presentation: (2012 epri materials reliability conference ...i 1,64 t-r fo .0 1 0= i ±ý 1,464(....
TRANSCRIPT
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The views expressed herein are those of the authors and do not reflect the viewsof the U.S. Nuclear Regulatory Commission.
Outline U.S.NRC
" Introduction and Motivation
* Analysis Methods
" Results
" Conclusion
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Outline -`U.S.NRCPW~tf 'Wp Jtwo &W
" Introduction and Motivation
" Analysis Methods
* Results
" Conclusion'
RG 1.161 and Appendix KOverview
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Regulatory Guide 1.161 and ASME Section XI, NonmandatoryAppendix K provide procedures for calculating adequate Charpyupper shelf energy to protect against ductile fracture of the vessel.
The applied J-Integral is estimated from stress intensity factorequations.
6 r (7,
r, -, 0,982 + I006(ail): • 'Re-evaluate using a,.giving K,,,' and K,,'
F= i,694. 1_117u/1)'- 7 435(v11 -2 3,512(at)' ,J = 100o (• ' ÷ 'I,'
E,
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RG 1.161 and Appendix KOverview
* Flaw geometry, a/c = 1/3
R I -J... .. .....
.....
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RG 1.161 and Appendix KMotivation
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. These stress intensity factor equations were derived for Rlt = 10,which applies to pressurized water reactor vessels.
* Boiling water reactor vessels typically have Rit = 20.
* The thinner vessels are expected to be less susceptible to steepthermal gradients.
This work further explores the validity of using the derived equationsfor the Rit = 20 case, through the use of independent methods ofcalculating stress intensity factor.
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Outline UUS.NRC
° Introduction and Motivation
• Analysis Methods
" Results
" Conclusion
Temperature ProfilesThe Heat Equation
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* Parabolic partial differential equation:
" Boundary conditions:
OTC1 I r ke
= 1( (T.f1 - Tý) for r -R, aind all r
q = for 1, - R, anid till r
T -- TO - ((-'R ) 7
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The Heat EquationSolving Strategies for Temperature Profiles
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r~II.pk *n4 rn~pwus,.
• Finite element analysis
" Crank-Nicolson method
" Analytical solutions
" Resource: Kreyszig, Advanced Engineering Mathematics
" This work
- Commercial engineering coding software with a built-in PDE solver
- Skeel and Berzins, "A Method for the Spatial Discretization of ParabolicEquations in One Space Variable," SIAM J. Sci. and Stat. Comput.
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Calculation of StressesPressure and Thermal Hoop Stresses
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* Pressure stresses in a thick-walled cylinder:
• Thermal stresses in a cylinder:
e _ I- _+ RJ Tzdr f"Tr -T(+O tR2 -I).
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Calculation of Stress Intensity Factor ''U.S.NRCThree Independent Methods ,
• American P etroleum Institute Standard 579-1:
GX t " G' """'t ±CJ" ('; -
I t-r 1,64 fO .0 1 0= I ±ý 1,464(. fOr 11/c 1.0L
Calculation of Stress Intensity Factor •'U.S.NRCThree Independent Methods - - ,
Fracture Analysis of Vessels - Oak Ridge (FAVOR) method:
- Similar to the API-579-1 method, except that a 3 rd order polynomial isused for the stress distribution.
Newman and Raju for internal pressure:
K, 7- ' 0
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Calculation of Stress Intensity Factor -It U.S.NRCApplication of the Methods Pift.•Ia.,- p ad,,d a.n,,,
" API-579-1 and FAVOR methods:
- Are based upon the principle of elastic superposition.
- May be applied for multiple loading conditions, if:
* All conditions are mode I and
* The polynomial used to describe the stress fits the actual stress profile well.
" The Newman and Raju equation was derived only for internalpressure and should be used only for that case.
InputsGeometry, Material Properties, etc.
U.S.NRC
Description valm~e
___________________0 16m [0.51 ft)R"( 20,6at__________ 0.1to 0,0
(1_____________C____ 113
K-terial Propertie ______________2,0006 Wla f4.200O' kipeft)
___________________0.30
'4 ~1.30100 mmlmK [7.20x10" MtftR]k 38 W/(m-K) [22 STUI(hr-fl.R)I
7770 k~/m4 [485 lbnft,']1536 J/(IrgK) [ 0.13 BTUI(Ib,.R)]I
Thermal Loading Conditions __________________________________5673 Wt~rm2-K) [ 1000 BTUI(hr-tt.R[
('R 0.02 Kis 1100 R/lir]________________561 K [1010 R)
fhnical Loin Conditici
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Outline -U.S.NRC
" Introduction and Motivation
" Analysis Methods
" Results
" Conclusion
Temperature DistributionContour Plots
350000
3DOOIT [K]
2500 n2250001•
20000 A
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" Small gradients at the beginningand end of the cooldown.
° Highest gradient observedbetween 15 000 s and 20 000 s.
18000
U Fesive . Pamton u nlioO I..lOm " "
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Thermal Stress DistributionHoop Stress Contour
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tAv a-'m
3o•=
2900C
200CK -I".41444? I?
* Vanishing thermal stresses earlyand late in the transient.
• Highest magnitude stressesobserved between 5 000 and20 000 s.
* Tension at ID, compression at OD.
500C
Stress Intensity Factor: ThermalTime History
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° API-579-1 method with a/c = 1/3,a/t = 1/4.
* Highest stress intensity factorobserved at 14 000 s.
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Stress Intensity Factor: ThermalComparison of Different Methods
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"--'IA6M6OoE , -MaxiI- - . A,,.676 I10 FAVORI
• RGIi
API-o~fnra,
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mum K in the transient.
ASME Code equations bound579-1 and FAVOR methods/t < 0.55.
for a
Subsequent agreement.
Stress Intensity Factor: ThermalEffect of Vessel Thickness
I S RG/ASconsermethod
U.S.NRC
ME Code equationvatively bounds the API-579-1
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Pressure Stress DistributionHoop Stress
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4A'
395 I
300
.............
Approximately linear distribution
ID: -400 MPa, OD: -380 MPaI.
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800 -
Stress Intensity Factor: PressureComparison of Different Methods
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40U
400
3000
2000
ISO
0 0APME co0o
40;
* Agreement up to a/t = 0.5.
RG/ASME Code equation becomesincreasingly conservative for a/t >0.5.
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Outline ,tU.S.NRC
" Introduction and Motivation
" Analysis Methods
" Results
" Conclusion
Conclusion tU.S.NRC
" The RG/ASME Code equations for estimating stress intensity factorunder thermal and internal pressure loading conditions agree with orconservatively bound independent methods for R/t = 20.
Reference: Conference Proceeding PVP2012-78229.
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