Chapter 8 SU13
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Transcript of Chapter 8 SU13
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Figure8.1
Objec/ve:todesignapipingsystemhowtoes/matethepumpsize
Chapter8ViscousflowinPipes
WeneedtohaveapumptocompensateHeadlossduetofric/onHeadlossduetoelbows,valves,andEleva/onchange
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Gas Turbine to Produce Electricity
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Cogeneration with Gas Turbine
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Gas Turbine Blade
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Cooling of Gas Turbine Blade
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6.9.3.Viscousflowinacirculartube
Figure6.34
Navier-Stokesequa/onincylindricalcoordinates
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8.1.1LaminarandTurbulentFlows
Figure8.3FlowislaminarifRe3,000
Isthislaminarorturbulentflow?
ReynoldsDyeExperiment
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Figure8.4
Timedependenceoffluidvelocityatapoint
Fluctua/oncomponentinthevelocityofaturbulentflow
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fig_08_18
VelocityProfiles
ParabolicprofileForLaminarFlow
Power-lawprofileForTurbulentFlow
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B
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fig_08_19
Fric/oninturbulentflowisgreatlyaffectedbyaroughsurface
Inlaminarflow,
whyisfric/onnotaffectedbysurfaceroughness?
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W
A. 28,158;B.31,424;C.35,597;D.42,632
Y
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8.1.2Entranceregion,developingflow,andfully
developedflow
Figure8.5
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8.1.3Pressurevaria/onalongahorizontalpipe,p(x)
Figure8.6
dPdzisconstantinafullydevelopedflow.
Whyisdpdxgreater
attheentranceregionthan
atthefullydevelopedregion?
Why?
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8.2FullyDevelopedLaminarFlow
Rela/onshipbetweenwallshearstressandpressuredrop
Figure8.7
Objec/ve:toderivetheaboverela/onfromtheabovesketchAssume:steadystateflow,constantdiameterpipe
accelera/oniszero.
Thiswasderivedfrom
Navier-Stokeseq.(Ch6)
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8.2FullyDevelopedLaminarFlow
Rela/onshipbetweenwallshearstressandpressuredrop
Figure8.8
Free-bodydiagramofacylinderoffluid
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8.2FullyDevelopedLaminarFlow
Rela/onshipbetweenwallshearstressandpressuredrop
Alterna/vely,wecanderiveitfromvelocityprofile.(Chapter6)
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8.2FullyDevelopedLaminarFlow
Rela/onshipbetweenwallshearstressandpressuredrop
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CapillaryTubeViscometer
Capillarytube
d=3mm
Balancetomeasure
Massflowrate
Reservoir
tank
OpentoAir
Liquid
L=15cm
H=7cmObjec/ve:todetermineliquidviscosity
Given:Wecollected55gper1min.
WhatisP[Pa]acrosscapillarytube?
WhatisthevalueofvolumeflowrateQ[m3s]?
Whatistheviscosityofliquid?
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H=7cm
L=15cm
Wecollected55gper1min.
CapillaryTubeViscometer
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CapillaryTubeViscometer
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W
A. 8;B.10;C.12;D.15
WhydoesEGLdecrease
alongxdirec/on?
Answer:duetopressuredrop
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8.2.3PipingSystemDesign
(Es/ma/onofthelossduetofric/on)
Deriva/onoffric/onfactorDefini/on
Recall
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8.2.3Es/ma/onoffric/onalpressuredropusingfric/onfactor
Recall
From
WhereForlaminarflow:
Forturbulentflow:
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Calcula/onprocedureofpressuredropduetofric/on
Step1:CalculateReynoldsnumber
Step2:Determineifflowislaminarorturbulent.
Step3:Determinefric/onfactor
Step4:CalculateP
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Example(Laminarflow)
Objec/ve:toes/matethefric/onalpressureloss
Given:Water,pipediameterd=4mm;Length=19m
Averagevelocity=0.35msDensity=1,000kgm3;Viscosity=1mPa.s
10m
7m
2m
Valve
Step1:CalculateReynoldsnumber
Step2:Determineifflowislaminarorturbulent.
Step3:Determinefric/onfactor(f=0.04)
Step4:Calculatefric/onalpressuredrop(Answer:P=11,638Pa)
=0.04 19 /0.004 0.5(1000)0.352=11,638
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Example(turbulentflow)
Objec/ve:toes/matethefric/onalpressureloss
Given:Water,pipediameterd=4mm;Length=19mAveragevelocity=15ms
Density=1,000kgm3;Viscosity=1mPa.s
10m
7m
2m
Valve
Step1:CalculateReynoldsnumber
Step2:Determineifflowislaminarorturbulent.
Step3:Determinefric/onfactor(f=0.0202)
f=0.316(60,000)0.25=0.31615.65=0.0202
Step4:Calculatefric/onalpressuredrop(P=10,790,000Pa)
Pump
=0.0202 19 /0.004 0.5(1000)152=10,790,000
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Page412
8.4.1MajorLossesSurfaceRoughnessEffectonFric/onalPressureDrop
Forasmoothpipe(inturbulentflow)
Foraroughsurfacepipe
UseMoodychart
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Fric/onfactorasafunc/onofReynoldsnumberandrela/veroughnessfor
roundpipestheMoodychartWhatisfforRe=60,000?Forasmoothpipef=0.02Foraroughpipe(/D=0.002)f=0.0253
Figure8.20
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B
V1=3msV2=2.1ms
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fig_03_21
Thelocusofeleva/onsprovidedbyPitottubesisEnergyline.
Thelocusofeleva/onsprovidedbysta/ctapishydraulicgradeline
Ifweassumenofric/onallossandnominorloss,(Figfromchapter3)
Pressurehead
WithPitottube
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fig_03_22
Ifweassumenofric/onallossandnominorloss,(Figfromchapter3)
Pressure
head
WithPitottube
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Mc
Thesearesta/cpressuretubes,
measuringsta/cpressures.
?
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Mc
FromB.Eq.,wehave
Vexit=24.3ms
Specificenergyisgivenas[Jkg].Thetotalenergyisconstanteverywhere.
Answer:totalenergyintermsofpressure;P=(1000)(9.8)(30m)=294.3kPa.
Totalenergydoesnotchange(duetofric/onlessassump/on).
Totalspecificenergy=/=294.3/
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Y
Disthepipediameter.
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fig_08_32
8.4.2MinorLossinaSuddenExpansion,Fig.8.32
GlobeValve
SwingCheckValve
GateValve
StopCheckValve
fig_08_33
Notethatinletvelocityisequaltooutletvelocity.
Whataboutinletpressureandoutletpressure?
Sameornot?Why?
Answer:Thereisalossofenergyintheformofpressuredropacrossavalve.
Whydowelosesomeenergyorpressure?
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)2
(2
g
VKh LL =
LossCoefficients
forPipeComponents
Table8.2
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Example
Objec/ve:toes/matethedischargepressureofpump
Given:Water,pipediameterd=2cm;Length=23m
Averagevelocity=2ms
Density=1,000kgm3;Viscosity(water)=1mPa.s
15m
5m3m
Valve
Kforelbow=0.7
Kforvalve=1.2
Pump
Duetofric/on
Duetominorloss
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Example8.8
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Example8.8
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2.Considerawaterpumpingsystemshowninthefigurebelow.Waterflowsat12gpm.
Insidediameterofthepipeis0.75in,lengthsaregivenin,losscoefficientsfor90-degree
elbows=0.2,losscoefficientforwideopenvalve=0.4.1gal=0.133683;
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2.Considerawaterpumpingsystemshowninthefigurebelow.Waterflowsat12gpm.
Insidediameterofthepipeis0.75in,lengthsaregivenin,losscoefficientsfor90-degree
elbows=0.2,losscoefficientforwideopenvalve=0.4.1gal=0.133683;
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2.Considerawaterpumpingsystemshowninthefigurebelow.Waterflowsat12gpm.
Insidediameterofthepipeis0.75in,lengthsaregivenin,losscoefficientsfor90-degree
elbows=0.2,losscoefficientforwideopenvalve=0.4.1gal=0.133683;
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Powerthatshouldbedeliveredtopump
=[]=Where
Q=volumeflowrate[m3s]or[3s]
P=totalpressureliinpump[Pa]or[psf]
Conversion:
1horsepower=1hp=550.lbs=745.7W
Ifpumphas83%efficiency,=[]= /0.83
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Y
Eleva/onfromEtoB
=2.1hp
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Y
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Y
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fig_08_e11
Example8.11
Powerthatshouldbedeliveredtoturbine
with100%efficiency:givenV=6.58s
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Example8.11
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W
Conversion:1horsepower=1hp=550.lbs=745.7W
A.1.0;B.1.5;C.2.0;D.3.0
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W
A.0.2;B.0.6;C.1.0;D.2.0
Conversion:1horsepower=1hp=550.lbs=745.7W
85
.85
.85
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W
Conversion:1horsepower=1hp=550.lbs=745.7W
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W
Thenconsidering80%efficiency,
Weget3.2650.8=4.08.
Conversion:1horsepower=1hp=550.lbs=745.7W
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Fric/onFactorsforLaminarFlowinNoncircularDucts
Usehydraulicdiameter,definedas
Table8.3
1
2cm
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B
V1A1=V2A2
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CoolingofAegisRadarSystem(phased-arraysystem)
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AS-17"Krypton"(Kh-31P)
AegisRadarSystem(phased-arraysystem)
OldRadar
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p_08_102
MicrochannelcoolingsystemforVLSIchip
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Figure8.35Series(a)andparallel(b)pipesystems.
8.5.2Mul/plePipeSystem
Whatisconstant?
Whatisconstant?
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W
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W
Notethatf.V2=constant
1
2
V2=2V1
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B
V1=Q1A1=101.3963=7.1718s
CalculateDP1
DP1=2,238.9psf
DP1=DP2
1
2
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TypicalVenturimeterconstruc/on.Figure8.44
Whatistheopera/ngprinciple?
8.6PipeFlowrateMeasurement
?
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Rotameter-typeflowmeter.(CourtesyofFischer&PorterCo.)
Figure8.46
8.6PipeFlowrateMeasurement
Whatistheopera/ngprinciple?
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Turbine-typeflowmeter.(CourtesyofE.G.&G.FlowTechnology,Inc.)
Figure8.47
8.6PipeFlowrateMeasurement
Whatistheopera/ngprinciple?
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FigureP8.84
HWProblem8.84
Waterat40oF,Flowrate=0.9galmin
(gpmconversion:1USgallon=0.003786m3=0.133683)
(Note1Bri/shimperialgallon=1.2USgallon)
Determinepressuredrop.
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Chapter12Turbomachines
Typicalposi/vedisplacementpumps:(a)/repump,(b)
humanheart,(c)gearpump.
Figure12.1
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12.4.2PumpPerformanceCharacteris/cs
Typicalperformancecharacteris/csforacentrifugalpumpofa
givensizeopera/ngataconstantimpellerspeed.
Figure12.11
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Schema/cofapumpinstalla/oninwhichthepumpmustli
fluidfromoneleveltoanother.
Figure12.13
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.
Typicalflowsystem
WithReservoirtankabovepump
Figure12.14
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12.4.2PumpPerformanceCharacteris/csFigure12.10(p.658)
Units:
1hP=745.7W
1hP=550
IfQ=0.5m3sandisP=20,000Pa,whatshouldbethesizeofmotor?(100%efficiency)
Pump efficiency is not 100%
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Pumpefficiencyisnot100%.
Figure12.11
84%
Ifpumpefficiencyis84%,13.4shouldbechangedto
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Figureonp.684(7thed)
Systemcurve
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U/liza/onofthesystemcurveandthepumpperformancecurve
toobtaintheopera/ngpointforthesystem.
Figure12.15
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Example12.4FigureE12.4
Objec/ve:todetermineQflowrate
Given:totallengthofpipe=200
Fric/onfactorf=0.02
Pipediameter=6in
Pumpcurveisgiven
Solu/on:
Weneedtodevelopasystemcurve,
whichlookslikethis.
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FigureE12.4con7nued 1gal=0.133683
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Effectofopera/ngpumpsin(a)seriesand(b)inparallel.
Figure12.16
W
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W
Conversion:1horsepower=1hp=550.lbs=745.7W
Answerseenextpage
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AnswerforW49.
W
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W
Conversion:1horsepower=1hp=550.lbs=745.7W
Answerseenextpage
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Answer
W
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W
Answerseenextpage
PumpCurve
SystemCurve
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W
A.0.55;B.2.15;C.4.35;D.5.40
W
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W
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W
Answer:P=15+4+40=59m.Thus,ModelB.
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Answer:PumpC
W
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