low values of str ength
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Inte rnatio nal Jo urnal o f Sc ie ntific & Eng inee ring Re se arc h, Vo lume 3, Issue 2, February -2012 4
ISS N 2229-5518
[27]. F. Berndt(2001) et al contr ibuted towar ds pump failur es indicating the effect of pump per formance[60].
dir ection[15]. Mario Savar(2009) et al pr oposed the method for pump impeller tr imming found good exper imental confirmation despite some theor etical constr aints. Dimensional head-dischar ge diagrams show a high coincidence when pr esented in non-dimensional form. The exper imental r esults for a range of seven examined impeller diameters ar e pr esented by a single cur ve with a high head corr elation coefficient R2=0.9895[33]. PunitSingh, Franz Nestmann(2011) et al developed a subj ected to the theor etical model specifically for the PAT optimization study under the backgr ound of some assumptions was very useful in isolat ing the important inter nal hydraulic var iables[36]. S.C.M. Yu(2000) et al focused on the flow patterns within the impeller passages of a centr ifugal blood pump. Four differ ent types of blade geometry have been tested including the radial straight blade and backward swept blade designs. Both designs can achieve a head of about 100 mm Hg at the design point [44].
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Inte rnatio nal Jo urnal o f Sc ie ntific & Eng inee ring Re se arc h, Vo lume 3, Issue 2, February -2012 5
ISS N 2229-5518
testing in this study indicated an acceptable design fr om which to build upon and optimize [59]. Bao -ling Cui(2011) et al based Navier-Stokes equations and the Spalart - Allmarasturbulence model, thr ee dimensional turbulent flow fields in centrifugal pump with long-mid-short blade complex impeller for calculating and numer icallyanalysing. [58]. Optimization
Slient featur es of micr o computer pr ogram
Data information
Parametric characteristics
Relation and interaction of curvatur e
Cost estimation
The sur vey very clear ly indicates that r esear chers
have shown consider able efforts on centr ifugal pumps based on its per formance characteristics and efficiency determination, v ery few papers wer e published on cfd analysis on pumps and ther e is no consistent papers on
scada applications in pump theory,consider amount of effor t has to be made on abr asive slurries, the r equir ement of longer life and r eliability have to be balanc ed by the constr ain of high initial cost and efficiency.
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