ASME Section VIII div 2 2010. ASME Boiler and Pressure Vessel Code. Alternative Rules

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2010 SECTION VIII, DIVISION 2

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5.2.3.5 Assessment Procedure

The following assessment procedure is used to determine the acceptability of a component using a limit-load

analysis.

a) STEP 1 – Develop a numerical model of the component including all relevant geometry characteristics.

The model used for the analysis shall be selected to accurately represent the component geometry,

boundary conditions, and applied loads. The model need not be accurate for small details, such as

small holes, fillets, corner radii, and other stress raisers, but should otherwise correspond to commonly

accepted practice.

b) STEP 2 – Define all relevant loads and applicable load cases. The loads to be considered in the

analysis shall include, but not be limited to, those given in Table 5.1.

c) STEP 3 – An elastic-perfectly plastic material model with small displacement theory shall be used in the

analysis. The von Mises yield function and associated flow rule should be utilized. The yield strength

defining the plastic limit shall equal

1.5S .

d) STEP 4 – Determine the load case combinations to be used in the analysis using the information from

STEP 2 in conjunction with Table 5.4. Each of the indicated load cases shall be evaluated. The effects

of one or more loads not acting shall be investigated. Additional load cases for special conditions not

included in Table 5.4 shall be considered, as applicable.

e) STEP 5 – Perform a limit-load analysis for each of the load case combinations defined in STEP 4. If

convergence is achieved, the component is stable under the applied loads for this load case. Otherwise,

the component configuration (i.e. thickness) shall be modified or applied loads reduced and the analysis

repeated. Note that if the applied loading results in a compressive stress field within the component,

buckling may occur, and the effects of imperfections, especially for shell structures, should be

considered in the analysis (see paragraph 5.4).

5.2.4 Elastic-Plastic Stress Analysis Method

5.2.4.1 Overview

a) Protection against plastic collapse is evaluated by determining the plastic collapse load of the

component using an elastic-plastic stress analysis. The allowable load on the component is established

by applying a design factor to the calculated plastic collapse load.

b) Elastic-plastic stress analysis provides a more accurate assessment of the protection against plastic

collapse of a component relative to the criteria in paragraphs 5.2.2 and 5.2.3 because the actual

structural behavior is more closely approximated. The redistribution of stress that occurs as a result of

inelastic deformation (plasticity) and deformation characteristics of the component are considered

directly in the analysis.

5.2.4.2 Numerical Analysis

The plastic collapse load can be obtained using a numerical analysis technique (e.g. finite element method)

by incorporating an elastic-plastic material model to obtain a solution. The effects of non-linear geometry

shall be considered in this analysis. The plastic collapse load is the load that causes overall structural

instability. This point is indicated by the inability to achieve an equilibrium solution for a small increase in load

(i.e. the solution will not converge).

5.2.4.3 Acceptance Criteria

The acceptability of a component using an elastic-plastic analysis is determined by satisfying the following

two criteria.

a) Global Criteria – A global plastic collapse load is established by performing an elastic-plastic analysis of

the component subject to the specified loading conditions. The plastic collapse load is taken as the load

which causes overall structural instability. The concept of Load and Resistance Factor Design (LRFD) is

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used as an alternate to the rigorous computation of a plastic collapse load to design a component. In

this procedure, factored loads that include a design factor to account for uncertainty, and the resistance

of the component to these factored loads are determined using an elastic-plastic analysis (see Table

5.5).

b) Service Criteria – Service criteria that limit the potential for unsatisfactory performance shall be satisfied

at every location in the component when subject to the design loads (see Table 5.5). Examples of

service criteria are limits on the rotation of a mating flange pair to avoid possible flange leakage

concerns and limits on tower deflection that may cause operational concerns. In addition, the effect of

deformation of the component on service performance shall be evaluated at the design load

combinations. This is especially important for components that experience an increase in resistance

(geometrically stiffen) with deformation under applied loads such as elliptical or torispherical heads

subject to internal pressure loading. The plastic collapse criteria may be satisfied but the component

may have excessive deformation at the derived design conditions. In this case, the design loads may

have to be reduced based on a deformation criterion. Examples of some of the considerations in this

evaluation are the effect of deformation on:

1) piping connections or,

2) misalignment of trays, platforms and other internal or external appurtenances, and

3) interference with adjacent structures and equipment.

If applicable, the service criteria shall be specified in the User’s Design Specification.

5.2.4.4 Assessment Procedure

The following assessment procedure is used to determine the acceptability of a component using an elastic-

plastic stress analysis.

a) STEP 1 – Develop a numerical model of the component including all relevant geometry characteristics.

The model used for the analysis shall be selected to accurately represent the component geometry,

boundary conditions, and applied loads. In addition, refinement of the model around areas of stress and

strain concentrations shall be provided. The analysis of one or more numerical models may be required

to ensure that an accurate description of the stress and strains in the component is achieved.

b) STEP 2 – Define all relevant loads and applicable load cases. The loads to be considered in the design

shall include, but not be limited to, those given in Table 5.1.

c) STEP 3 – An elastic-plastic material model shall be used in the analysis. The von Mises yield function

and associated flow rule should be utilized if plasticity is anticipated. A material model that includes

hardening or softening, or an elastic-perfectly plastic model may be utilized. A true stress-strain curve

model that includes temperature dependent hardening behavior is provided in Appendix 3.D. When

using this material model, the hardening behavior shall be included up to the true ultimate stress and

perfect plasticity behavior (i.e. the slope of the stress-strain curves is zero) beyond this limit. The effects

of non-linear geometry shall be considered in the analysis.

d) STEP 4 – Determine the load case combinations to be used in the analysis using the information from

STEP 2 in conjunction with Table 5.5. Each of the indicated load cases shall be evaluated. The effects

of one or more loads not acting shall be investigated. Additional load cases for special conditions not

included in Table 5.5 shall be considered, as applicable.

e) STEP 5 – Perform an elastic-plastic analysis for each of the load cases defined in STEP 4. If

convergence is achieved, the component is stable under the applied loads for this load case. Otherwise,

the component configuration (i.e. thickness) shall be modified or applied loads reduced and the analysis

repeated. Note that if the applied loading results in a compressive stress field within the component,

buckling may occur, and an evaluation in accordance with paragraph 5.4 may be required.

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5.3 Protection Against Local Failure

5.3.1 Overview

5.3.1.1 In addition to demonstrating protection against plastic collapse as defined in paragraph 5.2, the

applicable local failure criteria below shall be satisfied for a component. The local strain limit criterion does

not need to be checked if the component design is in accordance with the standard details of Part 4.

5.3.1.2 Two analysis methodologies are provided for evaluating protection against local failure to limit the

potential for fracture under applied design loads.

a) The analysis procedures in paragraph 5.3.2 provide an approximation of the protection against local

failure based on the results of an elastic analysis.

b) A more accurate estimate of the protection against local failure of a component can be obtained using

the elastic-plastic stress analysis procedures in paragraph 5.3.3.

5.3.2 Elastic Analysis

In addition to demonstrating protection against plastic collapse, the following elastic analysis criterion shall be

satisfied for each point in the component. The sum of the local primary membrane plus bending principal

stresses shall be used for checking this criterion.

()

123

σσσ

++ ≤ (5.5)

5.3.3 Elastic-Plastic Analysis

5.3.3.1 The following procedure shall be used to evaluate protection against local failure for a sequence

of applied loads.

a) STEP 1 – Perform an elastic-plastic stress analysis based on the load case combinations for the local

criteria given in Table 5.5. The effects of non-linear geometry shall be considered in the analysis.

b) STEP 2 – For a location in the component subject to evaluation, determine the principal stresses,

, the equivalent stress,

, using Equation (5.1) and the total equivalent plastic strain,

peq

c) STEP 3 – Determine the limiting triaxial strain,

, using Equation (5.6) where

m , and

are

determined from Table 5.7.

()

123

exp

133

LLu

σσσ

εε

⎡⎤

⎛⎞

++⎧⎫

⎛⎞

=⋅ − −

⎢⎥

⎜⎟

⎨⎬

⎜⎟

⎝⎠

⎢⎥

⎩⎭

⎝⎠

⎣⎦

(5.6)

d) STEP 4 – Determine the forming strain

based on the material and fabrication method in accordance

with Part 6. If heat treatment is performed in accordance with Part 6, the forming strain may be assumed

to be zero.

e) STEP 5– Determine if the strain limit is satisfied. The location in the component is acceptable for the

specified load case if Equation (5.7) is satisfied.

peq cf L

εε

+≤

(5.7)

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5.3.3.2 If a specific loading sequence is to be evaluated in accordance with the User’s Design

Specification, a strain limit damage calculation procedure may be required. This procedure may also be used

in lieu of the procedure in paragraph 5.3.3.1. In this procedure, the loading path is divided into

k load

increments and the principal stresses,

1,k

2,k

3,k

, equivalent stress,

,ek

, and change in the

equivalent plastic strain from the previous load increment,

,peq k

, are calculated for each load increment.

The strain limit for the

k load increment,

,Lk

, is calculated using Equation (5.8) where

m , and

are determined from Table 5.7. The strain limit damage for each load increment is calculated using Equation

(5.9) and the strain limit damage from forming,

orm

, is calculated using Equation (5.10). If heat treatment

is performed in accordance with Part 6, the strain limit damage from forming is assumed to be zero. The

accumulated strain limit damage is calculated using Equation (5.11). The location in the component is

acceptable for the specified loading sequence if this equation is satisfied.

()

1, 2, 3,

exp

133

kkk

Lk Lu

σσσ

εε

⎡⎤

⎛⎞

⎧⎫

⎛⎞

⎪⎪

⎢⎥

⎜⎟

=⋅ − −

⎨⎬

⎜⎟

⎢⎥

⎝⎠

⎪⎪

⎩⎭

⎝⎠

⎣⎦

(5.8)

peq k

(5.9)

exp 0.67

form

⎡⎤

⎛⎞

⋅−

⎢⎥

⎜⎟

⎝⎠

⎣⎦

(5.10)

1.0

form k

DD D

εε ε

=+ ≤

∑

(5.11)

5.4 Protection Against Collapse From Buckling

5.4.1 Design Factors

5.4.1.1 In addition to evaluating protection against plastic collapse as defined in paragraph 5.2, a design

factor for protection against collapse from buckling shall be satisfied to avoid buckling of components with a

compressive stress field under applied design loads.

5.4.1.2 The design factor to be used in a structural stability assessment is based on the type of buckling

analysis performed. The following design factors shall be the minimum values for use with shell components

when the buckling loads are determined using a numerical solution (i.e. bifurcation buckling analysis or

elastic-plastic collapse analysis).

a) Type 1 – If a bifurcation buckling analysis is performed using an elastic stress analysis without geometric

nonlinearities in the solution to determine the pre-stress in the component, a minimum design factor of

Φ= shall be used (see paragraph 5.4.1.3). In this analysis, the pre-stress in the component is

established based on the loading combinations in Table 5.3.

b) Type 2 – If a bifurcation buckling analysis is performed using an elastic-plastic stress analysis with the

effects of non-linear geometry in the solution to determine the pre-stress in the component, a minimum

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design factor of

1.667

Bcr

Φ= shall be used (see paragraph 5.4.1.3). In this analysis, the pre-stress

in the component is established based on the loading combinations in Table 5.3.

c) Type 3 – If a collapse analysis is performed in accordance with paragraph 5.2.4, and imperfections are

explicitly considered in the analysis model geometry, the design factor is accounted for in the factored

load combinations in Table 5.5. It should be noted that a collapse analysis can be performed using

elastic or plastic material behavior. If the structure remains elastic when subject to the applied loads, the

elastic-plastic material model will provide the required elastic behavior, and the collapse load will be

computed based on this behavior.

5.4.1.3 The capacity reduction factors,

, shown below shall be used unless alternative factors can be

developed from published information.

a) For unstiffened or ring stiffened cylinders and cones under axial compression

0.207 1247

for

=≥ (5.12)

338

1247

389

for

(5.13)

b) For unstiffened and ring stiffened cylinders and cones under external pressure

0.80

= (5.14)

c) For spherical shells and spherical, torispherical, elliptical heads under external pressure

0.124

= (5.15)

5.4.2 Numerical Analysis

If a numerical analysis is performed to determine the buckling load for a component, all possible buckling

mode shapes shall be considered in determining the minimum buckling load for the component. Care should

be taken to ensure that simplification of the model does not result in exclusion of a critical buckling mode

shape. For example, when determining the minimum buckling load for a ring-stiffened cylindrical shell, both

axisymmetric and non-axisymmetric buckling modes shall be considered in determination of the minimum

buckling load.

5.5 Protection Against Failure From Cyclic Loading

5.5.1 Overview

5.5.1.1 A fatigue evaluation shall be performed if the component is subject to cyclic operation. The

evaluation for fatigue is made on the basis of the number of applied cycles of a stress or strain range at a

point in the component. The allowable number of cycles should be adequate for the specified number of

cycles as given in the User’s Design Specification.

5.5.1.2 Screening criteria are provided in paragraph 5.5.2 that can be used to determine if fatigue

analysis is required as part of a design. If the component does not satisfy the screening criteria, a fatigue

evaluation shall be performed using the techniques in paragraphs 5.5.3, 5.5.4 or 5.5.5.

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5.5.1.3 Fatigue curves are typically presented in two forms: fatigue curves that are based on smooth bar

test specimens and fatigue curves that are based on test specimens that include weld details of quality

consistent with the fabrication and inspection requirements of this Division.

a) Smooth bar fatigue curves may be used for components with or without welds. The welded joint curves

shall only be used for welded joints.

b) The smooth bar fatigue curves are applicable up to the maximum number of cycles given on the curves.

The welded joint fatigue curves do not exhibit an endurance limit and are acceptable for all cycles.

c) If welded joint fatigue curves are used in the evaluation, and if thermal transients result in a through-

thickness stress difference at any time that is greater than the steady state difference, the number of

design cycles shall be determined as the smaller of the number of cycles for the base metal established

using either paragraph 5.5.3 or 5.5.4, and for the weld established in accordance with paragraph 5.5.5.

5.5.1.4 Stresses and strains produced by any load or thermal condition that does not vary during the

cycle need not be considered in a fatigue analysis if the fatigue curves utilized in the evaluation are adjusted

for mean stresses and strains. The design fatigue curves referenced in paragraph 5.5.3 and 5.5.4 are based

on smooth bar test specimens and are adjusted for the maximum possible effect of mean stress and strain;

therefore, an adjustment for mean stress effects is not required. The fatigue curves referenced in paragraph

5.5.5 are based on welded test specimens and include explicit adjustments for thickness and mean stress

effects.

5.5.1.5 Under certain combinations of steady state and cyclic loadings there is a possibility of ratcheting.

A rigorous evaluation of ratcheting normally requires an elastic-plastic analysis of the component; however,

under a limited number of loading conditions, an approximate analysis can be utilized based on the results of

an elastic stress analysis, see paragraph 5.5.6.

5.5.1.6 Protection against ratcheting shall be considered for all operating loads listed in the User’s

Design Specification and shall be performed even if the fatigue screening criteria are satisfied (see paragraph

5.5.2). Protection against ratcheting is satisfied if one of the following three conditions is met:

a) The loading results in only primary stresses without any cyclic secondary stresses.

b) Elastic Stress Analysis Criteria – Protection against ratcheting is demonstrated by satisfying the rules of

paragraph 5.5.6.

c) Elastic-Plastic Stress Analysis Criteria – Protection against ratcheting is demonstrated by satisfying the

rules of paragraph 5.5.7.

5.5.2 Screening Criteria for Fatigue Analysis

5.5.2.1 Overview

a) The provisions of this paragraph can be used to determine if a fatigue analysis is required as part of the

vessel design. The screening options to determine the need for fatigue analysis are described below. If

any one of the screening options is satisfied, then a fatigue analysis is not required as part of the vessel

design.

1) Provisions of paragraph 5.5.2.2, Experience with comparable equipment operating under similar

conditions.

2) Provisions of paragraph 5.5.2.3, Method A based on the materials of construction (limited

applicability), construction details, loading histogram, and smooth bar fatigue curve data.

3) Provisions of paragraph 5.5.2.4, Method B based on the materials of construction (unlimited

applicability), construction details, loading histogram, and smooth bar fatigue curve data.

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b) The fatigue exemption in accordance with this paragraph is performed on a component or part basis.

One component (integral) may be exempt, while another component (non-integral) is not exempt. If any

one component is not exempt, then a fatigue evaluation shall be performed for that component.

c) If the specified number of cycles is greater than

()

, then the screening criteria are not applicable and

a fatigue analysis is required.

5.5.2.2 Fatigue Analysis Screening Based On Experience with Comparable Equipment

If successful experience over a sufficient time frame is obtained with comparable equipment subject to a

similar loading histogram and addressed in the User’s Design Specification (see 2.2.2.1.f), then a fatigue

analysis is not required as part of the vessel design. When evaluating experience with comparable

equipment operating under similar conditions as related to the design and service contemplated, the possible

harmful effects of the following design features shall be evaluated.

a) The use of non-integral construction, such as the use of pad type reinforcements or of fillet welded

attachments, as opposed to integral construction

b) The use of pipe threaded connections, particularly for diameters in excess of 70 mm (2.75 in.)

c) The use of stud bolted attachments

d) The use of partial penetration welds

e) Major thickness changes between adjacent members

f) Attachments and nozzles in the knuckle region of formed heads

5.5.2.3 Fatigue Analysis Screening, Method A

The following procedure can only be used for materials with a specified minimum tensile strength that is less

than or equal to 552 MPa (80,000 psi).

a) STEP 1 – Determine a load history based on the information in the User’s Design Specification. The

load history should include all cyclic operating loads and events that are applied to the component.

b) STEP 2 – Based on the load history in STEP 1, determine the expected (design) number of full-range

pressure cycles including startup and shutdown, and designate this value as

c) STEP 3 – Based on the load history in STEP 1, determine the expected number of operating pressure

cycles in which the range of pressure variation exceeds 20% of the design pressure for integral

construction or 15% of the design pressure for non-integral construction, and designate this value

. Pressure cycles in which the pressure variation does not exceed these percentages of the

design pressure and pressure cycles caused by fluctuations in atmospheric conditions do not need to be

considered in this evaluation.

d) STEP 4 – Based on the load history in STEP 1, determine the effective number of changes in metal

temperature difference between any two adjacent points,

, as defined below, and designate this

value as

. The effective number of such changes is determined by multiplying the number of

changes in metal temperature difference of a certain magnitude by the factor given in Table 5.8, and by

adding the resulting numbers. In calculating the temperature difference between adjacent points,

conductive heat transfer shall be considered only through welded or integral cross sections with no

allowance for conductive heat transfer across un-welded contact surfaces (i.e. vessel shell and

reinforcing pad).

1) For surface temperature differences, points are considered to be adjacent if they are within the

distance

computed as follows: for shells and dished heads in the meridional or circumferential

directions,

2010 SECTION VIII, DIVISION 2

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2.5LRt= (5.16)

and for flat plates,

3.5

(5.17)

2) For through-the-thickness temperature differences, adjacent points are defined as any two points

on a line normal to any surface on the component.

e) STEP 5 – Based on the load history in STEP 1, determine the number of temperature cycles for

components involving welds between materials having different coefficients of thermal expansion that

causes the value of

()

αα

−

Δ to exceed 0.00034, and designate this value as

f) STEP 6 – If the expected number of operating cycles from STEPs 2, 3, 4 and 5 satisfy the criterion in

Table 5.9, then a fatigue analysis is not required as part of the vessel design. If this criterion is not

satisfied, then a fatigue analysis is required as part of the vessel design. Examples of non-integral

attachments are: screwed-on caps, screwed-in plugs, shear ring closures, fillet welded attachments,

and breech lock closures.

5.5.2.4 Fatigue Analysis Screening, Method B

The following procedure can be used for all materials.

a) STEP 1 – Determine a load history based on the information in the User’s Design Specification. The

load histogram should include all significant cyclic operating loads and events that the component will be

subjected. Note, in Equation (5.18), the number of cycles from the applicable design fatigue curve (see

Annex 3.F) evaluated at a stress amplitude of

S is defined as ()

NS . Also in Equations (5.19) through

(5.23), the stress amplitude from the applicable design fatigue curve (see Annex 3.F) evaluated at

cycles is defined as

()

SN.

b) STEP 2 – Determine the fatigue screening criteria factors,

C and

C , based on the type of construction

in accordance with Table 5.10, see paragraph 4.2.5.6.j.

c) STEP 3 – Based on the load histogram in STEP 1, determine the design number of full-range pressure

cycles including startup and shutdown,

. If the following equation is satisfied, proceed to STEP 4;

otherwise, a detailed fatigue analysis of the vessel is required.

()

1FP

NNCS

≤ (5.18)

d) STEP 4 – Based on the load histogram in STEP 1, determine the maximum range of pressure fluctuation

during normal operation, excluding startups and shutdowns,

, and the corresponding number of

significant cycles,

. Significant pressure fluctuation cycles are defined as cycles where the pressure

range exceeds

SS times the design pressure. If the following equation is satisfied, proceed to

STEP 5; otherwise, a detailed fatigue analysis of the vessel is required.

()

⎛⎞

Δ≤

⎜⎟

⎝⎠

(5.19)

e) STEP 5 – Based on the load histogram in STEP 1, determine the maximum temperature difference

between any two adjacent points of the vessel during normal operation, and during startup and

shutdown operation,

TΔ , and the corresponding number of cycles,

. If the following equation is

satisfied, proceed to STEP 6; otherwise, a detailed fatigue analysis of the vessel is required.

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()

aTN

⎛⎞

Δ≤

⎜⎟

⎝⎠

(5.20)

f) STEP 6 – Based on the load histogram in STEP 1, determine the maximum range of temperature

difference fluctuation,

TΔ , between any two adjacent points (see paragraph 5.5.2.3.d) of the vessel

during normal operation, excluding startups and shutdowns, and the corresponding number of significant

cycles,

. Significant temperature difference fluctuation cycles for this STEP are defined as cycles

where the temperature range exceeds

as ym

. If the following equation is satisfied, proceed to

STEP 7; otherwise, a detailed fatigue analysis of the vessel is required.

()

aTR

⎛⎞

Δ≤

⎜⎟

⎝⎠

(5.21)

g) STEP 7 – Based on the load histogram in STEP 1, determine the range of temperature difference

fluctuation between any two adjacent points (see paragraph 5.5.2.3.d) for components fabricated from

different materials of construction during normal operation,

, and the corresponding number of

significant cycles,

. Significant temperature difference fluctuation cycles for this STEP are defined

as cycles where the temperature range exceeds

(

)

11 2 2

as y y

SEE

αα

⎡

⎤

−

⎣

⎦

. If the following equation is

satisfied, proceed to STEP 8; otherwise, a detailed fatigue analysis of the vessel is required.

()

211 22

aTM

CE E

αα

⎛⎞

⎜⎟

Δ≤

⎜⎟

−

⎝⎠

(5.22)

h) STEP 8 – Based on the load histogram in STEP 1, determine the equivalent stress range computed from

the specified full range of mechanical loads, excluding pressure but including piping reactions,

and the corresponding number of significant cycles,

. Significant mechanical load range cycles for

this STEP are defined as cycles where the stress range exceeds

S . If the total specified number of

significant load fluctuations exceeds the maximum number of cycles defined on the applicable fatigue

curve, the

S value corresponding to the maximum number of cycles defined on the fatigue curve shall

be used. If the following equation is satisfied a fatigue analysis is not required; otherwise, a detailed

fatigue analysis of the vessel is required.

()

La S

SSN

Δ≤ (5.23)

5.5.3 Fatigue Assessment – Elastic Stress Analysis and Equivalent Stresses

5.5.3.1 Overview

a) An effective total equivalent stress amplitude is used to evaluate the fatigue damage for results obtained

from a linear elastic stress analysis. The controlling stress for the fatigue evaluation is the effective total

equivalent stress amplitude, defined as one-half of the effective total equivalent stress range

()

PPQF+++ calculated for each cycle in the loading histogram.

b) The primary plus secondary plus peak equivalent stress (see Figure 5.1) is the equivalent stress, derived

from the highest value across the thickness of a section, of the combination of all primary, secondary,

2010 SECTION VIII, DIVISION 2

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and peak stresses produced by specified operating pressures and other mechanical loads and by

general and local thermal effects and including the effects of gross and local structural discontinuities.

Examples of load case combinations for this stress category for typical pressure vessel components are

shown in Table 5.3.

5.5.3.2 Assessment Procedure

The following procedure can be used to evaluate protection against failure due to cyclic loading based on the

effective total equivalent stress amplitude.

a) STEP 1 – Determine a load history based on the information in the User’s Design Specification and the

methods in Annex 5.B. The load history should include all significant operating loads and events that are

applied to the component. If the exact sequence of loads is not known, alternatives should be examined

to establish the most severe fatigue damage, see STEP 6.

b) STEP 2 – For a location in the component subject to a fatigue evaluation, determine the individual

stress-strain cycles using the cycle counting methods in Annex 5.B. Define the total number of cyclic

stress ranges in the histogram as

c) STEP 3 – Determine the equivalent stress range for the

cycle counted in STEP 2.

1) If the effective alternating equivalent stress is computed using Equation (5.30), then determine the

stress tensor at the start and end points (time points

t and

t , respectively) for the

k cycle

counted in STEP 2, Determine the local thermal stress at time points

t and

t ,

mLT

ij k

and

nLT

ij k

respectively, as described in Annex 5.C. The component stress ranges between time points

and

t and the effective equivalent stress ranges for use in Equation (5.30) are calculated using

Equations (5.24) through (5.27).

()()

,,, ,,

mmLTnnLT

ijk ijk ijk ijk ijk

σσσ σσ

Δ= − − −

(5.24)

()

()()

()

0.5

11, 22, 11, 33,

222

22, 33, 12, 13, 23,

kk kk

Pk LTk

kk kkk

σσ σσ

σσ σσσ

⎡⎤

Δ−Δ +Δ−Δ +

⎢⎥

Δ−Δ =

⎢⎥

Δ−Δ +Δ+Δ+Δ

⎣⎦

(5.25)

,,,

LT m LT n LT

ij k ij k ij k

σσ

Δ= − (5.26)

()()()

0.5

22 2

, 11, 22, 11, 33, 22, 33,

LT LT LT LT LT LT

LT k k k k k k k

σσ σσ σσ

⎡⎤

Δ = Δ−Δ +Δ−Δ +Δ−Δ

⎢⎥

⎣⎦

(5.27)

2) If the effective alternating equivalent stress is computed using Equation (5.36), then determine the

stress tensor at the start and end points (time points

t and

t , respectively) for the

k cycle

counted in STEP 2, The component stress ranges between time points

and

, and the

effective equivalent stress range for use in Equation (5.36) are given by Equations (5.28) and (5.29)

, respectively.

,,,

ij k ij k ij k

σσ

Δ= − (5.28)

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