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ENGINEERING SOFTWAREPressure Vessel
Design and AnalVsis
Seminar Notes
Table of Contents
Table ofContents
Chapter
1:
II/trodl/ctioll to the Semil/a/'
&
the Sofhl'are
Purpose of the Seminar
1
Structure of the Seminar
1
Seminar Da)' I
/
Semillar Da)'
2
2
Seminar Da)'
3
2
Overall Notes
2
About the Software
2
CodeCalc: The PVElite Component Anal)'sis Pmgram
2
Features
2
SUlJlmalY ojApplications
3
Chapter 2: Ol'erl'iew ofthe ASME Code
History of the Code
1
Organization of the Code
2
Scope and Limitations of the Code
3
Allowable Tensile Stress per the Code
4
Internal pressure
011shells and heads
5
C)'lindCl's
5
Spheres, Elliptical Heads, Torispherieal Heads
7
Important Terms for analyzing cylinders and heads
8
Geometry for Pressure Vessel Heads
8
Elliptical Heads
8
Hemispherical Heads
9
Geometry for Pressure Vessel Heads
10
Torispherical Heads
/0
Chapter
3: Usil/g the Program-The 1I1ail/ Mel/II
File Menu
1
New
2
Open
2
Save
2
Save As
3
Prillt
3
Prilll Prel';ew
3
Prilll Setup
J
Exit
3
Previous FOlll' Files
3
Edit Menu
4
Title Page
4
Project Data
4
Insert New Item
4
Delete
Current Item
4
Se/ecl All
4
Dese/ecl All
4
Analyze Menu
5
Browse
5
Analyze Selected Items
5
Analyze Current Componenl
5
SlImmll1Y
5
Choose Analysis Type
5
Output Menu
6
Tools Menu
7
Configuratioll Options
7
Comput3tion Control Tab 7
Miscellaneous Options 9
Set Unit
9
Make UI/il File
10
Calculator
I
J
Edit/Add Materials Dialog
JJ
Diagnostics Menu
13
CRC Check
/3
Build Version Check
J3
DLL Versio/1 Check
13
View Menu
14
ESL Menu
15
Phone Updmc
J5
GClIemle Fax
Codes
J
5ReceiJ'c lind Enler Fax Codes
/5
View ESL In/ormation
J5
Help Menu
16
Camel/IS
J
6Tip
of
IheDa)'
16
Illfo
16
Chapter
4:
Example Problem l-A Simple Dl'lIm
Problem
1
Specifications
Brittle Fracture - Minimum Design Metal Temperature
10
External Pressure on shells aud heads
21
Stiffening
27
What do
)'011need to kllow 10 analyze cylinders alld heads for external
pressure?
28
External Pressure OUU1 28
Diameter 28
Actual (or assumed) Thickness 29
Design Length for the Vessel or Vessel Segment 29
Width and Thickness of Reinforcing Rings 29
Nozzle Reinforcement and Failure Path Calculations
36
Hillside and Off-Angle Nozzle Angles
45
What do you need
10
know
/0pelform
nozzle reinforcement
calClllatiolls?
50
Required Thickness of Head or Shell and N07..z1e
50
Geometry ofNol.7.le and Shell 50
Diameter Limit, Thickness Limit 51
Is the Nozzle
illa Seam? 51
Details of Nozzle Welds 51
Largc Nozzle Considerations 51
Mallway or Access Opening 51
Chapter
5:
Cones and Conical Sections
Guidelines for Cones
I
Typical Geometry for a Simple Cone
2
What do
yOllneed
(0know to perform cone calculations?
5
Dimensions of/he COile am/the Cylinders at Either End
5
Dimensions
o/TrallsifiollKlluckles
ar
allY exist)
5
HalfApex Angle of
fheCOliC
5
Axial Forces
011'he COile
5
Width alld 11/ickncss o.rCone Reinforcement
5
Chapter
6:
Welt/ed Flat Heads
Guidelines for Welded Flal Heads
1
Whal do you need to know to analyze welded nat heads?
4
Af/achme,,' Dctails
4
Required lIlId AClllal Thickness o/Ihe Shelf
4
Large ami Small Dimensions for the Head
4
Chapter
7:
Half-Pipe Jackets
Guidelines for Half-Pipe Jackets
Flange Design and Analysis
7
Gaskets
7
Gasket Materials and Gasket Factors 8
Other Gasket Types 12
Facing Sketches 12
Flange Types 13
Flange Behavior 16
Flange Stresses
20
Stress Analysis
20
Blind Flanges and Channel Covers
38
Large Central Openings
46
Chapter
8:
Floating Heads ami Spherically Dished Covers
Types of Spherically Dished Covers
1
Description
1
Exmnple
2
Chapter
9:
Heat Exchallger Tubesheets
TEMA Tubesheets
1
ASME Tubesheets
17
Chapter 10: Expallsioll Joillts
Flanged and Flued Expansion loints
1
Prc~surc
Vessel Design and Analysis Seminar Component Design Problem
5
Metal Bellows Expansion Joints
16
Pressure Vessel Design and Analysis Seminar Cornponcllt Design Problem
19
Chapter
11:
Stresses
Stresses in Shells due to Loads on Attachments
Discussion of Results
3
WRC 107 Stress Calculations
3
Why
are the Stresses
alEdge of the Pad the Same as at the Edge of the NOlzle?
3
What arc the Allowable Stresses? 4
IYRe/O?
Stress
SUlIlmatiollS5
ASME Section VIII Division2-Elaslic Analysis a/Nozzle
6
Stresses in Horizontal Pressure Vessels
20
Chapter
12:
Tall Vertical Towers
Allowable Stresses on Tall Towers
1
Analyzing Tall Vertical Process Towers
2
Design Procedure
3
Wind Load Computations
3
Wind Pressl/re Complllation
4
Earthquake Load Computation
5
Skirt and BaseRing Design
11
Basering Thickness Calculations
11
Thickness
of Baseringllnder Tension 14
Thickness
of TopRingunder Tension 14
Basering Design Selections
15
Calculation of Required Area for Each Bolt
15
Selection
of tileBolt Size 15
Selection of Preliminary l3asering Gcometly 15 Analysis of Preliminary Uasering Geometry 15 Sclection of Final Bascring Gcomctry
15
Analysis of Uasering Thickncsses16
Skirt 11lickness Calculations
/6
13asic Skirt Thickness
16
Stress in Ski'1 due to Gussets or Top Ring
16
Chapter
13:
Vessel Legs, Support Lugs, and Lifting Lugs
Vessel Legs
I
Support Lugs
3
Lining Lugs
4
Bibliogmphy
Pressure Vessel Design and Analysis - Seminar Notes
Chapter 1: Introduction to the
Seminar
&
the Software
PURPOSE OF THE SEMINAR
Weleome to COADE's Pressure Vessel Design and Analysis Seminar. The purpose of this
course is to help you become comfortable with the guidelines for designing and analyzing
pressure vessels, and to make you more effective at your job by introducing you to
com-puterized design tools for pressure vessels-the CodeCale program and the PVElile
pro-gram.
The intent of this course is
IlQ1
to have you memorize the exael rules of the ASME Code
for pressure vessel design. Instead, we want you to become morc familiar with the ASME
Code, be able to find what you need to know in it. "'nd above all be able to spot unrealistic
results or questionable designs, whether gcncrated by you, by a computer. or by some
other engineer. In a nutshell, we want to teach you what you need to know to successfully
apply the ASME Code to pressure vessel design and analysis.
STRUCTURE OF THE SEMINAR
Our approach to this goal will be to look at pressure vessels on a component by component
basis. In other words, we will study separately each of the many pressure vessel
compo-nents-sheils, heads, nozzles, flanges,
tubesheets, etc. This approach is widely practiced
by engineers as they design or analyze pressure vessels.
It
also allows us to start with
rela-tively simple components and progress to more complicated ones. Most
of the
lecturcs in
the course will have the following fonnat:
Introduction to the theory of analysis for a particular component.
Detailed review of ASME Code rules associated with a particular component.
Design of the component using the CodeCale or PVElile programs.
Seminar Day 1
The first area to cover includes the history nnd structure
of the
ASME Code, calculation of
nllowable stresses using Code rules, and review of the scope of vessels covered by the
Code.
This section
of the
seminar also inCludes a discussion
of the
design of some of the most
basic components of pressure vessels: shells, heads, and nozzles. We will begin with rules
for internal pressure design of shells and heads, along with associated mles for weld
effi-ciency and brittle fracture. We will also learn how to use the
CodeC~lcprogram,
espe-cially the SHELL program for internal pressllre analysis.
Abollt the Software
Pressure Vessel Design and Analysis· Semin<tr Notes
We will then stndy the mles for external pressnre design of shells and heads. If time
per-mits we will also study nozzle reinforcement and the design of
Oal
head and conical
sec-tions. This will complete our study of components typically associated with drums.
Seminar Day 2
On day two we will study components associated with heat
exch~lI1gers.\\le
will
extell-sively study flanges and bolted flanged connections such as those in TEMA channel
cov-ers, ASM E blind flanges, and floating heads ofheat exchangers. We will look at
tubeshccts, including floaling, stationary, and fixed tubesheet designs, as well as metal
bellows expansion joints and flanged and nued expansion joints, commonly lIsed in heat
exchangers to absorb differential thermal stress.
Seminar Day 3
On day three we will focus on tall vertical pressure vessels and vessel supports. We will
review the loadings on tall vessels, such as wind and earthquake. We will also review the
design of vessel skirts and base rings, horizontal vessels on saddle supports, and legs or
support lugs which arc commonly used for smaller yessels and exchangers. We will also
study yessel-shell stresses that arc caused by loads on attachmcnts, including nozzles and
support lugs.
Overall Notes
This notebook is arranged to allow yOll to work step-by-step through the course, and to
work example problems of each type of calculatiou. Plenty of space has been left to take
additional notes.
We want to encourage you to ask questions and make comments during the course so that
we can cover the material you 1110st want to learn. A three day course is really
100short to
fully explore both the theoretical and the practical aspects of the ASME Code, but we do
want to cover as much of these topics as possible. Your input will make this easier and
more effective.
ABOUT THE SOFTWARE
CodeCalc: The PVElile Component Analysis Program
The CodeCale program is a package of seyenleen applications for the design and analysis
of pressure vessels and heat exchangers. The purpose of the program is to provide the
mechanical engineer with easy
10use, technically sound, well documented calculations
that will speed and simplify the task ofyessel design or re-rating.
Calculations in the CodeCalc program are based on the latest editions of national codes
such as the ASME Boiler and Pressure Vessel Code, or industry standards such as the Zick
method of analysis for horizontal drums. The CocicCalc program offers exceptional case
of usc, which results in dramatic improvement in efficiency for both design and re-rating.
One expert estimates that the time he needs
(0rcrate an exchanger has been reduced from
eight hours to two hours.
Features
The following arc features of the CorieCalc/PVElile program:
Pressure Vessel Design and Analysis. Seminar Notes
Abollt the SoOwarc
Thc Windows cnvironmcnt provides cxtcnsive on-line help at a keystrokc, and
man-ages multiple analysis files so that thc
USCI'CHn define a whole pressure vcssel in a
sin-gle file.
The
USCI'Cfln define his own unit systcm, opening CodeCfllc
10thc world of metric
and
Sf
calculations. Internally, however, calculations continuc to be in the English
sys-tcm of units, assuring continued compliance with ASME Code requirements.
The CodeC"le progmm has " complete m"teri"llibmry including over 2000 t"bles of
allowable stress versus temperature and 49 external pressure charts.
The CodcCalc program also includes a component library which contains diameter
and wall thickness for all standard pipc sizes, pressure vs. temperature charts for
ANSI B 16.5 nanges, "nd section properties for AISC beam sections.
A sUlllmary capabi lity allows evaluation of all the components of a pressure vessel or
hcat exchanger. Design pressure, temperature, material, and Maximuill Allowable
Working Pressure are shown for each component.
Printed output from the CodcCalc program is exceptionally clear and complcte, with
user definable headings on each pagc. User comments and additions Illay bc inserted
at any point in the output. The ability to save any analysis to disk m<lkes it easy to
keep records and do revisions.
High quality documentation with complete operating instmctions, tlltorifll, and many
example problems makes the CodeC"1c program suitable for both beginners and
experts.
Summary of Applications
The following applie"tions are avail"ble in the CodeC"le Program:
SHELL-lntern"1 and external pressure design of vessels and exeh"ngers using the
ASME Code, Section VIII, Division I mles. Components include cylinders,
coni-cal sections, ellipticoni-cal heads, tori sphericoni-cal heads, nat heads, and spheric"1 shells
and heads. This program calculates required thickncss and maximum allowable
intern<ll prcssure for thc given componcnt.
It
also calculates the minimum design
metal temperature per UCS-66, and evaluates stiffening rings for external pressure
design.
NOZZLE-Required w"1I thickness and reinforcement under internal pressure for
nozzles in shells and heads, using the ASME Code, Section VIII, Division I mles
and including tables of outside diameter and wall thickness for all nominal pipe
diameters and schcdulcs. The program also calculates the strength of
reinforce-mcnt and evaluates failure paths for the nozzle.
CONICAL-lnternal and external pressure analysis of conical sections and stiffening
rings using the ASME Code, Section VIII, Division I mles. Complete are" of
reinforcement and moment of inertia calculations for the cone under both internal
<lnd cxternal pressure are included.
HALFPIPE-Intcrnal pressure design for vessels with split pipc type j"eketing. The
program calculates the required thickness of the vessel wall as well as the required
thickness of the halfpipej"ekel. l3ased on ASME, Section VIII, Division I,
Appendix EE.
FLOHEAD-Jntern"1 "nd exten,"1 pressure "nalysis of bolted dished heads (/loating
heads) using the ASME Code, Scetion VIII, Division I mles. An "dditional
About the Sofiwarc
1-4
Pressure Vessel Design and Analysis - Seminar Notes
lations technique allowed by the Code (Soehren's ealeulation) is also
imple-mented by this program.
FLANGE-Stress analysis and geometry selection for all types of flanges using Ihe
ASME Code, Section VIII, Division I mles. This program bOlh designs and
ana-lyzes the following types of flanges:
Weld neck flanges and all integral flange types
Slip on flanges and all loose flange Iypes with hubs
Ring type flanges and all loose flange types without hubs
Blind flanges, both circular and
non~circlliarTEMA channel covers
Reverse geometry weld neck flanges
Flat faced flanges with full face gaskets
LGCENTER-Stress analysis for flat heads with a large, central circular opening
based on ASME, Section VIII, Division I, Appendix 14. The program calculates
the stresses at both the OD of the head and the location of the opening.
TUI3SHT-Analysis of aillypes of lubesheets using Ihe Seventh Edition of the
Stan-dards of the Tubular Exchanger Manufaelurers Association. The program takes
full account of the effects of tubesheets extended as flanges, and'for fixed
lubesheets also includes the effects of differentialthemlal expansion and the
pres-ence of an expansion joint.
ASMETUI3E-Analysis of several types of tubesheets using the mles from Appendix
AA of the ASME Code, Section VlIl, Division I. This appendix provides
alter-nate mles for tubesheet design, and may result in thinner tubesheets than the
TEMA program.
HORIZVES-Slress analysis of horizontal dmms on saddle supports using the
method of L.P. Ziek. Results include stresses at the saddles, the midpoint of the
vessel, and in Ihe heads. Stiffening rings used inlhe design of the vessel arc also
evaluated.
LEG&LUG-Analysis of vessel support legs, support lugs, and lifling lugs. This
anal-ysis is based on industry standard calculation techniques, and the resulting
stresses are compared to the AISC Handbook of Steel Construction or the ASME
Code. A full table of AlSC beams, channels and angles is included in the program.
PIPE&PAD-Required wall thickness and maximum allowable working pressure for
two pipes, and branch reinforcement rcquirements for the same two pipes
consid-ered as a branch and a header. I3ased on ANSI 1331.3 mles, this program includes
tables
of outside
diamcter and wall thickness for all nominal pipe diameters and
schedules.
WRC 107-Stresses in cylindrical or spherical shells due to loading on an attachment,
using the method of P.P. I3ijlaard as defined in Welding Research Council Bulletin
107.
I3ASERING-Thickness calculations and design for annular plate base rings, lop
rings, bolting, and gussets. Thesc calculations are performed using industry
stan-(!cud
calculation techniques.
Pressure Vesscl Dcsign and Analysis - Seminar Notes
About the Sofiware
THINJNT-Calculates stress in a metal bellows expansion joint of the type typically
used in piping and heat exchangers. The program does elastic stress analysis for
stresses due to internal pressure and opening or closing
of the
joint, and calculates
the cycle life of the joint based on the ASME Code, Section VIII, Division I,
Appendix BB.
THICKJNT-Calculates stresses in a heat exchanger
expansion joint
fabricated from
relatively thick plate, also called flanged and filled expansion joints, using the
mles of the TEMA Seventh Edition, Paragraph RCB-8. The analysis is based on
the equivalent geometry used in "Expansion Joints for Heat Exchangers" by S.
Kopp and M.
f.
Sayre, with slight modifications.
RECTVES-Perfonns stress calculations and Maximum Allowable Working Pressure
calculations for the rectangular, obround, and circular vessels described in the
ASM E Code, Section VIII, Division I, Appends 13. The calculations arc taken
from Sections 13-6 through 13-13.
SUMMARY-Description and evalnation of all the components ofa pressure vessel
or heat exchanger. Design pressure, temperature, material, actual thickness, and
Maximum Allowable Working Pressure are shown for each component.
About the Software
1-6
Pressure Vessel Design and Analysis - Seminar Notes
Pressure Vessel Design and AllCllysis - SeminClr Notes
Chapter 2: Overview
of the
ASME
Code
HISTORY OF THE CODE
The Boiler Codc has becn in existence for almost 90 years.
During the 1800's there wcre numerous catastrophic failures of prcssure vessels and
boil-ers, resulting in thousands of deaths.
Public and professional concern resulted in the release of the first mles for power boilers
in 1915.
The first pressure vessel Code was issued by the ASME in 1925.
In 1968 the Code was divided into two subsections:
Section VIII, Division
1 -
Rules for Constmction of Pressure Vessels.
Section VIII, Division
2 -
Alternative Rules for Pressure Vessels.
The main differences between Division
1
and Division
2
are
Division
2
has higher allowable stresses in most cases - resulting in thinner vessels.
Division
2
also has more sophisticated design requirements, requiring more extensive
stress analysis than is used in Division
J.
Division
2
frequcntly requires a fatigue analysis.
Division
2
frequently requires more extensive inspection and record keeping than
Division
In 1992, the Code moved the allowable stress tables and external prcssure charts for
mate-rials from Section VIII, Division
1
to Section
II,
Part
D.
This new publication contains
all
of the material data from previous editions of Section Vlll, Division I, plus a few new
ref-erence tables from other sections.
Division 3, whieh is a new division intended fOf high prcssufe vessels, has been in
prepa-ration for sevcral years, and is now issued.
Section VIII, Division I is by far the most widely used of the two current divisions.
Almost all the pressure vessels constmeted in the U.S. are constmcted to Division 1.
In this course, unless specifically noted otherwise, "The Code
llis Section
VIII,
Division
I.
ASME approves Code Case 2290 which increases Division I allowable stresses.
Organization of the Code
ORGANIZATION OF THE CODE
Pressure Vessel Design and Analysis - Seminar Notes
2-2
The Code is divided into three Subseelions, pins Mandatory Appendices and
NOl1Jnanda-tory appendices
Thc three subsections cover
A -
General Requiremcnts
B - Requirements Pertaining to Methods of Fabrication of Pressure Vessels
Part UW - Requirements for Pressure Vessels rabricated by Welding
Pari ur - Requirements for Pressure Vessels rabricaled by rorging
Part UB - Requiremenls for Pressure Vessels rabricated by Brazing.
C -
Rcquircmcnts Pertaining to Classes of Materials
Part UCS - Carbon and Low Alloy Steels
Part UNr - Nonferrous Materials
Part UCI - Cast lron
Part UCL - Clad and Lined Vessels
Part UCD - Cast Ductile Iron
Part UHT - Heal trealed ferritie steels
ParI ULW - Layered Construclion
Part ULT - Materials with higher allowable stresses at low temperature
Mandatory appendices cover snbjects nol covered in the main body of the Code. The
requirements of these appendices are mandatory when the subject covered is appropriate
10
the eonslmction oflhe vessel.
Nonmandatory appendices provide information and suggest good practices relative to
prcssure vessel construction. They also scrve as a place where
new
design rules 3rc
intro-duced and tested before moving into the mandatory requirements.
Pressure Vessel Design and Analysis - Seminar Notes
SCOPE AND LIMITATIONS OF THE CODE
Scope and Limitations
of the
Code
Section VIII, Division I applies to all pressurized containers, but with Ilumerous
excep-tions. Some
of the
exceptions listed in paragraph U-I include
Vessels within the scope of other sections (i.e. power boilers).
Fired process tubular heaters (furnaces)
Pressure containers that arc part ora machine (i.e. pumps)
Piping or piping components
Pressurized water storage up to 300 psi
Ilea ted water storage up to 210°F
Vessels with design pressure 15 psi or less
Vessels with a maximum cross section dimension 6 in. or less
Vessels for Human Occupancy
Division I rules are applicable to vessels not exceeding 3000 psi design pressure. You can
usc Division I above 3000 psi, but special precautions to avoid fatigue and other additions
to the mles are recommended.
The scope of Division I includes the nozzles and attachments to the vessel.
Unfired steam boilers may be constmeted to Division 1 or Section
I.
Some classes, such
as evaporators or vessels in chemical plants fife required to meet Division I.
SOIIle small vessels are exempt from inspection:
Up to 5 cubic feet at 250 psi
Up to 1.5 cubic feet at 600 psi
ANY Vessel that meets ali the requirements of Division I may be stamped with a U stamp
even though exempted by one of the above limitations.
Allowable Tensile Stress per the Code
Pressure Vessel Design anu Analysis - Seminar Notes
ALLOWABLE TENSILE STRESS PER THE CODE
Division I mles arc based on a maximum principle stress failurc theory. While not very
accuratc, this thcory is simple to understand and apply.
By way of contrast, Division 2 is based on a maximum shear stress theory, which is more
accuratc. Somc other Codcs are based on the even more accurate theory of maximum
dis-tortion encrgy (Von mises stress).
The allowable tensile strcss for materials in Division I is the minimnm of the following
stresses:
1/3.5 ofthc specified minimum tensile strength at ambient temperature
1/3.5 of the tensile strength at the design temperature
2/3 of the specified minimum yield strength at ambient temperature
2/3 of the yield strength at the design temperature
100% of the average stress to produce a creep rate of 1% in 10,000 hours.
67% of the average stress to produce rupture in 100,000 hours.
80% of the minimum stress to produce rupture in 100,000 hours.
In 1999, the ASME changed the 1/4 to 1/3.5.
In the temperature range in which tensile strength or yield strength set the allowable
stresses, higher allowable stresses arc permitted for austenitic stainless steels and
nickel-alloy materials where greater defomlation is not objectionable. In this case the critcrion of
2/3 yield strength at temperature may bc increased to 90%
of yield
strength at temperature.
Bolting materials whose strength has been enhanced by heat treating or strain hardening
are limited to 1/5 of tensile and 1/4 of yield.
Pressure Vessel Design
<llldAnalysis
~Seminar Notes
Internal pressure on shells <Iud heads
INTERNAL PRESSURE ON SHELLS AND HEADS
Cylinders
Theoretical derivation
of stress
for thin walled cylinder:
Hoop Strcss: (circumferential)
Force
~PXD;XL
A
reo
=
2
X / XL
Force
I'D;
I'D;
- -
~-
orl
Area
21
2S
Axial Stress: (longitudinal)
(D)2
Force
=P
x n x
-i
Area
=n x
D;
Xt
Force
Area
I'D;
or
14/
I'D;
4S
For thick-walled cylinders the theoretical stress is expressed by the Lame equations. The
formulation
of the
Lame equations is as follows, for internal pressure only. The maximum
stress at the ID surface is:
Hoop
Rodial
~-I'
ASME has a slight variation on the first formula, making it fit fairly closely the rcsult of
thc sccond fommla:
PR
SE - 0.61'
The
aD
basis form
of the
samc equation is:
SE
+
0041'
The ID and OD formulas do not yicld exactly thc same results: for relatively thick walled
cylinders, the effect can bc noticeable.
The following graph shows the relative accuracy of these three formulas. The Lame
equa-tion is exact for all geometries. Thc simple approximaequa-tion becomes pretty bad for
Internal pressure
011shells and heads
Pressure Vessel Design and Analysis - Seminar Notcs
walled cylilHJers. The ASME equation is much closer to the exact solution than the simple
approximation.
2M 10"0to
T-~"
"'"
"...,
-~
-
--
-
--
EO.ls"9l--
EQ(8.1 ~ ~--
EO.(s.l) .10 1.0 ,.5 2.0 2"S 3.0 35 4.02-6
"~
"
figure'.6 Compori.onol fom,vlai !ofO<x>pIl'mlr.0 cy!i,*kolVotl ••
The Joint Efficicncy in this (and all othcr) ASME Code formulas is a measure of the
inspeclion quality on Ihe weld seam. In general, weld seams that receive full radiography
have a joint efficicney of 1.0. Weld scams that receive spot radiography have a joint
effi-ciency of 0.85. Weld seams that receive no radiography have a joint effieffi-ciency of 0.7.
Seamless components have a joint efficiency of 1.0.
In addition to the basic mles described above, the Code requires that no two seams in the
same vessel differ in joint efficiency by more than one category of radiography. For
exam-ple, ifcireumferential seams receive no radiography (E=0.7) then longitudinal scams have
a maximum E of 0.85, even if they receive full radiography. The practical outworking of
this is that circumferential seams, which are usually less highly stressed, may be spot
radiographed (E=0.85) while longitudinal seams arc fully radiographed. This provides the
sallle metal thickness at some savings in inspection costs.
Pressure Vessel Design and Analysis - Seminar Notes
Splleres, Elliptical I-leads, Torispherical Heads
SPHERES, ELLIPTICAL HEADS, TORISPHERICAL HEADS
Cylinder
Elliptical Hcad
Spherical Head
Torispherical Head
In
Basis
~p(D12
+
CAl
SE- 0.61'
~
p[K(D
+
CAl]
2S£ - 0.21'
(
DI2
+
CA)
f
~
l'
2S£-0.2P
f
~
p[M(L
+
CAl]
2SE-0.lp
00 Basis
l'
(D/2)
SE
+
0041'
f -1'[
KD
]
2SE+2p(K-OI)
~
1'(
D/2
)
2SE+ 0.81'
1'[
ML
]
I
~
2SE+ 0.785P(M -
02)
OD
Basis
Pa
~
SE(f-ea)
[D/2-0A(I-ca)]
Cylinder
Elliptical
Spherical
Pa
Pa
Pa
In
Basis
SE(I - ea)
[(D/2
+
ea)
+
0.6(1 -
ea)]
2SE(I - ea)
[K(D
+
2ea)
+
0.2(1 - ea)]
SE(I-ea)
(DI2
+
ea)
+
0.2(1 - ea)]
Pa
Pa
2SE(I- cal
[KD-2(1
+
ea)(K -
0.1)1
SE(I - ea)
[D12 -
0.8(1 -
ea)]
Torispherical
Pa
~
SE(I-ea)
Pa
[M(D
+
ea)
+
0.1 (1-
ea)]
SE(t-ea)
[(MD -
(I -
ea))(K -
0.2))
The fonnulas for elliptical and torispherical heads are general. The factors
M
and
K
are
semi-empirical adaptations of more complicated shell theories.
K
and
M
have the
follow-ing fommlas:
Where h
~depth of head
L
~crown radius
r
~knuckle radius
For the special case of a
2: I
elliptical head,
K~1.For the special case of a nanged
&
dished (6%) torispherieal head, M
~0.885 and the
inside crown radius equals thc outside diameter of the vcssel.
The shape of elliptical and torispherieal heads produces compressive stresses at the
knuck-les.
ror thin torispherical heads the eqliatiol1 in Division I is unconscrvativc-dimpling can
occur even in vesscls that meet the Code requircments. Division 2 contains a more
compli-cated equation that should be checked when the value of
rlt
is large.
Important
Terms
for
analyzing cylinders and heads
Pressure Vessel Design and Analysis - Seminar Notes
IMPORTANT TERMS FOR ANALYZING CYLINDERS AND HEADS
ALLOWABLE STRESS-Sclect the allowable slrcss from the appropriatc Code table
at thc design temperature.
JOINT Erf'ICIENCY-Sclcct Ihejoinl cfficiency from lable UW-12
DIAMETER (INSIDE OR OUTSIDE)-ID formulas are found in paragraphs UG-27
and UG-32 00 formulas arc found in Appendix I
CORROSION ALLOWANCE-Subtractthc corrosion allowance from the actual
thickncss, and [liso increase the inside diamcter to account for corrosion.
ACTUAL THICKNESS
ANDIOR
DESIGN PRESSURE-You can calculate
maxi-mum allowable working pressure
if you
know the thickness
of the
component.
Otherwisc, use the design pressure to calculate the required componcnt thickness.
ASPECT RATIO f'OR ELLIPTICAL HEADS-This is typically 2:1, but may range
from I: I to 3: I
CROWN RADIUS AND KNUCKLE RADIUS FOR TORISPHER1CAL
HEADS-The ratio ofcTOwn radius to knuckle radius may not bc less than 1 nor grcater than
16.66
GEOMETRY FOR PRESSURE VESSEL HEADS
Elliptical
Heads
Major
A~is(Head Diameter)
Minor
Axis
(1/2)
Head Diameler
2-8
(Aspect mtio
=
ratio of major nxis to minor axis, Iypically 2.0)
Pressure Vcssel Design ;:md Analysis - Seminar Notes
Hemispherical Heads
Geomctry for Pressure Vessel lIeads
/
,I
!
I
I
I
Overview
of the
ASME Code
---/""""""---
-'-'~-... / """"
\.
\
\
\
- -
HCild Di;nnctcr
--~
---,I
Geomelry ror Pressure Vesscilleads
Pressure Vessel Design and Analysis - Seminar Notes
GEOMETRY FOR PRESSURE VESSEL HEADS
Torispherical Heads
-r---'"
I
....,...--...
II
).
KNUCKLE
IIEAO DIAMETER _/ / \ RADIUS Ir)
I
/
I
I
_I
til
[$1
q
I
"I
"'/
i!
",/
vi
I
I
/
I
I
!
IThe typical torispherieal head, also known as Flanged
&
Dished, has a crown radius equal
to the outside diameter of the cylinder, and a knuckle radius equal to six percent of the
cyl-inder diameter.
Pressure Vessel Design and Analysis - Seminar Notes
Chapter 3:
Using the
Program-The Main Menu
CodcCalc always starts with the Vessel Data Input Screen. Across the top of this screen is
a line of itcms that is called the Main Menu. The Main Menu controls the major fUllctiolls
of the program. \Ve will review the functions available in each of these menu items.
The items in the Main Menu - file, Edit, Analyze, Output, Tools, Diagnostics, View, ESL,
and Help - may be selected with a mouse click or by pressing the underlined character
while pressing the Ait key. for example, the Output processor may be selected by pressing
the Ait and 0 keys simultaneously.
First, we will begin by going over each of the Main Menu items.
FILE MENU
The File Menu controls the general operations of CodeCalc files. Options that are
dis-played in the menu with an ellipsis ( ... ) cause a file manage window to appear when
selected.
Figure
1--
The File Menu
File Menu
New
Pressure Vessel Design and Analysis
~Scminar Noles
Starts a new file.
[jo t~1I4<. {1-,.,J 1""" ObT-rJir..1~L '/>e.. lI,t> .' •
oc&
"fa
I
+9At~
,( 1.<~1·m8=IlD ri-&'ff
.ftOEHDr=
($lUI H H (])I:ll
n O l O SJo"f, ..dllo<o.... ~1r..."...,.1 ",).J"~ ;·,.;...Ii!'.';OJ:", J ~'·"i";··"-"'l~·,r•. ~ 'I "';'L"'-"~,f".:-""..".", ~ ,~ ,-(,·r.r~;
-,P"",
~, r,r"';.··;···'ll.·r"~~!.·_'L ~ i'~ h. n~=-",-·.,·.
~ rn.J':-~:to."'·i~It--;""~, ~ :'I:rl.i:r) ....~"'''"," J.;!!_...r: ----L....JOpen
Figure 2--File New
Save
3-2
Opens a previously created file. When the Open option is chosen, the user is prompted to
select an existing job file. Files ortype '.ee; will be displayed for selection.
~ ?X
Figure 3--0pen Dialog
Saves the current file in its present condition.
Pressure Vessel Design and Analysis - Seminar
Nolcs
Save As
file
MCIIUSaves a file that has not been previously namcd or saves the current file under another
namc.
fW·i
::!:lY.o~_11,cd ~R(le1'tl'~{CCi I~ASIIE_T...t.!hffi-CCI:=l
Shls C(I , t:JChed,lCcl :=1[~T{"~CO I ~('/<<'l_O,b,C(l ~t.lMJ~ccci r,.[':Ir~, S•.-e<D!>plI: ICOOU:ALCFlesl'.cci)it
Figure 4--Save As Dialog
Sends the current vcsscl graphic image directly to a postscript or laser jet printer.
Print Preview
Displays the page that will be sent to the printer (sec above).
Print Setup
Brings up the standard Windows printer setup screen,
Exit
Exits CodeCalc. A message window will appear to give the user a last opportunity to save
any modifications to the current job.
Previous Four Files
The File Menn also lists the last fOUf vessel inpullilcs accessed from your computer. Any
of these liles may be opened with a mouse click.
Edit
Menu
EDIT MENU
Pressure Vessel Design and Analysis - Seminar Notes
3-4
Once a filc is selectcd, the Edit Mcnu indicates the options available for ediling.
A3Irujll'.I."juOnli,Nj
1.i,.l.tmiif.!:·1.it1,3i
.!~ ~r!;.~.O{
11!1~,('"{. l{lnbeo:
I[IOOI
Oew'f.olT.nd.s.heaStc6:.'l:I:"'ISPH=rR"'iC.'''"l"''''''''''';'-Oe:P;nlr~Plenuo:
pooocoo,~
Db.-v.I~~~...~lo;JllrRaoJlPleu...,": J1OO0C0J
Figure
5--
Tile Edit Menu
Title Page
Allows the user to enler report titles for this group of rep orIs.
Project Data
Allows the user to enler up to 3 Ii tie lines, which appear at Ihe lop of each page of the
prillted reports.
Insert New Item
Inserts a new element after the current element.
Delete Current Item
Deletes the current clement.
Select All
Selects all of the items in the browse window.
Deselect All
Deselects all of the items in the browse window.
Pressure Vessel Design
illHJAnalysis - Seminar NOles
ANALYZE MENU
Analyze Menu
The Analyze options cause the program to quit the input process and enter the analysis
process. CodeCalc will first save the current job to the input file with the same filename;
Ihcn il will process the analysis.
Browse
Allows the seleclion of certain components in Ihe input lile to be analyzed.
Analyze Selected Items
Performs calculations for selecled analysis Iypes. The calculations will be saved in a
binary file and will be ready for display or printing.
Analyze Current Component
Performs calculations for the current analysis type. The analysis program looks for
appro-priate data in the current analysis file and performs calculations, saving the results in
a text
file. The results oflhc analysis will then be ready for display or printing.
Summary
Looks through all the data in the current analysis file and prepare
a brief summary of cach
analysis.
Choose Analysis Type
Selects Ihe Iype of componenl you wish to work on.
Figure 5--Choose Analysis Type Menu
The analysis types chosen from this menu can also be selected from Ihe Analysis Tool Bar
by simply clicking on the icon.
Figure
7--
The Analysis Types Toolbar
Output MCllu
OUTPUT MENU
Pressurc Vessel Design and Analysis - Scminar Notes
3-6
The Output Menu allows the user to review the analysis results and print (hc graphics of
the vessel. The following option is available under Output:Review - allows the user to
review the analysis results
of the
clIrrcJ1tjob,
if
those
results are available.
Il8fIU~:~ _ _
f
OUC1f,6orld~t.eISedi:tl: ISPH£RlCAlliEAO
Figure 8--Ti,e Output Menu
Using the
Program~The Main Menu
}-Pressure Vessel Design and Analysis - Seminar Noles
TOOLS MENU
Tools Menu
The Tools Menu controls the utility processors
as
summarized
here. Configuration - This
option allows the user to dcfine a variety of system variables for the program. The first
screen
of the Configuration mcnu looks like this:
!
pic5lHljlf.lllliS
1i0!!!ij4B
H.'i'iMl.•f1r1.i!'.
33.
1 . ,De £.li. hWfli .D~1m
O~lb:.I i,SL ~~ .u~~!
0 cHi
I
e;J,'
-f:
1-
'(0:(9'1"L -',:]-1Il1l3
ill
,
1
1
~U~
!~
Of 3~heh" "'~Ur.·
...
•
. t~ ,t
O~
I
~WTd",1
ILU/JJ"1iMD.o'l: ££IM1H~,
} D~W~cl~t.o,IS·~; ISpm_flI0lH~AOFigure
9--
Tile Tools Menu
Configuration Options
Computation Control Tab
The Computation Control Tab in thc Configuration dialog leis some specific program
computation control parameters be set. These controls Icl you set some options in some
programs that
control the results of some computations.
Figure
1
a--Configuration Options
Following is a description of the options:
Computc Increascd Nozzle Thickness? In many cases pressure vessels are designed
and built long before the piping system is attached to them, This means that the nozzle
loadings are unknown. lfthis field is checked, thcn your minimum nozzlc thickness (tm)
will be the maximum of
trn
=
(.134,trn for internal pressure) less than or equal Nps 18
Irn
=
(DD/ISO,trn for internal pressure) greater than Nps 18
By
using such a requirement in addition
10UG-45,
the piping dcsigners will have some
additional metal to work with to satisfy thermal bending stresscs in systems these vessels
are designed
for.
Tools Menu
Pressure Vessel Design and Analysis· Seminar Notes
Note
These fonnulae are not in the ASME Code. They are used in industry.
You can also specify the minimum wa)) thickness of the nozzle (Tm) in the Nozzle input.
If you do so, that will override this calculation.
Calculate F iu Flohead if the Pressure is Zero? In the design of noating heads, a
factor
F
is computed. The factor
F
is a direct function of the internal pressure. If the
inter-nal pressure is 0, then F is equal to 0. However, some interpret the Code to mean that F
should always be computed regardless of which case we arc analyzing. Typically, the case
in question is the flange bolt-up case. When the uni' is being bolted up, it has
110internal
pressure. That is why the defanlt is not checked.
(fyou wish F to always be considered in the thickness cales, then check this box. This is
the conservative method of calculation.
Use P iustead ofMAWP for UG-99B? The Code paragraph UG-99(b) discusses the
subject of hydrostatic test pressure on vessels. The equation that wonld nonnally be used
is as follows:
Test Pressure
=
1.3' MAWP • StestfSdesign
The code in note 34 states that the MAWP may be assumed to be the same as the design
pressure when calculations arc not made to delcnnine the MAWP.
This will allow for lower test pressures. This directive should be used with caution.
Perform Area Calculatious for Small Nozzles? The Code paragraph UG-36
dis-cusses the requirement of performing aTea placement calculations when srnall nozzles arc
involved. The Code States
Openings in vessels not subject to rapid fluctuations in pressure do not require
reinforcement other than that inherent in the constmetion under the following
con-ditions:
3.5-in. finished opening in a shell or head .375 in. thick or less
2.375-in. finished opening in a shell or head greater than .375 in.
If your geometry meets this criteria and this box is nol checked, then no area of
reinforce-ment calculations will be perfonned.
Priut Water Volume
jn
Gallons? Normally the volumes computed by the program
arc in diameter units.
]fyou want to use US gallons instead of cubic diameter units, check this directive.
Other-wise, the program will use cubic units as the default value.
Use Calculated Value of M for Torispherical Heads in UG-45 bI? The Code in
paragraph UG-45 requires a calculation of the required head thickness at the location of
the nozzle. This may lead one to believe that the thickness Inay be computed per
para-graph UG-37. However a recent code interpretation states that the thickness should be
computed by the mles of paragraph UG-32 or by the rules in Appendix I.
Thus, this directive should always be checked.
The second screen of the Configuration Menu looks like this:
Pressure Vessel Design and Analysis - Seminar Notes
Tools Menu
Miscellaneous Options
The Miscellaneous Options
of the
Configuration MCllulets the user select some
miscella-Ileous directives. These directives control some printout style options and others.
?Ixl
•~[>1Jom3!,,·rlWr.RCNn1
nA~~fio~rl~?"-Oda<.iUr.sfle Kr.;lllhll
iJ1
"-Figure 11--Miscellaneous Options
Following is a description of the options:
Report Content. This directive allows thc uscr to change the length of the printcd
reports. When the summary option is checked. the formulas and substitutions will not be
printed out. Thus, this option will generate less paper and more compact reports.
Whcn thc dctailcd option is chccked, the reports will be the normallcngth.
External Printont in Rows? There are two choices for thc style of printing extemal
pressure results: rows and columns. Printing the values by row tends to reduce the length
of the printouts. This is the default.
If you wish to print by column, do not check this directive.
Set Unit
This option allows the user to change the current job's units system. Once this option is
selected, a File Open dialog will appear and allow the user to select a new units file. Thcsc
Tools Menu
Pressure Vessel Design and Analysis· Seminar Notes
units files have the extension ,fil. English, Metric and SJ units are available in the system
subdirectory. After you select a units file, the following window will appear:
!
~,lllJfe
"SystemUnl' Ctml.v. utt.Unl·II~
.S~UIi
Coi'<rt¥l. .UlerlW •I~
'lmtth' led"It
_
'~f
J"'-
n~Oenr~ ~
1n:7cuft,"Jl~r
Ihled'!..
f
!
f«oe pw>dt. 1IJ.
~ .WrdSpeed ..~ _'~t...
lt:"Mf
it
H311(~)~
-"11
~.
In-.d
"at;oWeO:;Hb/sq~
_'11~·~-=-}-.IblJqll.11
Mil • rq~ '1I:=i~~ ~ h ..l····~~lnu4
...1
it ...
"""""" .
r=-l}
~
...
~<
.
r;---:J1.1rl1
I~Slim
•
bthqn •~l ~''WmLoad
brJfql\.'P"'7l;-IP'f
_11'
~ T~~
,.;,., d<gtt,F •~
rr::::;:-j ,"'...
'ttl . 'rr-lj-
~I
(Preuue 'p$iQ ...
~ ~
VclnoO utt:i'doe.l' I • }.,lIn,'t
i
£.MocUn!»-'sqn'"
~.·l~1,
Oi.YMer Wes 'f l i t..
~,~ P~O~If)t
bl./N-n,·n-J.c;.'~~W6lTt~U r~.1
.·'--~l.~t
~
ImlkiJonOM~/t'Ufl
.r:-l
1.. b./cull~.
lr::=!Ci
"
Figure 12..Unil Window
If the units selection is acceptable, press the OK bullon; otherwise, press Cancel. When
OK is selected, the current units will be overlayed with the selected units.
Make Unit File
This option allows the creation of a cuslom units file. Simply pull down the appropriate
conversion constant or label and the corresponding unit or label will change accordingly.
If your conversion constant is not one ofthe choices, type in the label and constant for
your particular unit. (The program will continue to use English units internally).
Figure 13..Make Unit Dialog
This window presents a table of items, the internal units used for each item, a conversion
factor, and the user lin its. The conversion factor is used to obtain the user units from the
internal units. The lip and down arrow keys can be used to move lhe selection to the
desired item. If a desired unit conversion is not available as a default program selection, it
can be entered manually by typing it in. Ensure that your conversion constants arc correct
and that your labels go with the constants. Once all units have been set, press OK to exit
Pressure Vessel Design ;lnd Analysis - Seminar Notes
Toob Menu
this screen and save the new units file. A safe place to save it would be in the system
sub-directory where Ihe supplied units files arc stored.
After you have saved the new units file, you will need to overlay the current units in your
job file with Ihe new units. This option is Ihe Set Unit option. After you sel your file with
the new units, all of the entered data will be converted into the new set of units
immedi-alely.
Calculator
This option allows the user to perform simple calculations and paste the results in the input
field in which the cursor resides.
.
Figure 14--The Calculator Option
You can use the calculator to compute a number and transfer that number into CodeCalc
by using the Edil, Copy fealure. From the desired field, right click and choose the Paste
option. Before pasting, ensure that the field's current contents have been removed.
Import Nozzle Dala - Imports nozzle information from a PVElilc inpul file (.pvi) for
use in the WRC 107 Module.
Edit!Add Materials - This opliou allows the user to add materials
10
Ihe COADE
Material dalabase. The screen appears as follows:
Edit/Add Materials Dialog
To use this processor, fill in all of the values in all cells. If more than one material is to be
entered, usc the Next button to enter the new material. After all materials have been
Tools Mellu
3-t2
Pressure Vessel Design and Analysis - Seminar Notes
entered, save the file with the Save button. Finally, press the Merge key to join the
user-defined material database with the supplied material database.
xl
Figure 15--Ma/erial Editor
Using the Program- The Main Menu
•
"
Pressurc Vessel Design ;lIId Analysis. Scminar Noles
DIAGNOSTICS MENU
The Diagnostics Menu helps to troubleshoot problem installations.
e'''''j...
·''iliji'.I:!liWj4
f.!"l.!M\i¥
fI"i,I,,_,!
Dillgnostics Menu
CRC
Check
IlemUI.ITbl:'f:~
!
Dtw'~"ShelSedl«ljSFH[Rl~HEAD
Figure 16--Diagnoslics Menu
)
Performs a cyelic redundancy check (CRC) on each of the supplied CodeCale files.
Build
Version Check
Checks the revision level of the CodeCalc executablc files.
DLL
Version Check
Checks to make sure thc CodcCale .DLL files are currcnl.
Note
If the DLLs are not current, the program may behave in an unusual manner or may
not mn
at
all.
View Menu
VIEW MENU
Pressure Vessel Design and Analysis. Seminar Notes
The View Menu allows the user to specify the tool bars to be displayed.
.
~
.,
Figure 17--The View Menu
The following options are available:
File Toolb.r
Figure 18--File Toolbar
Analysis Toolbar
Figure 19--Analysis Toolbar
Status Bar
)
3-14
-
~-Figure 20--8ta/us Bar (a/ the bottom of/he screen)
Using the Program- The Main Menu
; ;
Pressure Vessel Design lind Analysis - Seminar Notes
ESL MENU
E51
Menu
The ESL Menu provides utilities lhal interact with the Extenlal SoOw",e Lock (ESL).
e ..
U1J....\IlIju.':M,'lj.J.!1
1.!@4f.!li',.HI"",--,:::;->q~p:~=--.:::=:::;,~
y_l:itb
'''''--l''h?MUpd~e
1-'---.:....=-,'----.:....--'---4l
1i~alfIFa:<Co.:le-\~'B~~[rtl'"h;cCode:l
~["lr/"'tM!Ul
Figure 21--ESL Menu
Phone Update
Allows update authorization information or other ESL changes to be obtained over the
phone.
Generate Fax Codes
Provides the uscr with access codes for rcmote ESL updating. These access codes should
be sent to COADE for authorization codes.
Receive and Enter Fax Codes
Allows yOll to enter the remole authorization codes you receivcd from COADE. Each set
of four codes will make one change to the data stored on your ESL.
View ESL Information
Displays the data stored on the ESL.
Ilclp Menu
HELP MENU
Pressure Vessel Design and Antilysis· Seminar Noles
f'lB,
01 3 _ Sho!tuO'HkadlD~;"IG_I
3-16
The Ilelp Menu displays on-line Help and infonnation on how to obtain technical support
for CodeCale.
I I • I
~
. tcir
lY",*e QoJpA.IIX4 Obt;Jl~l- ~SlY-1m1
1 .'6
~.
IiH/'f
1
+ ... _"
I
~
A.-MUf.!
pC
t<w";'~_
·1 Ti?cJIt.eOillY_.r
Irlo~_~
f!:l:nJ.axiECAl.C_=;'m~]~:jQ~otr<~n~_~';""~'~' ~j,
H=t:{urbtf:11-00').)
...
oiI.Figure 22--Help Menu
Contents
Starts the Help facility.
Tip of the Day
Provides tips for running CodeCale.
Info
Provides information on the best ways to contact COADE personnel for teclmical support,
and provides a link to COADE's website.
Pressure Vcssel Design and Analysis - Scmin:lr NOlcs
Chapter 4:
Example Problem
1-A Simple Drum
PROBLEM
The drawing on the following page shows a simple horizontal pressure vessel that we will
use for our first example problem. In this case the preliminary sizing of the vessel and its
attachments has been completed, and we are asked I) to select thicknesses for the pressure
components, nozzles, and reinforcemcnt, and
2)
to check the vessel for stresses when it is
full of liquid.
SPECIFICATIONS
Design conditions, as shown on the drawing, arc
230
psig
(1.586
N/1l1l11
2
)
ii;ternal pressure
and fnll vacuum at 450°F (232°C). Materials arc carbon stecl, SA-516, 70, Nonnalized.
The vessel is subject to full radiography, and has a 1/8-in. (3.175 mm) corrosion
allow-ance.
The length of the vessel is 244 in. (6198 mm) between langent lines (the heads have a 2-in.
(51 mm) straight flange, making the weld-to-weld length of the vessel 240 in. (6096 mm)).
We will require the following programs in this analysis:
Internal pressure on shells and heads - SHELL program,
External pressure on shells and heads - SHELL program.
Nozzle thickness and reinforcement - NOZZLE program.
Follow these steps to complete this first example problem:
I.
Analyze the cylindrical shell under internal pressure, and pick a design thickness for
it.
Next analyze the 2:
I
elliptical head, using the same basic thickness.
2.
Analyze the cylinder under full vacuum conditions. Also,. analyze the heads for
exter-nal pressure.
3.
Analyze the nozzle reinforcement using the NOZZLE program. Select appropriate
reinforcing pads for each nozzle.
4.
After the entire vessel has been analyzed using CodeCale, model the same vessel
under PYElite and review the results.
i
144.0'10=
F
9~
J
_ _ _ _ _---i
0
I _ .• REINFORCING nn,..c:ni
l U ~~ ... II'o'I<.l'C NOZZLE SCH!:DULEOTY. SIZE AND SCHED. TYPE RTG.
120.0' RF
388:
,
..
..
MK. :l N1,
N~ 192"230 PSIG & Full Vacuum Design Temperature: 450 F
0101 hp Knockout Drum
