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Elasticplastic Jand COD estimates for axial through-wall cracked pipes
Yun-Jae Kim, Nam-Su Huh, Young-Jae Park, Young-Jin Kim*
SAFE Research Centre, School of Mechanical Engineering, Sungkyunkwan University, 300 Chunchun-dong, Jangan-gu, Kyonggi-do,
Suwon 440-746, South Korea
Received 5 January 2002; revised 19 March 2002; accepted 19 March 2002
Abstract
This paper proposes engineering estimation equations of elasticplastic Jand crack opening displacement (COD) for axial through-wall
cracked pipes under internal pressure. On the basis of detailed 3D nite element (FE) results using deformation plasticity, the plastic
inuence functions for fully plastic J and COD solutions are tabulated as a function of the mean radius-to-thickness ratio, the normalised
crack length, and the strain hardening. On the basis of these results, the GE/EPRI-type J and COD estimation equations are proposed and
validated against 3D FE results based on deformation plasticity. For more general application to general stressstrain laws or to complex
loading, the developed GE/EPRI-type solutions are re-formulated based on the reference stress (RS) concept. Such a re-formulation provides
simpler equations for Jand COD, which are then further extended to combined internal pressure and bending. The proposed RS based Jand
COD estimation equations are compared with elasticplastic 3D FE results using actual stressstrain data for Type 316 stainless steels. The
FE results for both internal pressure cases and combined internal pressure and bending cases compare very well with the proposed Jand COD
estimates. q 2002 Published by Elsevier Science Ltd.
Keywords: Axial through-wall crack; Crack opening displacement; J-integral; Reference stress approach; Finite element; Plastic inuence functions
1. Introduction
Leak-before-break (LBB) analysis is an important frac-
ture mechanics concept for design and integrity evaluation
of nuclear pressurised piping. In this respect, signicant
efforts have been made over the last two decades on elastic
plastic fracture mechanics methods for LBB analysis [13].
However, a majority of research activities have been
focused on analyses of circumferential cracked pipes, but
reports on axial cracked pipes are rare. For instance, noting
that application of LBB analysis requires estimates of the J-
integral and the crack opening displacement (COD), there
are currently a number of engineering methods available to
estimate elastic plastic J and COD for circumferential
through-wall cracked (TWC) pipes [411], whereas few
methods are yet available for axial TWC pipes. In the GE/
EPRI handbook [12], the Dugdale model is given for esti-
mating elastic plastic Jof axial TWC pipes under pressure,
and a small scale yielding model for estimating COD.
Although this may be due to the fact that axial cracks in
pipes would be less signicant than circumferential cracks,a reliable non-linear fracture mechanics method for the LBB
analysis of axial cracked pipes is still desirable.
The goal of this paper is to develop an elasticplastic
fracture mechanics method to estimate J and COD for
axial TWC pipes under internal and combined pressure
and bending. To achieve this goal, 3D nite element (FE)
analyses based on deformation plasticity are carried out to
determine fully plastic components of J and COD for axial
TWC pipes under internal pressure. These results are re-
formulated in the form of the reference stress (RS)
approach, which is then validated against further elastic
plastic 3D FE analyses using realistic stressstrain data.
Finally, the extension of the proposed RS based Jestimation
method to combined pressure and bending and to estimate
other non-linear fracture mechanics parameters, such as the
Cp-integral, is discussed.
2. Fully plastic J and COD solutions
2.1. FE analysis based on deformation plasticity
Fig. 1 depicts an axial TWC pipe under internal pressure
p, with relevant dimensions, considered in the present work.
International Journal of Pressure Vessels and Piping 79 (2002) 451464
0308-0161/02/$ - see front matter q 2002 Published by Elsevier Science Ltd.
PII: S0308-0161(02) 00030-3
www.elsevier.com/locate/ijpvp
* Corresponding author. Tel.:182-31-290-5274; fax:182-31-290-5276.
E-mail address: [email protected] (Y.-J. Kim).
Abbreviations: COD, crack opening displacement; ERS, enhanced refer-
ence stress; FE, nite element; GE/EPRI, general electric/electric power
research institute; LBB, leak-before-break; RO, RambergOsgood;
TWC, through-wall cracked
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Some important dimensions for the pipe should be noted.
The mean radius and the thickness of the pipe are denoted as
Rm and t, respectively, and the half crack length is denotedby c. The plastic limit load solution (see e.g. Miller [13])
suggests that important non-dimensional variables are the
ratio of mean radius to the thickness, Rm=t; and the normal-
ised crack length parameter r, dened by
r cRmt
p 1
Elastic plastic analyses of the FE model for the axial TWC
pipe (Fig. 1) were performed using the general-purpose FE
program, ABAQUS [14]. The tensile properties for the FE
analysis are assumed to follow the RambergOsgood
(RO) relation:
1
10 s
sy1 a
s
sy
2 3n
2
where 10, sy, a and n are constants, with E10 sy whereE and sy are Young's modulus and the yield strength,
respectively. The deformation plasticity option with a
small geometry change continuum model was invoked. In
the present FE calculations, specic values of the variables
a , E and sy were used; a 1; E 190 GPa and sy 400 MPa: It should be noted, however, that such specic
values do not affect fully plastic J and COD solutions
based on deformation plasticity, which will be proposed in
the present work, as plastic inuence functions do not
depend on these variables (see Section 2.2 for details). For
the strain hardening exponent n, on the other hand, three
values were selected, n 1; 3 and 7. Note that the case ofn 1 corresponds to the elastic case with Poisson's ratio ofn 0:3:1 Regarding other variables, two values of Rm=twere considered, Rm=t 5 and 20, and four values of rwere considered, r
0:5; 1.0, 2.0 and 3.0. Thus a total of
24 calculations were performed in the present work.The number of elements and nodes in a typical FE
mesh are 1440 elements/8485 nodes. Two elements
were used through the thickness, which has been
shown to provide the most reliable results for COD
calculation [15,16]. Although the aspect ratio of the
near-tip elements is quite high, it does not affect the
present FE computations of J and COD, as the stress
gradient through the wall is low for the present
problem. For problems where the stress gradient through
the wall is high, for instance when through-wall bend-
ing is applied or when welding residual stress is con-
sidered, more elements should be used through thethickness. Considering symmetry conditions, only one
quarter of the pipe was modelled. Fig. 2 shows the
FE mesh for r 1 and Rm=t 5: To avoid problemsassociated with incompressibility, reduced integration
20 node elements (element type C3D20R in ABAQUS)
were used. Internal pressure was applied as a distributed
load to the inner surface of the FE model, together with
an axial tension equivalent to the internal pressure
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464452
Nomenclature
c half crack length
E Young's modulus, E0 E=12 n2 for planestrain; E for plane stress
h1, h2 fully plastic inuence functions for the GE/
EPRI methodJ J-integral
K linear elastic stress intensity factor
n strain hardening index 1 # n , 1 forRambergOsgood model, Eq. (2)
nI strain hardening indices for the ERS-based
COD estimation equation, Eq. (32)
p internal pressure
pL plastic limit pressure assuming the limiting
stress ofsypoR optimised reference pressure
Rm mean radius of pipe
t pipe wall thickness
a coefcient of RambergOsgood modeld crack opening displacement at centre of crack
1 strain, general
n Poisson's ratio
r normalised crack length, c=Rmtps stress, general
sref reference stress
sy yield strength
Fig. 1. Schematic illustration of axial TWC pipes under internal pressure p.
1 The effect of n on J was found to be minor for the present problem.
For instance, the value ofJusing n 0:5 differs within 3% from that usingn 0:3 for all cases considered.
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applied at the end of the pipe to simulate the closed
end. More importantly, 50% of the internal pressure was
applied to the crack face to consider the effect of the
crack face pressure.
The J-integral values were extracted from the FE resultsusing a domain integral, as a function of the applied internal
pressure. The J values are averaged, whereas the COD
values, were determined from the FE displacement results
in the mean thickness of the centre of the crack.
2.2. FE based plastic inuence functions
Elastic FE calculations (with n 1) gave the elastic J, Je,from which the shape factor Ffor the elastic stress intensity
factor K was found:2
Je
K2
E 1
Es1 pcp F 2; s1
pRi
2t 3
Note that the plane stress condition was assumed to calcu-
late the values of F.3 Resulting values of F are given in
Table 1, and shown in Fig. 3. Fig. 3 also compares the
present results with published results [12], showing good
agreement. Similarly, the shape factor V, associated with
the elastic COD, de, can be found from
de 4
Es1cV 4
Note again that the plane stress condition was assumed to
calculate the values ofV. Resulting values ofVare given in
Table 2, and shown in Fig. 3. Fig. 3 also compares thepresent results with those in the GE/EPRI handbook [12]
and in Refs. [17,18]. Noting that the solutions in Refs.
[17,18] were obtained from detailed 3D FE analysis, excel-
lent agreement between the present solutions and those in
Refs. [17,18] gives condence in the present FE calcula-
tions. On the other hand, approximate solutions given in
the GE/EPRI handbook slightly underestimate the COD.
For RO materials, the plastic components ofJand COD,Jp and dp, can be expressed as
Jp asy10ch1np
pL
!n11
5
dp a10ch2np
pL
!n
6
where pL denotes the plastic limit pressure for axial TWC
pipes, of which the expression used in the present work is
the solution based on detailed FE limit analyses [19]:
pL 23
p syt
Rm
1
11 0:34r1 1:34r2p 7
where r is dened in Eq. (1). Fig. 4 compares this solution
with the limit pressure resulting from detailed 3D FE limit
analyses [19], together with two published solutions. The
rst one is the limit pressure solution due to Folias [20],
which is given by
pL syt
Rm
111 1:05r2
p 8
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464 453
Fig. 2. Typical nite element meshes for axial TWC pipe with Rm=t 5 andr 1:0:
Table 1
Values of the shape factor F for the stress intensity factor and the plastic
inuence h1-functions for the plastic J-integral
Rm=t r F h1n 1 h1n 3 h1n 7
5 0.5 2.743 3.859 5.656 6.710
1 3.604 3.740 4.730 4.367
2 5.576 3.409 3.578 2.8663 7.465 3.055 2.851 2.270
20 0.5 2.545 3.897 5.806 6.901
1 3.344 3.779 4.927 4.648
2 5.240 3.533 4.012 3.606
3 7.113 3.255 3.430 3.324
Table 2
Values of the shape factor V for the elastic COD and the plastic inuence
h2-functions for the plastic COD
Rm=t r V h2n 1 h2n 3 h2n 7
5 0.5 2.632 4.460 5.617 6.388
1 3.922 4.980 5.824 5.460
2 8.582 6.723 7.223 6.334
3 15.417 8.540 8.606 7.656
20 0.5 2.452 4.500 5.695 6.407
1 3.627 4.989 5.946 5.611
2 8.093 6.868 7.915 7.649
3 14.913 8.949 10.100 10.744
2 The stress on the end of the pipe, s1, in Eq. (3), is the thin-shell
approximation. The thick-shell averaged stress is slightly different.
However, for Rm=t$ 5 considered, there is not much difference. When
the correct expression for s1 is used, the corresponding value of F can
easily be found from Eq. (3). Thus the use of the correct expression ofs1 is
not so important, and for clarity, the thin-shell approximation is used in the
present work.3 This plane stress assumption may not be valid for thick-walled pipes.
However, the plane stress assumption does not affect the present solution,
as the fully plastic solutions do not depend on elastic solutions.
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The other solution is one due to Erdogan [21]
pL syt
Rm
1
0:6141 0:87542r1 0:386 exp22:275r
!9
Fig. 4 shows that Eq. (7) agrees very well with the FE results
for all ranges of r, whereas agreement between the FEsolutions and the above published solutions is excellent
for r. 0:5; but not so good for 0 , r, 0:5: This is
because in the limiting case of an uncracked cylinder r!0; the above two solutions converge to the Tresca solutionnot to the Mises solution, and thus the factor 2=
3
pis
missing.
Note that in Eqs. (5) and (6), the plastic inuence func-
tions, h1 and h2, are functions ofRm=t; the normalised crack
length r and the strain hardening exponent n. Values of h1and h2 were calibrated from the present FE analysis as
follows. Firstly, the plastic components of the FE J and d
values were calculated by subtracting their elastic com-
ponent from the total FE J and d values:
JFEp JFE 2
1
E
pRi
2t
2pcF
2 10
dFEp
dFE 24
E
pRi
2t cV 11
Then the values of h1 and h2 were calibrated from Eqs. (5)
and (6), respectively. Note that the calculated values of h1and h2 depend on the load magnitude, as shown in Fig. 5. In
the present work, the value was chosen as the (almost)
asymptotic value at large loads. Resulting values of h1 and
h2 are tabulated in Tables 1 and 2, respectively.
3. J and COD estimations based on GE/EPRI method
The plastic inuence functions, reported in Section 2.2,
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464454
Fig. 3. Variations of the shape factors, Fand V, for the stress intensity factor and the elastic COD with r: the F-solutions for (a) Rm=t 5 and (b) Rm=t 20;the V-solutions for (c) Rm=t 5 and (d) Rm=t 20: The present solutions are compared with Ref. [12] and Refs. [17,18].
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can be used to estimate J and COD for axial TWC pipes,
based on the GE/EPRI approach (see for instance Refs.
[4,12]). For instance, the J-integral can be estimated from
J 1E
pRi
2t
pce
pFce
!21asy10ch1n
p
pL
n11
12
where the effective crack length ce is estimated from
ce c1 wry;
w 111 p=pL2
; ry 12p
n2 1n1 1
Ksy
2 32 13On the other hand, the COD can be estimated from
d 4E
pRi
2t
ceVce1 a10ch2n
p
pL
!n
14
where the values ofh1(n) and h2(n) can be determined using
the data given in Tables 1 and 2 with appropriate interpola-
tion/extrapolation. Fig. 6 compares estimated J, according
to Eq. (12), with the FE results for four cases of a and n
(Note that for all cases, sy is xed tosy 400 MPa). Fig. 7,on the other hand, compares the estimated COD, according
to Eq. (14), with the FE results. They show that the proposed
GE/EPRI-type J and COD estimations are quite good. It is
worth noting, however, that the FE results shown in Figs. 6
and 7 are based on the idealised stressstrain data according
to the RO relation, see Eq. (2).The GE/EPRI-type J and
COD estimation equations, given above, have some inher-
ent problems. First of all, this method requires the RO
idealisation of the tensile data, and there can be inaccuracy
associated with this process. The RO idealisation is known
to be a poor approximation to tensile data for typical
materials, which consequently can produce inaccuracy in
the estimated J and COD. Readers can refer to other
published papers (e.g. Refs. [5,6,9,10,22,23]). The second
problem is that it is difcult to generalise this method tomore complex problems, such as to combined loading cases.
To provide relevant solutions for combined loading, in prin-
ciple more extensive FE calculations have to be performed.
To overcome these problems, the GE/EPRI-type Jand COD
estimation results, given in this section, are re-formulated in
the form of the RS approach [24] in Section 4.
4. J and COD estimations based on reference stress
concept
4.1. Reference stress formulation
For the elastic case n 1; the elastic component of Jand COD, Je and de, in Eqs. (3) and (4) can be re-written as
Je asy10ch1n 1p
pL
!215
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464 455
Fig. 5. Variation of the FE results for h1 and h2 with the load magnitude for Rm=t 5 and r 0:5:
Fig. 4. Comparison of the FE limit pressure solutions for axial TWC pipes
under internal pressure with known solutions. The FE result for r 0corresponds to that for uncracked pipes.
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de a10ch2n 1p
pL
!16
where h1n 1 and h2n 1 denote the values ofh1 andh2 for elastic materials, respectively. Comparing Eq. (15)
with Eq. (3) gives the values of h1n 1; which are tabu-lated in Table 1. Normalising Eq. (5) with respect to Eq. (15)
gives
Jp
Je a
h1nh1n 1
p
pL !
n21
17
Variations ofh1n=h1n 1 with n are shown in Fig. 8 for
Rm=t 5 and 20. Similarly, comparing Eq. (16) with Eq. (4)gives the values of h2n 1; which are tabulated in Table2. Normalising Eq. (6) with respect to Eq. (16) gives
dp
de a h2n
h2n 1p
pL
!n21
18
Variations ofh2n=h2n 1 with n are also shown in Fig. 8for Rm=t 5 and 20. The results in Fig. 8 show that thevalues of h1n=h1n 1 and h2n=h2n 1 are rather
sensitive to strain hardening n, that is ranges from ,0.7 to
,1.8 for n ranging from 1 to 7.
Introducing another normalising (reference) pressure pref,
and re-phrasing Eqs. (17) and (18) gives
Jp
Je a h1n
h1n 1pref
pL
!n21
& 'p
pref
!n21
19
dp
de a h2n
h2
n
1
pref
pL
!n21& ' p
pref
!n21
20
Noting that h1n=h1n 1; h2n=h2n 1 and pref=pL arenon-dimensional variables, Eqs. (19) and (20) can be written
as
Jp
Je aH1
p
pref
!n21
21
dp
de aH2
p
pref
!n21
22
where non-dimensional functions, H1 and H2, presumably
depend on Rm=t; r and n. An important underlying idea of
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464456
Fig. 6. (ad): Comparison of FE J results for axial TWC pipes under internal pressure with the GE/EPRI estimates. Note that the FE results are based on
RambergOsgood materials with deformation plasticity.
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the RS based J and COD estimation approach is that a
proper denition of pref can minimise the dependence of
H1 and H2 on Rm=t; r and n in Eqs. (21) and (22)
[8,10,24]. Suppose such a load has been found, which will
be termed `optimised reference pressure', poR. On the basis
of the present FE results, the following expressions are
proposed for poR:
poR crpL 23
cr 20:06r2 1 0:21r1 0:82 for r, 1:5
1 for r$ 1:5@ 24
where the expression for pL is found from Eq. (7). Note that
for r! 0; cr ! 0:82; whereas for r$ 1:5;cr 1:Introducing these expressions for pref poR into Eqs. (21)and (22) gives the values of H1 and H2. Variations of the
resulting H1 and H2 values with n are shown in Fig. 9. The
results in Fig. 9 rstly show that the sensitivity in
h1n=h1n 1 and h2n=h2n 1 is reduced in H1 andH2. For instance, for the range of 1 # n # 7; the values of
h1n=h1n 1 and h2n=h2n 1 range from ,0.7 to,1.8, whereas those for H1 and H2 from ,0.8 to ,1.2.
Noting that the values of both H1 and H2 are now closer to
unity, Eqs. (21) and (22) can be approximated as
Jp
Je< a
p
poR
!n21
25
dp
de< a
p
poR
!n21
26
Noting that for the RO materials, the plastic strain is
related to the stress as
1p a sE
s
sy
2 3n2
1 27
Eqs. (25) and (26) can be written explicitly in terms of the
RS, sref, and the reference strain, 1ref, as
Jp
Je
E1ref
sref; sref
p
poRsy 28
dp
de
E1ref
sref; sref
p
poRsy 29
In Eqs. (28) and (29), sy denotes the 0.2% proof stress, and
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464 457
Fig. 7. (ad): Comparison of FE COD results for axial TWC pipes under internal pressure with the GE/EPRI estimates. Note that the FE results are based on
RambergOsgood materials with deformation plasticity.
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1ref is the true strain at s sref; determined from the truestressstrain data.
4.2. Proposed reference stress based J and COD estimation
Eq. (28) gives the estimate of the plastic J-integral, and
the total J-integral can be estimated by adding the elastic
component with a plasticity correction [25]:
J
Je
E1ref
sref
11
2
sref
sy2 3
2sref
E1ref
; sref
p
poR
sy
30
where poR is given in Eq. (23). The COD can be estimated
from Refs. [811]
d
de
E1ref
sref1
1
2
sref
sy
2 32sref
E1reffor 0 # sref, sy
d
de
1
sref
sy
2 3n121
for sy # sref
VbbbbbbbbbbX
31In Eq. (31), (d/de)1 denotes the value of (d/de) at sref=sy 1;
calculated from the rst equation in Eq. (31), so that Eq. (31)
is continuous at sref sy: The strain hardening index n1 inEq. (31) should be estimated from
n1 ln1u;t 2 su;t=E=0:002
lnsu;t=sy32
where su,t and 1u,t denote the true ultimate tensile stress and
percentage uniform elongation at s su; respectively.These are obtained from the corresponding engineering
values using
su;t 11 1usu; 1u;t ln11 1u 33
4.3. FE validation
To validate the proposed RS based Jand COD estimation
equations for axial TWC pipes under internal pressure, addi-
tional elasticplastic 3D FE analyses were performed. The
main difference between these calculations and the previous
ones in Sections 2 and 3 is the material properties. The
previous cases considered idealised RO materials with
deformation plasticity, whereas the present cases used
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464458
Fig. 8. Variations of h1
n
=h1
n
1
for the J-integral with n for (a) Rm=t
5 and (b) Rm=t
20; variations of h2
n
=h2
n
1
for the COD with n for (c)
Rm=t 5 and (d) Rm=t 20:
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actual experimental uni-axial stressstrain data of Type 316
stainless steel at the temperature, T 288 8C; withincremental plasticity option. Stressstrain curves for the
material are shown in Fig. 10, and the relevant data are
summarised in Table 3. Two values of Rm=t and r were
considered, Rm=t 5 and 20, and r 0:5 and 2.0, givinga total of four cases.
Elasticplastic analyses of this FE model were performed
using ABAQUS [14]. The experimental true stressplastic
strain data were directly given in the FE analysis. Materials
were modelled as isotropic elastic plastic materials that
obey the incremental plasticity theory, and a small geometrychange continuum FE model was employed. Detailed
information on the FE model is in Section 2.1.
Fig. 11 compares the FE Jand COD results for Rm=t 5with the predictions based on the proposed RS method,
denoted as the `enhanced reference stress (ERS)' method.
In Fig. 11, the Jvalues are normalised with respect to sy and
c, while the COD (d) values with respect to c. The load,
internal pressure, is normalised with respect to the opti-
mised reference pressure, poR. (see Eq. (23)). The results
are also compared with two other methods: the GE/EPRI
method and the RS method. Noting that the GE/EPRI Jand
COD estimations are developed in the present work (see
Section 3), the resulting J and COD are also compared
with the FE results. Application of the GE/EPRI method
rstly requires that the material's tensile data should be
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464 459
Fig. 9. Variations ofH1 for the J-integral with n for (a) Rm=t 5 and (b) Rm=t 20; variations ofH2 for the COD with n for (c) Rm=t 5 and (d) Rm=t 20:
Fig. 10. Stressstrain curve for SA312 Type 316 (288 8C) and the resulting
RambergOsgood t.
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tted using the RO relation, see Eq. (2). In the presentwork, the entire true stressstrain data up to the ultimate
tensile strength were tted4 using the ROFIT program [26],
developed by Battelle. The resulting RO parameters, a
and n, are listed in Table 3, and the resulting RO ts are
compared with the experimental tensile data in Fig. 10.
Once the RO parameters, a and n, are determined, then
Jand COD can be estimated using Eqs. (12)(14) in Section
3, with the values ofh1(n) and h2(n) obtained by interpolat-ing the present FE results (tabulated in Tables 1 and 2). The
resulting values of J and COD are denoted as `Present GE/
EPRI' in Fig. 11. The RS method is similar to the ERS
method, except that the RS is dened using the limit pres-
sure, Eq. (7), instead of the optimised reference pressure,
Eq. (23). For r 2; the optimised reference pressure is thesame as the limit pressure, and thus the ERS-based predic-
tions are same as those based on the RS method. The
comparisons in Fig. 11 show that the proposed ERS-based
J and COD estimates are in overall good agreements with
the FE results. On the other hand, the GE/EPRI J and COD
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464460
Table 3
Summary of tensile properties for SA312 Type 316 stainless steel at 288 8C, used in the present FE analysis
Material E (GPa) sy (MPa) su (MPa) RO Parameters ERS Parameters
a n 1u n1
SA312 Type 316 (288 8C) 190 165 455 8.42 2.92 0.3 3.82
Fig. 11. (a d) Comparison of FE Jand COD results for axial TWC pipes with Rm=t 5 under internal pressure with the engineering estimates: (i) the proposedenhanced reference stress (ERS) method, (ii) the GE/EPRI solutions, developed in the present work (Present GE/EPRI), and (iii) the reference stress (RS)
method.
4 There are other ways to t the tensile data using the RO relation.
Typical ways include to t the data only up 5% strain and to t the data
from 0.1% strain to 0.8 1u,t, where 1u,t denotes the true ultimate strain.
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estimates are not so accurate, compared to the FE results.
Such results are consistent with our earlier nding [10,22]
and such inaccuracy is associated with the RO t. In fact, if
different ways of tting the RO equation are performed,
accuracy can be improved, but no guidance on the best RO
t can be given since it depends on material [22]. The Jand
COD estimates based on the RS method are good but less
accurate than those based on the ERS method. Fig. 12
repeats the results for Rm=t
20: It can be seen that the
effect of Rm=t on estimated J and COD is minimal, andthus the same conclusions as those for Rm=t 5 can bedrawn.
5. Discussion
In this paper, engineering Jand COD estimation equations
for axial TWC pipes under internal pressure are developed.
On the basis of detailed 3D FE results with deformation
plasticity, fully plastic components ofJand COD estimation
equations for RO materials are given, which lead to the GE/
EPRI-type estimation equations. The developed solutions are
re-formulated based on the RS concept, to overcome
problems associated with the RO tting. Comparison with
elasticplastic 3D FE results using actual stressstrain data
for Type 316 stainless steels with the proposed J and COD
estimates shows excellent agreement.
The present work considers internal pressure only.
However, typical pressurised piping components are subject
to combined internal pressure and global bending. It has
been found that a bending loading has only a slight effecton plastic limit load for axial TWC pipes [13]. Noting that
the denition of the RS in the proposed enhanced RS
approach is related to the plastic limit load, it can be argued
that the proposed Jand COD estimation equations for inter-
nal pressure can be equally applied to combined pressure
and global bending loading.5 To verify our proposal, the
proposed J and COD estimates for internal pressure,
Eqs. (30)(33), are compared with the FE results for axial
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464 461
Fig. 12. (ad) Comparison of FE J and COD results for axial TWC pipes with Rm=t 20 under internal pressure with the engineering estimates: (i) theproposed enhanced reference stress (ERS) method, (ii) the GE/EPRI solutions, developed in the present work (Present GE/EPRI), and (iii) the reference stress(RS) method.
5 This statement is true not only for the proposed enhanced RS based J
and COD estimations but also for the GE/EPRI and RS based estimations.
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TWC pipes under combined pressure and global bending.
The load proportionality factor l for combined loading is
dened as
l MpR2i pRm34
In the FE analysis, internal pressure and bending moment
are increased in a proportional manner. For the proportion-
ality factor, only one value of l was considered, l 0:5:The axial crack was located at the position of the maximum
tensile stress due to global bending. The resulting FE J andCOD results are compared with the proposed ERS method,
the GE/EPRI method and the RS method in Fig. 13 for
Rm=t 5 and in Fig. 14 for Rm=t 20: See Section 4.3 fordetailed descriptions on presentation of results. It can be
seen that the bending moment in fact has a minimal effect
on estimated J and COD and thus those proposed for inter-
nal pressure can be used for combined pressure and global
bending. Although the results for one value ofl were given
here, it would be sufcient to show that the proposed J and
COD estimates can be used for combined pressure and
global bending.
Whenthe cracked pipeis operatedat elevatedtemperatures,
assessment should be carried out against creep crack growth,
which in turn requires estimation of the Cp-integral and the
COD due to creep [27]. On the basis of the analogy between
plasticity and creep, the present estimation equations can be
used to estimate the Cp-integral and the COD rate, _dc; due to
creep [28]
Cp EE0
K
2_1c
sref35
_dc
de _1csref=E
with dct 0 0 36
where _1c isthecreepstrainrateattheRS s sref; determinedfrom the actual creep-deformation data. Validation of these
estimation equations will be given in a separate paper [29].
6. Conclusions
This paper proposes engineering estimation equations of
elasticplastic Jand COD for axial TWC pipes under inter-
nal pressure. On the basis of detailed 3D FE results using
Y.-J. Kim et al. / International Journal of Pressure Vessels and Piping 79 (2002) 451464462
Fig. 13. (ad) Comparison of FE Jand COD results for axial TWC pipes with Rm=t 5 under combined internal pressure and bending with the engineeringestimates: (i) the proposed enhanced reference stress (ERS) method, (ii) the GE/EPRI solutions, developed in the present work (Present GE/EPRI), and (iii) thereference stress (RS) method.
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deformation plasticity, the plastic inuence functions for
fully plastic Jand COD solutions are tabulated as a function
of the mean radius-to-thickness ratio, the normalised crack
length and the strain hardening index. On the basis of these
results, GE/EPRI-type J and COD estimation equations are
proposed and validated against the 3D FE results based on
deformationplasticity. Formore general applicationto general
stressstrain laws or to complex loading, the developed GE/
EPRI-type solutions are re-formulated based on the RS
concept. Such a re-formulation provides simpler equations
for Jand COD, which are then further extended to combinedinternal pressure and bending. The proposed RS based Jand
COD estimation equations are compared with elasticplastic
3D FE results using actual stressstrain data for Type 316
stainless steels. The FE results for both internal pressure
cases and combined internal pressure and bending cases
compare very well with the proposedJand COD estimations.
Acknowledgements
The authors are grateful for the support provided by a
grant from Safety and Structural Integrity Research Centre
at Sungkyunkwan University.
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