Fatigue Life Evaluation of Coke Drum.pdf
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Fatigue Life Evaluation of Coke Drum Support Skirt / Shell Junction Using Transient Thermal Stress Analysis
HOT- BOX & WELD BUILD-UP
Note: The enclosed general information is for reference only. The details of project specific calculations will be provided “later”
FOSTER WHEELER USA CORP. 2020 DAIRY ASHFORD, HOUSTON, TEXAS 77077
May 22, 2007
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1.0 INTRODUCTION
1.1 SCOPE
An analytical study is performed to estimate the fatigue life of support skirt to
shell junction for Coke drums based on transient thermal / mechanical stress
calculations and using finite element analysis method. The fatigue life is
estimated based on the actual operating skin temperature.
This engineering analysis also provides specific recommendations to optimize
specific process and operating parameters so that the life of skirt / shell junction
can be extended and fatigue damage reduced.
Although high stresses and cracking happen in nearly all coke drums due to
thermal cyclic fatigue, the damage can be minimized by controlling operating and
process parameters.
1.2 BACKGROUND
Coke drums undergo severe thermal and pressure cycling on a daily basis due to
alternative pre-heating, filling with coke, quenching and decoking operation. This
cyclic mode of operation results in significant thermal stresses at the support skirt
attachment to the drum.
Transient temperature gradients and stress reversals are developed in the skirt
during the cyclic cooling and heating process leading to thermal fatigue failure. If
the temperature ramps during quench and / or preheat / switch to coking cycles
are severe, it will create high thermal fatigue stresses resulting in premature skirt
junction cracking.
It should be noted that the ASME code fatigue data for welded vessel uses a
factor of safety of 2 on stress and 20 on cycles.
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1.3 ASSUMPTIONS
The effect of the following parameters is not included in the analysis:
- Stress concentrations unintentionally introduced during fabrication
- Weld metal physical properties same as the base metal properties.
- Occasional operating “upsets” and wind loads are ignored.
- Only the effect of thermal, pressure and weight loads are included.
- Fatigue strength reduction factor (FSRF) of weld between the skirt and
drum at inner crotch is assumed to be equal to 1.0. FSRF depends on
the weld type and inspection level. For some coke drums, FSRF = 2.0
are required. This will lower the fatigue life.
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2.0 RECOMMENDATIONS TO INCREASE COKE DRUM FATIGUE LIFE
Using transient thermal data of actual operating condition, the results of transient
thermal stress analysis based on finite element techniques provide an insight into
specific operating / process factors which have significant impact on fatigue life
of skirt / shell junction.
The analysis results provide the operator with optimum transients and control
parameters to improve the fatigue life of skirt / shell junction as noted below.
- Extended pre-heat and higher temperature after pre-heat has significant
positive effect on skirt junction fatigue life.
- Maximize the duration of switch to coke to minimize the temperature ramp.
- Faster quench rate has significant negative impact on skirt junction fatigue
life.
Note that there is a temperature gradient reversal in going from quench to
preheating / switch cycle due to transient cooling / heating sequence. This causes
a stress reversal and therefore higher stress range which leads to lower fatigue
life.
By combining transient thermal / stress analysis results and recommended process
parameters, the reliability of the existing coke drum operation can be improved.
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3.0 Transient Thermal Data during Coking Cycle
The transient skin temperature data for coke drum is taken from FW data base of
operating unit and summarized below. Thermal ramps during quenching and
preheating / switch to coking cycle are noted in the following tabulation:
(The following data was used for transient thermal stress analysis)
Operating Event
Time
(min)
Operating temp
Temperature Rate of temp
change,
(0F / min)
# Description Duration 0C
0F
1
Quench # 1:
- Steam to
Fractionator
- Steam to
Blowdown
2
Quench # 2
Quenching and
Filling
3 Drain, Drill,
Reheat, Test
Does not govern thermal stress or fatigue life.
4 Preheating /
Switch to Coke
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4.0 FATIGUE LIFE EVALUATION USING TRANSIENT THERMAL
ANALYSIS
Coke drums undergo severe thermal and pressure cycling on a daily basis when
subject to alternative pre-heating, filling up with coke, quenching and then
decoking operation. This cyclic mode of operation results in significant thermal
stresses at the support skirt attachment to the drum.
Temperature gradients are developed along the skirt during steady state and
transient thermal conditions inside the coke drum. Higher thermal gradient will
lead to higher thermal stresses and lower fatigue life. Transient temperature
gradients developed during the cyclic quenching and heating process are reverse
in nature and therefore cause reversal in bending stresses imposed on skirt.
In general, the magnitude of thermal stresses induced due to thermal condition of
coke drum during quenching and preheating / switch to coking are much higher
compared to steady state thermal condition.
Therefore, the fatigue evaluation of coke drum is governed by thermal transient
analysis. It is determined that the weld between the skirt and shell at the inner
crotch is subjected to highest bending stress reversal due to alternate cooling and
heating.
Stress reversal effect is considered to determine the stress range and to evaluate
fatigue life.
Finite element analysis is used to evaluate the thermal and stress profiles for the
transient conditions. Thermal cycle includes transient cooling condition and
transient heating condition.
A 2-D axi-symmetric FEA model is used for thermal and stress evaluation. The
FEA model also includes insulation, fireproofing and “hot box” area. Two models
are created for each design, namely, a thermal model and a stress model. In the
thermal model a determination is made of the transient temperature gradients in
the skirt during the heat up and quench cycle.
The temperature gradients from thermal model is then exported to the Stress
model to determine thermal stresses. Three cases are considered in the stress
model: 1) the thermal case alone, for heat up and quench conditions; 2) an internal
pressure case acting with dead and live loads in the drum and 3) the combined
thermal, internal pressure plus dead and weight loads during the heat up and
quench part of the coking cycle.
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Upon determination of the maximum stresses for both transient conditions, the
stress reversal effect is considered to determine the full stress range and to
evaluate fatigue life.
The allowable criteria for the evaluation of fatigue due to peak stress is twice the
stress amplitude using fatigue curves from ASME Section VIII, Division 2,
Appendix V.
The results of this thermal / mechanical stress analysis are used to perform fatigue
evaluation at critical locations.
Load Cases and Load Combination
For thermal / mechanical stress analysis, following load cases are analyzed:
- Thermal gradient only
- (Pressure + Weight)
- (Thermal Gradient + Pressure + Weight)
CRITICAL LOCATIONS FOR FATIGUE LIFE EVALUATION
Finite element analysis results identify the following the critical location for
fatigue life evaluation:
- Weld between Skirt and Knuckle @ inner crotch (see FEA plot)
In order to comply with the requirements of Appendix – 5, principal stresses are
calculated using FEA stress results, followed by maximum stress intensity and
alternating stress amplitude, Salt, calculations. Salt is adjusted for fatigue strength
reduction factor and for modulus of elasticity at maximum metal temperature.
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5.0 FEA MODEL AND BOUNDARY CONDITIONS
A 2-D axi-symmetric finite element model is constructed using ALGOR software.
The FEA model also includes insulation, fireproofing and “hot box” area (see
FEA plot Figure # 1 and 2).
The FEA model includes sufficient length of shell so that the fixed end boundary
condition at the skirt base plate does not effect the results at skirt / shell junction.
The geometry, Process and mechanical design conditions noted on design and
vendor drawing of Coke drum are used in FEA model.
The stress model consists of the same components, geometry and elements as the
thermal model. The nodal temperatures calculated in thermal model are
transferred to stress model to calculate thermal gradient stresses.
The skin temperature measured by TI’s on shell during current operation
immediately above the lower tangent line or estimated skin temperature for
“future” case is applied to the internal metal surfaces.
Forced heat transfer film co-efficient, h is applied to the outside surface and “hot-
box” enclosure. Hot-box is modeled to include the radiant heat effect using body-
to-body option in ALGOR. The thermal conductivity, K, specific heat, Cp, and
mass density of all components are input in the transient thermal model.
Two models are created for each design, namely, a thermal model and a stress
model. In the thermal model a determination is made of the transient temperature
gradients in the skirt during the heat up and quench cycle. The stress analysis
resulting in maximum stress intensity is determined using thermal profiles at
various time steps iteratively. The weld at inner crotch between skirt and shell is
determined to be the highest stressed location.
For stress model, the pressure loads are applied as surface loads on the inside of
the shell, knuckle and cone. Note that the pressure load also includes the
additional effect of static head due to content inside coke drum. End loads are
applied as equivalent pressure load to account for internal pressure effect and
weight loading acting at the end of shell.
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