A significant problem in elastic-plastic Design By Analysis is that of defining a “plastic load” to be used as the basis for calculating the allowable static load for the vessel, in the same way that the limit load does in limit analysis. In practice, this is done by applying what is called a criterion of plastic collapse, although the phrase “plastic collapse” is in fact a misnomer, as the purpose of these criteria is to define the load at which plastic deformation becomes excessive, and not when actual physical collapse occurs. Throughout the years a large number of plastic collapse criteria have been proposed in the literature, amongst them are the tangent intersection method, the 1% Plastic strain pressure, the twice elastic slope pressure, the twice elastic deformation pressure, and the 0.2% offset strain pressure. Here it must be said that some common pressure vessel codes have removed these criteria of plastic collapse in their latest revision and replaced them by what are called direct route methods.
Limit-load analysis method
Limit-load analysis method assumes an ideal elastic-perfectly plastic (or rigid-perfectly plastic) material model and small deformation theory. When perfect plasticity and small deformation theory are assumed, the load carrying capacity of the structure is limited by equilibrium considerations.
Initially, the structural response is linear elastic but as yield is exceeded regions of plastic strain develop and the response becomes non-linear. As loading continues, equal increments of load cause increasingly greater plastic deformation. The plastic zone expands to equilibrate the internal and external stresses with the externally applied forces until a stage is reached when no further expansion of plastic zones can occur to accommodate the applied load increase. This is called the limit load.
At the limit load, the load deformation curve becomes horizontal: dP/dd=0. The structure can no longer maintain equilibrium with the external loads and unlimited plastic deformation occurs. The structure fails by loss of equilibrium at the limit load of the structure.
1) The material model is elastic-perfectly plastic with a specified yield strength.
2) The strain-displacement relations are those of small displacement theory.
3) Equilibrium is satisfied in the undeformed configuration.
Real structures, however may behave rather differently to the limit analysis model in two ways: the material may exhibit post-yield strain hardening and also large deformations may occur.
Elastic-plastic analysis method
As strain-hardening materials can support stresses greater than yield, plastic deformation can continue for loads above the theoretical limit load of the structure without violating equilibrium. Changes in structural configuration as loading progresses can also affect the load carrying capacity of the vessel. If large structural deformations occur the structural load-path may change. This can increase or decrease the load carrying capacity of the vessel. The effects of non-linear geometry shall be considered in this 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. 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.
Direct route methods
EN13445/3 Annex B provides direct route, and The Design By Analysis (DBA) route is included in the standard as a complement to the common (and easy) Design By Formulae (DBF) route, for cases not covered by the DBF route, but also as an allowed alternative,
as a complement for cases where superposition (of pressure actions) with environmental actions – wind, snow, earthquake, etc. - is required,
as a complement for fitness-for-purpose cases where (quality related) allowed manufacturing tolerances are exceeded,
as a complement for cases where local authorities require detailed investigations, e. g. in major hazards' situations or for environmental protection reasons.
Within this DBA route, there are two possibilities available:
The so-called Direct Route (DR)
the Stress Categorization Route (SCR)
The second, the SCR, is the one, well-known from many national standards and technical regulations, which requires categorization of stresses, or parts of stresses, into primary, secondary, and peak stresses.
Because of the "familiarity" with this route, it is included in this standard as well, despite its also well-known drawbacks and problems – the problems associated with non-uniqueness of the choice of stress classification lines, and the problems associated with the categorization, the non- uniqueness of the determination of primary stresses . This approach, derived for assessing the results from thin shell theory, cannot easily be applied to results from 3-D (continuum) Finite Element Analyses, but it requires only linear-elastic analyses, with the advantages of uniqueness in the determination of stress results and the possibility of (linear) superposition of these results for different actions.
ASME III Appendix F – A Valuable Guide to the Operability Assessment of Piping Systems
The NRC Inspection Manual Chapter 0326 refers to ASME III Appendix F as an acceptable method for the evaluation of “a degradation or nonconformance associated with piping or pipe supports …”. Appendix F provides five alternative methods for the qualification of pressure equipment, piping, and their supports. They are: (1) elastic analysis, (2) plastic analysis, (3) limit collapse analysis, (4) plastic collapse analysis, and (5) plastic instability analysis. Each of the five methods provides a different way of approaching the evaluation, with criteria that are specifically matched to the method. In this manner Appendix F reduces the conservatism inherent to the design analysis methods for normal operating conditions.
The Level D Service Limits and design rules contained in Appendix F are intended (F‑1200) to prevent the rupture of the pressure‐retaining boundary, but are not intended to assure operability of components during or following the specified event.
Following is a brief description of each of the five Appendix F methods, and how to implement them in practice. A comprehensive evaluation will consider all five methods and determine which criterion is the limiting condition. A more detailed coverage of operability analysis and the use of Appendix F is provided by George Antaki in his training course on this subject.
Implementation Overview
These methods are best performed using finite element analysis. First, you should review the capabilities of the software to determine if it supports the features and material models required to perform these analyses. Some software may require the explicit inclusion or activation of nonlinear geometric effects in the solution, where the solution step is updated based on the deformed geometry. This is likely to be trivial for the elastic case, but is important for all cases with plasticity as the deformations may be significant.
Appendix F does not specify the source for the plastic stress‐strain curve. One good source is ASME Section VIII, Division 2, Annex 3‐D.3, which provides equations to develop the curves for commonly used materials. Extra caution should be applied to avoid mixing engineering stress and true stress without appropriate translation. Note that the stress‑strain curves input into the FEA software are likely to be true stress‑strain, and either the results or the plastic evaluation criterion of Appendix F must be adjusted accordingly.
Apply the load in small increments so that the effects of increasing the load may be seen. The shape of the stress‑strain response and displacement‑vs‑load curves provide valuable insight into the behavior and failure modes of the system.
All elements of the system must be considered for evaluation of stresses, etc. However, experienced analysts can accurately predict where the limiting conditions may be found, and can focus their results extraction efforts at those locations. It may be necessary to apply stress intensification factors (SIFs) to piping components, or the software may evaluate the ovalization of piping directly.
The elastic analysis method is described in Appendix F § F‑1330. This method is the simplest and can be performed using hand calculations or almostany FEA software. The criteria for the elastic method are of a form similar to those used in design analyses, and are summarized as:
Pm < 70% SU
Pm + Pb < 105% SU
t < 42% SU
This is the only method where linear scaling or extrapolation of a known load can be applied. Note that the elastic method does not address buckling or other large deformation failure modes.
The limit analysis method is described in ASME III Div. I Subsection NB § NB‑3213.27. It considers the material to behave in an elastic-perfectly plastic manner. This method determines the load at which a plastic hinge occurs, and is well suited for analysis of compressive loads, or bending of pipe elbows and non‑compact beams. The allowable load is limited to 90% of the collapse load.
The material properties must specify the tangent modulus in addition to the Young’s modulus. For FEA software that support bilinear material property curves, the first entry is Young’s modulus, and the second entry is zero. A zero tangent modulus is perfectly plastic – the strain will increase with load but the stress will not (i.e. no strain hardening occurs). Obviously, the software must support plasticity ‑ some simpler analysis programs only support linear elastic analysis.
Collapse is shown by runaway displacement (NB‑3213.28) followed by solution non-convergence. The displacement over time should be reviewed to confirm that non-convergence does in fact occur due to collapse and not a numerical error in the model. Finding the collapse load may take some iteration to determine precisely. Instead of incrementing up the load, it may be most efficient to start by intentionally overshooting the limit, then observe the load at the time when the solution fails, and narrow in from there.
The plastic analysis methods are described in Appendix F § F‑1340 and ASME III Div. I Subsection NB § NB‑3213.24 thru NB‑3213.26. The plastic analysis methods all require strain hardening material properties. There are three sets of plastic analysis criteria.
The first criterion (F‑1341.2) is simply labeled 'plastic analysis' and may be summarized as:
Pmax < 90% SU
Pm < 70% SU
t < 42% SU
Note that the maximum stress criteria Pmax has a higher limit than the elastic method, which is enabled by using a more sophisticated analysis technique.
The second criterion (F‑1341.3 and NB‑3213.24) is labeled plastic collapse, and it can be described as the load causing deformation equal to twice the deformation at the onset of yield, which is equivalent to the load at the time the stress‑strain response curve intersects with a line having half the slope of Young’s modulus.
The third criterion (F‑1341.4) is labeled plastic instability, and it consists in finding the load at 70% of the maximum load supported by the system.
All three methods of plastic analysis can be performed with one run of the FEA model. You would run the model until all of the plastic analysis criteria are met or exceeded, which will be the instability condition (beyond which the analysis cannot continue to solve). The allowable load is the load applied at the time (i.e. solution substep) when a given criterion is reached.