generalized fluid system simulation program - version …
TRANSCRIPT
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GFSSPGENERALIZED FLUID SYSTEM
SIMULATION PROGRAM- Version 5 (Beta Release)
Alok MajumdarER43/NASA/MSFC
Users Group MeetingOctober 26, 2004
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Topics
• GFSSP Overview• New Features of Version 5
– Conjugate Heat Transfer– Improvements in
• Enthalpy Equation• Ideal Gas Option• VTASC
• Demonstration• Applications
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Classification of CFD Codes
Computational Fluid Dynamics (CFD)
Navier Stokes Analysis (NSA)
Network Flow Analysis (NFA)
Finite Difference
Finite Element
Finite Volume
Finite Volume
Finite Difference
GFSSP
Computational Fluid Dynamics (CFD)
Navier Stokes Analysis (NSA)
Network Flow Analysis (NFA)
Finite Difference
Finite Element
Finite Volume
Finite Volume
Finite Difference
Computational Fluid Dynamics (CFD)
Navier Stokes Analysis (NSA)
Network Flow Analysis (NFA)
Finite Difference
Finite Difference
Finite Element
Finite Element
Finite VolumeFinite
VolumeFinite
VolumeFinite
VolumeFinite
DifferenceFinite
Difference
GFSSP
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GFSSPThermo-Fluid System Analysis Tool
Properties
- Fluids• Cryogenic• Propellants• Refrigerants• Air• Ideal Gas• Generic
- Solids• Metals• Alloys• Generic
Components
• Flow Resistances
-Pipe
- Fittings
- Seals
• Pump
• Heat Exchanger
• Turbopump
• Control Valve
• Generic
Processes
• Mixing of Fluid
• Pressurization
• Blow down
• Choking
• Phase Change
• Water hammer
• Conjugate Heat Transfer
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Finite Volume Formulation in a Fluid Network
= Boundary Node
= Internal Node
= Branch
H2
N2
O2
H2 + O2 +N2
H2 + O2 +N2
= Boundary Node
= Internal Node
= Branch
H2H2
N2N2
O2O2
H2 + O2 +N2H2 + O2 +N2
H2 + O2 +N2H2 + O2 +N2
GFSSP calculates pressure, temperature, and concentrations at nodes and calculates flow rates through branches.
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Conjugate Heat Transfer
Boundary Node
Internal Node
Branches
Solid Node
Ambient Node
Conductor
Solid to Solid
Solid to Fluid
Solid to Ambient
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Mathematical Closure
Unknown Variables Available Equations to Solve
1. Pressure 1. Mass Conservation Equation
2. Flowrate 2. Momentum Conservation Equation
3. Fluid Temperature 3. Energy Conservation Equation of Fluid
4. Solid Temperature 4. Energy Conservation Equation of Solid
5. Specie Concentrations 5. Conservation Equations for Mass Fraction of Species
6. Mass 6. Thermodynamic Equation of State
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GFSSP – Program Structure
Graphical User Interface (VTASC)
Solver & Property Module User Subroutines
Input Data
File
New Physics
• Time dependent
process
• non-linear boundary
conditions
• External source term
• Customized output
• New resistance / fluid
option
Output Data File
• Equation Generator
• Equation Solver
• Fluid Property Program
• Creates Flow Circuit
• Runs GFSSP
• Displays results graphically
Graphical User Interface (VTASC)
Solver & Property Module User Subroutines
Input Data
File
New Physics
• Time dependent
process
• non-linear boundary
conditions
• External source term
• Customized output
• New resistance / fluid
option
Output Data File
• Equation Generator
• Equation Solver
• Fluid Property Program
• Creates Flow Circuit
• Runs GFSSP
• Displays results graphically
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Mass Conservation Equations
Nodej = 1
mji. Node
j = 3mij.
Nodej = 2
mij.
Nodej = 4
mji.
mji.
mij.
= -
SingleFluidk = 1
SingleFluidk = 2
Fluid Mixture
Fluid Mixture
Nodei
∑=
=−=
∆−∆+
nj
jmmm
ij
1
.
ττττ
Note : Pressure does not appear explicitly in Mass Conservation Equation although it is earmarked for calculating pressures
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Momentum Conservation Equation
i
j
g
θ
ω ri rj
.mij
Axis of Rotation
Branch
Node
Node• Represents Newton’s Second Law of Motion
Mass X Acceleration = Forces
• Unsteady
• Longitudinal Inertia
• Transverse Inertia
• Pressure
• Gravity
• Friction
• Centrifugal
• Shear Stress
• Moving Boundary
• Normal Stress
• External Force
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Energy Conservation Equation
k = 2
Nodej = 1 mji
. Nodej = 3
mij.
Nodej = 2
mij.
Nodej = 4
mji.
mji.
mij.
= -
SingleFluidk = 1
SingleFluid
Fluid Mixture
Fluid Mixture
Nodei
2 2/ /
. .,0 ( 0.5 ) ,0 ( 0.5 )
1j ij c i ij cij j ij i i
p pm h m hJ J
j nMAX m h u g MAX m h u g Q
j
τ τ τρ ρτ
ρ ρ
+∆
+ +
− − − =
∆= − − + = ∑
iQ
Rate of Increase of Internal Energy =
Enthalpy Inflow + Kinetic Energy Inflow -ow + Kinetic Energy Outflow +
Heat Source
• Upwind Scheme for advection
Enthalpy Outfl
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Equation of State
Resident mass in a control volume is calculated
from the equation of state for a real fluid
RTzpVm=
z is the compressibility factor determined from
higher order equation of state
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Heat Conduction Equation
i
js = 1
js = 2js = 3
js = 4
jf = 1 jf = 2 jf = 3 jf = 4
ja = 1 ja = 2
( ) i
n
jsa
n
jsf
n
jss
isp SqqqTmC
sa
a
sf
f
ss
s
•
=
•
=
•
=
•
+++=∂∂ ∑∑∑
111
τ ( )
∑ ∑ ∑
∑ ∑ ∑
= = =
= =
•
=
+++∆
+∆
+++
=ss
s
sf
f
sa
a
afs
ss
s
sf
f
sa
a
a
a
f
f
s
s
n
j
n
j
n
jijijij
p
n
j
n
j
ims
mpn
j
jaij
jfij
jsij
is
CCCmC
STmC
TCTCTCT
1 1 1
1 1,
1
τ
τ( )isjsijijijss TTAkq s
sss−=
•
δ/
( )isjfijijsf TTAhq f
ff−=
•
( )isjaijijsa TTAhq a
aa−=
•
Ambient Node
Solid Node
Fluid Node
Conservation Equation
Successive Substitution Form
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Solution Scheme
Mass Momentum
Energy
Specie
State
Simultaneous
Successive Substitution
SASS : Simultaneous Adjustment with Successive Substitution
Approach : Solve simultaneously when equations are strongly coupled and non-linear
Advantage : Superior convergence characteristics with affordable computer memory
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SASS Solution Scheme
Iteration Loop Governing Equations Variables
Simultaneous Solution
Successive Substitution
Property Calculation
Convergence Check
Mass Conservation
Momentum Conservation
Equation of StateResident Mass
Energy Conservation of fluid Enthalpy
Pressure
Flowrate
Energy Conservation of solid Solid Temperature
Thermodynamic PropertyProgram
Temperature, Density, Compressibility factorr, Viscosity, etc.
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Graphical User Interface
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Verification of Conjugate Heat Transfer Results
0
50
100
150
200
250
0 3 6 9 12 15 18 21 24
X (inches)
Tem
pera
ture
(Deg
F)
AnalyticalGFSSP
GFSSP Model
Comparison with Analytical Solution
Problem Considered
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Other Improvements
• Ideal Gas Option– Allows to chose new reference temperature and
pressure– Allows mixture of ideal gas and real fluid
• VTASC– Conjugate Heat Transfer– Ideal Gas Option– Display of results– Use of default properties for resistance and conductor
option
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Summary
• The major highlight of Version 5 is– Conjugate Heat Transfer
• The other improvements are– Ideal Gas Option– Enthalpy Equation– VTASC Upgrade
• Work in Progress– Modeling of Boil-off and Fill-up of Cryogenic Tank– Modeling of Liquid Metal and Electromagnetic Pump– Chilldown of Cryogenic Transfer Line– Flow in Micro channel– Pressurization of Joint in Solid Rocket Motor– Cryo-pumping– Isentropic Flow in Nozzle
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Numerical Modeling of Thermofluid Transients During
Chilldown of Cryogenic Transfer Lines Update
Todd SteadmanJacobs Sverdrup Technology, Inc.
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Experimental Setup
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GFSSP Model
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Model Details• Time Step = 0.0015 secs
• Upstream Boundary ConditionsFluid: Liquid HydrogenP = 74.97 psiaT = 48.6 R
• Pipe CharacteristicsMaterial: Copper1” Outside Diameter, 3/16” Wall Thickness
13577
67.6 Number Courant ≥⋅
==sftft
aLb
ττ
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Temperature Comparison
0
50
100
150
200
250
300
350
0 10 20 30 40 50 60 70 80 90 100Time (sec)
Tem
pera
ture
(K)
Version 5.01Version 4.0Exp Data
STATION 1 STATION 2 STATION 3 STATION 4
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Pressure Prediction
0
100
200
300
400
500
600
0 10 20 30 40 50 60 70 80 90 100Time (sec)
Pres
sure
(kPa
)
Version 5.01Version 4.0
STATION 1
STATION 2
STATION 3
STATION 4
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Quality Prediction
0
0.2
0.4
0.6
0.8
1
1.2
0 10 20 30 40 50 60 70 80 90 100
Time (sec)
Vapo
r Qua
lity
Version 5.01Version 4.0
STATION 1 STATION 2 STATION 3 STATION 4
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Mass Flow Rate Prediction
0
0.02
0.04
0.06
0.08
0.1
0.12
0.14
0.16
0.18
0 10 20 30 40 50 60 70 80 90 100
Time (sec)
Mas
s Fl
ow R
ate
(kg/
s)
Version 5.01Version 4.0
INLET
MIDPOINT
EXIT
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Heat Transfer Coefficient Prediction
0
1000
2000
3000
4000
5000
6000
7000
8000
9000
0 10 20 30 40 50 60 70 80 90 100
Time (sec)
Hea
t Tra
nsfe
r Coe
ffici
ent (
W/m
^2-K
)
Version 5.01Version 4.0
STATION 1STATION 2
STATION 3
STATION 4
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Allied AerospaceERCMorganQualisRaytheon
GFSSP USERS GROUP MEETING
Johnny MaroneyJacobs Sverdrup
10/26/04
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Allied AerospaceERCMorganQualisRaytheon
Topics
• Chill down in a small tube• Micro-Channel• Stennis LOX Line
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Chill Down in a Small Tube• Dr. Matthew Cross Doctorial Dissertation
- Correlated Experimental Data to GFSSP Version 4
• Compared Version 4 to Version 5- Heat Transfer in subroutine- Conjugate Heat Transfer
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Chill Down in a Small Tube
Hydrogen Aluminum Tube
26 in length
3/16 inDiameter
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Version 4
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Version 5
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V4 & V5, RELH=0, Alok new files, Solid Temperature Comparison
-450-430-410-390-370-350-330-310-290-270-250-230-210-190-170-150-130-110-90-70-50-30-101030507090
0 10 20 30 40 50 60 70 80 90 100 110 120 130 140 150 160 170 180 190 200 210
Time (seconds)
Tem
pera
ture
(F) V4 Solid T3 ( F)
V4 Solid T15 ( F)V4 Solid T27 ( F)V5 Solid T32 (F) V5 Solid T44 (F) V5 Solid T56 (F)
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V4 & V5, RELH=0, Alok new files, Pressure Comparison
13.2
13.3
13.4
13.5
13.6
13.7
13.8
13.9
14.0
14.1
14.2
14.3
14.4
14.5
14.6
14.7
14.8
14.9
15.0
0 10 20 30 40 50 60 70 80 90 100 110 120 130 140 150 160 170 180 190 200 210
Time (seconds)
Pres
sure
(psi
a) V4 P3 (Psia) V4 P15 (Psia) V4 P27 (Psia) V5 P3 (Psia) V5 P15 (Psia) V5 P27 (Psia)
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Micro-Channel• Height = 0.000383 inches, width = 0.00238
inches • 45.5 mm (1.8 inches) total piping• Rectangular ducts• Water• Steady State
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14.7 psia, 77F15.7 psia, 77F
6.6159 mm
2.659 mm
14.7 psia, 77F
22.6849 mm
2.6487 mm
2.6487 mm
0.4328 mm
0.4328 mm
2.9287 mm
2.9287 mm
2.659 mm
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RS-84 Subscale Preburner LOX• Stennis• Varying Elevations• Control Valves (% open/closed)• Inlet at 7210 psia, -281.69F• Outlet at 6850 psia, -276.1F• BPV opens at 0.2 seconds, closes at 14.8 seconds• Valve opens at 4.0 seconds, closes at 12.8 seconds
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LOX Run Line Section Identification for K factors
TestArticleInterface
UHPLOXTank
Bypass LegFLM-14A03-LOFlow Meter
MVP
GN2 TA PurgeMVP
GN2 TA Purge
LF-14A15-LOFilter
TankS/OValve
Section 1ends (tank valve,
3 els, 43 ft 6” pipe,-0.33’ elv)
Section 2 ends(2 els, 12.5’ 6” pipe,
+2.8’ elv)
Section 3 ends(3.0’ 6” pipe,
+0’ elv)
Section 5ends (LF)
P
T
VPV-14A03-LO
MV-14A2092-LO
Section 6 ends(1 red, 18.15’ 4” pipe,4 els, +7.5’ elv)
Section 7 ends(4.23’ 4” pipe,1 el, +0’ elv)
Section 9 ends(3.64’ 4” pipe,+0’ elv)
Section 10 (13 Br) ends(1 red, 2.34’ 2.5” pipe,1 el, -1.1’ elv)
Section 7 Br ends(1 red, 1 tee br, 0.82’ 1.5” pipe,+0’ elv)
RO-14A2091-LO
Section 9 Br ends(1.18’ 1.5” pipe,+0’ elv)
Section 11 BrEnds (3.27’ 1.5” pipe, 1 el)
Section 12 Br ends(1 exp, 2.89’ 4” pipe,1 tee br)
6” pipe ID = 4.209”4” pipe ID = 2.86”4” monel clad pipe ID = 2.61”1.5” pipe ID = 1.1”2.5” pipe ID = 1.827”Br=branch section
Elev = 29.5’
Elev = 38.4’
Height difference between Tank discharge and Test Article Interface = +8.9’Volume downstream of MOV VPV-14A03-LO (excluding bypass)= 378.6 cubic inchesVolume downstream of MV-14A2092-LO to main line tie-in = 38.4 cubic inches
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Allied AerospaceERCMorganQualisRaytheon
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LOX Flowrate history for Main and Bypass Line and Test Article, Time Step = 0.1 Seconds
-100.00
0.00
100.00
200.00
300.00
400.00
-4.00 0.00 4.00 8.00 12.00 16.00 20.00
Time (seconds)
Flow
rate
(lb/
s)
F3132 LBM/SF3536 LBM/SF4647 LBM/S
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LOX Pressure History at Test Article, Time Step = 0.1 Seconds
0.00
1000.00
2000.00
3000.00
4000.00
5000.00
6000.00
7000.00
-4.00 0.00 4.00 8.00 12.00 16.00 20.00
Time (seconds)
Pres
sure
(psi
a)
P46 PSIA
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Allied AerospaceERCMorganQualisRaytheon
LOX Pressure History for Main and Bypass Valve, Time Step = 0.1 Seconds
0.00
2000.00
4000.00
6000.00
8000.00
-4.00 0.00 4.00 8.00 12.00 16.00 20.00
Time (seconds)
Pres
sure
(psi
a)
P31 PSIAP32 PSIAP35 PSIAP36 PSIA
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1
Introduction
• Topics• Rapid Pressurization of Solid Rocket Motor
(SRM) Field Joint• Nitrogen Cryo-Pumping Into Thermal Protection
Protection System (TPS) Foam Voids & Subsequent Ejection
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2
Field Joint Pressurization• Problem Description
• Channel Is Pressurized From 12.2 psia and 60 °F to °F to 900 psia and 2300 °F Within 1 Second
• Highly Transient Fluid Flow Within and Heat Transfer to Surrounding Structure
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3
Field Joint Pressurization• GFSSP Model Description
• Single Boundary Node Represents Flow Inlet• Last Node Represents Primary O-Ring Gland• Nodes/Branches In Between Represent Flow
Channel• Conjugate Heat Transfer To Solid Nodes
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4
Field Joint Pressurization• Future Efforts
• Integrate GFSSP With Solid Structure Heat Transfer Code For Advanced Conjugate ModelingModeling
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5
N2 Cryo-Pumping & Ejection• Problem Description
• Voids Unintentionally Produced During TPS Application
• Void/Channel Initially Filled With GN2• Foam Around Void Cools To LH2 Temp. (-423 °F)
During Shuttle Tanking• Cryo-Pumping Draws N2 Into Void• N2 Is Ejected From Void Due To Subsequent TPS
Heating During Shuttle Ascent
N2Source Tanking
Ascent
TPS Foam Void
N2 Leak Path
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6
N2 Cryo-Pumping & Ejection• GFSSP Model Description
• For In-Flow, Transient Inlet Conditions For Fluid Provided At Node 1
• Void Temperature (N2 & Foam Walls) Approximated Approximated As Spatially Uniform At Each Time Time Step (Tanking & Ascent)
• Transient Void Temperature Specified By Using Solid Solid Node In Conjunction With Fluid Node and Very Very Low Resistance Conductor (i.e. Very High h)
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1
SSME Regen. Cooling Problem
Objective:• Use GFSSP to model heat transfer between main MCC
flow and regenerative cooling flow.
Accomplished:1. Developed a simple model of heat transfer between two
counter flow fluids.2. Investigated GFSSP’s ability to predict flow conditions
in a Converging-Diverging nozzle
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2
Basic Heat Exchanger Model
Hot flow path
Solid (nozzle wall) nodes
Cool flow path
Model geometry (i.e. pipe diameter, wall thickness, etc…) was chosen arbitrarily
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3
Basic Heat Exchanger ModelTemperature distribution in a counter flow heat exchanger
* Working fluid - H2O
50.0
60.0
70.0
80.0
90.0
100.0
110.0
2 3 4 5Node
Tem
pera
ture
(F)
Hot Side Cold Side Wall_hotWall_mid Wall_cold
Flow
Flow
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4
User Subroutine for hg & hc
Equation for Gas side (Bartz):
( )σ
µ×
×
= ∗
9.01.08.0
6.0
2.0
2.0 Pr026.0
AA
RD
cgpC
Dh ttnsc
ns
p
tg
( )12.0
2
68.0
2
211
21
211
21
1
−+
+
−+
=
MMTT
nsc
wg γγσWhere,
Equation for Coolant Side:55.0
2.0
8.0
3/2
2.0
Pr029.0
=
wc
copc T
TdGC
hµ
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5
User Subroutine for hg & hc
C**************************************************SUBROUTINE USRHCF(NUMBER,HCF)
C PURPOSE: PROVIDE HEAT TRANSFER COEFFICIENTC**************************************************
INCLUDE 'COMBLK.FOR'C**************************************************
C Loop to determine throat area and diameter
areat=10000do numbera=2,5
call indexi(numbera,node,nnodes,ipn)call indexud(ipn,node,inode,nint,numbr,namebr,nbr,
& ibrun,ibrdnibranch,ibu,ibd)if (area(ibu) .LT. areat) then
areat = area(ibu)endif
enddo
Dt = (4.0*areat*144.0/3.141593)**(0.5)R = 0.75*Dt
C****************************************
C Call Nozzle Properties
numberb=1call indexi(numberb,node,nnodes,ipnb)
y = gama(ipnb)aMach = emach(ipnb)Pns = p(ipnb)*(1+(y-1)/2*aMach**2)**(y/(y-1))Tns = TF(ipnb)*(1+(y-1)/2*aMach**2)cstar = sqrt(32.2*y*Rnode(ipnb)*Tns)/
& (y*sqrt((2/(y+1))**((y+1)/(y-1))))Cp = Cpnode(ipnb)vis = emu(ipnb)/12.0Prl = Pr(ipnb)g = 32.2
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6
User Subroutine for hg & hcC Call index variables and determine heat transfer coefficient
Do numberc = 2,5call indexi(numberc,node,nnodes,ipn)call indexud(ipn,node,inode,nint,numbr,namebr,nbr,ibrun,ibrdn,ibranch,ibu,ibd)numberd = numberc + 24call indexs(numberd,nodesl,nsolidx,ipsn)bmach = sqrt(2/(y-1)*((Pns/P(ipn))**((y-1)/y)-1))sigma = 1/((0.5*(Ts(ipsn)/Tns)*(1+(y-1)/2*bmach**2)+0.5)**(0.68)*(1+(y-1)/2*bmach**2)**(0.12))
HCF = 0.026/Dt**(0.2)*(vis**(0.2)*Cp/Prl**(0.6))*(Pns*g/cstar)& **(0.8)*(Dt/R)**(0.1)*(areat/area(ibu))**(0.9)*sigmaEnddo
Do numbere = 8,11call indexi(numbere,node,nnodes,ipn)call indexud(ipn,node,inode,nint,numbr,namebr,nbr,ibrun,ibrdn,ibranch,ibu,ibd)numberf = numbere + 6call indexs(numberf,nodesl,nsolidx,ipsn)Gdot = flowr(ibu)/area(ibu)/144.dia = (4.0*area(ibu)*144.0/3.141593)**(0.5)
HCF = 0.029*cpnode(ipn)*vis**(0.2)/Pr(ipn)**(2/3)*Gdot**(0.8)/dia**(0.2)*(Tf(ipn)/Ts(ipsn))**0.55Enddo
RETURNENDC***********************************************************************
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7
GFSSP Modeling – CD Nozzle Investigation
Throat
• Tutorial 2 in GFSSP Course Charts
• Working fluid – H2O (steam)
• Inlet Pressure - 150 psi
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8
GFSSP Modeling – CD Nozzle Investigation
0.0
20.0
40.0
60.0
80.0
100.0
120.0
140.0
160.0
-1 0 1 2 3 4 5 6 7
Axial Distance
Pres
sure
(psi
)
.
P_ex =134 psi P_ex = 60 psi P_ex = 15 psi Isentropic
Pressure vs. Axial Location
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9
GFSSP Modeling – CD Nozzle Investigation
0.00
0.02
0.04
0.06
0.08
0.10
0.12
0.14
0.16
0.18
0.20
-1 0 1 2 3 4 5 6 7
Axial Location
Den
sity
(lbm
/ft^3
)
.
P_ex = 134 psi P_ex = 60 psi P_ex = 15 psi Isentropic
Density vs. Axial Location
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10
GFSSP Modeling – CD Nozzle Investigation
Temperature vs. Axial Location
0.0
200.0
400.0
600.0
800.0
1000.0
1200.0
-1 0 1 2 3 4 5 6 7
Axial Location
Tem
pera
ture
(F)
.
P_ex = 134 psi P_ex = 60 psi P_ex = 15 psi Isentropic
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11
GFSSP Modeling – CD Nozzle Investigation
Mach Number vs. Axial Location
0.00
0.50
1.00
1.50
2.00
2.50
3.00
3.50
-1 0 1 2 3 4 5 6 7
Axial distance
Mac
h N
umbe
r
.
P_ex = 134 psi P_ex = 60 psi P_ex = 15 psi Isentropic
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12
GFSSP Modeling – CD Nozzle Investigation
0.00
0.50
1.00
1.50
2.00
2.50
3.00
3.50
-1 0 1 2 3 4 5 6 7
Axial distance
Mac
h N
umbe
r
.
P_ex = 134 psi P_ex = 60 psi P_ex = 15 psi Isentropic Mach P
Isentropic Calculation based on GFSSP Pressure
Mach Number vs. Axial Location (Modified)
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13
VTASC Regen. Cooling Model
Cooling Channel flow path (H2)
Nozzle flow path (Ideal Gas) Throat
Solid (nozzle wall) nodesNozzle flow path, Coolant Channel, and wall thickness set to MCC geometry
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14
SSME Regen. Cooling Problem
Preliminary Results
1. Demonstrated basic counter flow heat exchanger.
2. Created subroutine to calculate heat transfer coefficients
3. Could not correctly predict Mach number in diverging portion of C-D nozzle.
4. Mach number necessary for correct calculation of heat transfer coefficient using the Bartz equation. Used isentropic calculation for HCF subroutine using GFSSP predicted pressure.
5. Model became complex as geometry, multiple fluid, and MCC operating conditions were applied. …Convergence became difficult to achieve and the time required was too large for use with SSME power balance models.
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15
SSME Regen. Cooling Problem
NOTE:
• Used a beta version of the GFSSP code with conjugate heat transfer.
• Used “2nd Law” option for solution control. New version has improved enthalpy (1st Law option) calculation for compressible flow.
• Investigation of this problem is continuing.
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1
Closed Circuit Modeling of Liquid Metal
Alok MajumdarER43/NASA/MSFC
Users Group MeetingOctober 26, 2004
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2
CONTENT
• Introduction• New Features
– Property Table– Electro Magnetic Conduction Pump– Closed Circuit Modeling– Fixed Flowrate
• Results• Summary
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3
Introduction
Objectives
• Calculate Flowrate
• State point properties
NaK – Helium System
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4
New Features
1. Property Look up Table for NaK
2. Electro-Magnetic Conduction Pump
3. Closed Circuit Model
4. Fixed Helium Flowrate
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5
NaK Property Table
Table for Specific Heat (Btu/lb-Deg R)
15 30 0.5100E+03 0.5600E+03 0.6100E+03 0.6600E+03 0.7100E+03 0.7600E+03 0.8100E+03 0.8600E+03 0.9100E+03 0.9600E+03 0.1010E+04 0.1060E+04 0.1110E+04 0.1160E+04 0.1210E+04 0.1260E+04 0.1285E+04 0.1310E+04 0.1335E+04 0.1360E+04 0.1385E+04 0.1410E+04 0.1435E+04 0.1460E+04 0.1510E+04 0.1560E+04 0.1660E+04 0.1760E+04 0.1860E+04 0.1902E+04 0.6000E+01 0.2300E+00 0.2280E+00 0.2250E+00 0.2230E+00 0.2210E+00 0.2190E+00 0.2170E+00 0.2160E+00 0.2150E+00 0.2130E+00 0.2120E+00 0.2110E+00 0.2105E+00 0.2100E+00 0.2090E+00 0.2087E+00 0.2085E+00 0.2083E+00 0.2080E+00 0.2083E+00 0.2087E+00 0.2090E+00 0.2093E+00 0.2097E+00 0.2099E+00 0.2100E+00 0.2105E+00 0.2110E+00 0.2120E+00 0.2130E+00
Temperature
Pressure
Specific Heat
No. of temperature points No. of pressure points
Property Tables are required for
• Density
• Enthalpy
• Specific Heat
• Viscosity
• Conductivity
• Entropy
• Specific Heat Ratio
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6
Electro-Magnetic Conduction Pump
Pump Characteristic Curve
Pump Pressure Rise is a function of:
• Flowrate
• Voltage/Current
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7
User Subroutine for Modeling Electro-Magnetic Conduction Pump
Interpolate data to find DELP
SUBROUTINE SORCEF
Read Pump Performance Data From Table
IF (IBRANCH(I) .EQ. 1718) THEN C BRACKET THE FLOWRATE IR=0 DO II =2,NFLW IF (FLOWR(I).GE.FLWTE(II-1).AND.FLOWR(I).LE.FLWTE(II)) THEN IR=II GO TO 100 ENDIF ENDDO 100 IF (IR.EQ.0) THEN IF (FLOWR(I).GT.FLWTE(NFLW)) IR=NFLW IF (FLOWR(I).LT.FLWTE(1)) IR=1 ENDIF C BRACKET THE VOLT JR=0 DO JJ = 2,NVOLT IF (VOLTIN.GE.VOLT(JJ-1).AND.VOLTIN.LE.VOLT(JJ)) THEN JR=JJ GO TO 200 ENDIF ENDDO 200 IF (JR.EQ.0) THEN IF(VOLTIN.GT.VOLT(NVOLT)) JR=NVOLT IF(VOLTIN.LT.VOLT(1)) JR=1 ENDIF C CALCULATE DELPTE FACTFLW=(FLOWR(I)-FLWTE(IR-1))/(FLWTE(IR)-FLWTE(IR-1)) FACTV=(VOLTIN-VOLT(JR-1))/(VOLT(JR)-VOLT(JR-1)) DELPTE=(1.-FACTFLW)*(1.-FACTV)*DPTE(IR-1,JR-1) & +FACTFLW*(1.-FACTV)*DPTE(IR,JR-1) & +FACTFLW*FACTV*DPTE(IR,JR) & +(1.-FACTFLW)*FACTV*DPTE(IR-1,JR) TERM100=144*DELPTE*AREA(I)
C ADD CODE HERE C MODELING OF THERMO-ELECTRIC PUMP DIMENSION VOLT(50),FLWTE(50),DPTE(50,50) LOGICAL UNREAD DATA VOLTIN/170/ C READ PUMP CHARACTERISTIC DATA FROM FILE IF (ITER.EQ.1.AND. (.NOT. UNREAD)) THEN OPEN (NUSR1,FILE='nak_58_pump.dat',STATUS='UNKNOWN') READ(NUSR1,*) NFLW,NVOLT READ(NUSR1,*) (VOLT(JJ),JJ=1,NVOLT) DO II = 1,NFLW READ(NUSR1,*) FLWTE(II),(DPTE(II,JJ),JJ=1,NVOLT) ENDDO UNREAD = .TRUE. ENDIF ! IF (ITER.EQ.0)..
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8
Closed Circuit Modeling
• Cyclic Boundary Condition needs to be satisfied at Node 1
• This implies Temperature at Node 22 must be equal to Temperature at Node 1
• This must be achieved by iteration
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9
Use of a new User SubroutineSet Temperatures at Boundary node equal to upstream node
C********************************************************************** SUBROUTINE USRADJUST(ITERADJ) C PURPOSE: ADJUST BOUNDARY CONDITION OR GEOMETRY C*********************************************************************** INCLUDE 'COMBLK.FOR' C********************************************************************** C ADD CODE HERE FLOWREQ= .1 RELAXAR=0.5 REPEAT = .FALSE. C ADJUST TEMPERATURE TO SATISFY CYCLIC BOUNDARY CONDITION NUMBER=1 CALL INDEXI(NUMBER,NODE,NNODES,IPN1) NUMBER=22 CALL INDEXI(NUMBER,NODE,NNODES,IPN2) DIFTEM=ABS(TF(IPN1)-TF(IPN2))/TF(IPN1) TF(IPN1)=TF(IPN2)
IF (MAX(DIFTEM,DIFFLW) .LT. 0.001.AND. ITERADJ.GT.2) THEN REPEAT=.FALSE. ELSE REPEAT=.TRUE. ENDIF WRITE(*,*)'ITERADJ=',ITERADJ, 'DIFTEM = ', DIFTEM ,'DIFFLW =', & DIFFLW
Check for convergence
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10
Fixed Flowrate for Helium
• Helium Flowrate was maintained constant by Flow Regulating Valve
• A variable area choked orifice was used
• Area was adjusted in SUBROUTINE USRADJUST
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11
User Subroutine for Flowrate adjustment
C ADJUST AREA OF CHOKED ORIFICE TO REGULATE FLOWRATE NUMBER=3435 CALL INDEXI(NUMBER,IBRANCH,NBR,IB) FLOWCALC = FLOWR(IB) IF (ITERADJ .EQ. 0) THEN AREAOLD=AREA(IB) FLWOLD=FLOWCALC IF (FLOWCALC .GT. FLOWREQ) THEN AREA(IB)=0.99*AREA(IB) ELSE AREA(IB)=1.01*AREA(IB) ENDIF ELSE C CALCULATE GRADIENT DADMDT=(AREA(IB)-AREAOLD)/(FLOWCALC-FLWOLD) DIFFLW=ABS(FLOWREQ-FLOWCALC)/FLOWREQ FLWOLD=FLOWCALC AREAOLD=AREA(IB) C CORRECT AREA AREA(IB)=AREAOLD+RELAXAR*DADMDT*(FLOWREQ-FLWOLD) ENDIF
Define adjustment of area in 1st
iteration
Determine the area based on gradient in subsequent iterations
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12
Pressure Distribution
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13
Temperature Distribution
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14
Helium Supply Temperature
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15
Helium Flowrate
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16
Summary
• NaK property was introduced through property table earmarked for RP-1
• Electro Magnetic Conduction pump was modeled in SUBROUTINE SORCEF
• Closed circuit model requires iterative adjustment to satisfy cyclic boundary condition
• Flow regulating valve also requires iterative adjustment of flow area
• SUBROUTINE USRADJUST (to be made available in the final release) performed iterations for cyclic boundary condition and flow regulating valve