Table Of Content-
-
Second Edition
Victor Helguero M.
Piping Stress
Handbook
Second Edition
Piping Stress
Handbook
Gulf Publishing Company
Book Division
Houston, London, Paris, Tokyo
Piping
Second
Library of
ISBN G87201_?03-6
Copyright @ 19_86 by Gulf publishing Company, Housron, Texas. All
ngfts reserved. printed in the United Stabs;f A;dca- itis book;;
p-ar,b ttrepf. may not be regoduced io a"y fo.rn *itt out perJsio'i
of the publisher.
$BN GE720r-nB{
. .:: -i.j. . -- ,,
Contents
vlll
Preface
Chapter 1
Basic Theory of Pipe Stress and ANSI/ASME Codes 831.1, 831.3'
. ... ..
831.4, and 831.8 Ptpe Stress Compliances . . . . . 1
Pipe Stress Theory. Expansion Stresses. Cold Springing. ANSI 831.1 Fower
Piping Code Stress Compliances (1983). ANSI 831.3 Chemical Plant and Pe-
troleum Refinery Piping Code Stress Compliances (1984). ANSI B31.4 Liq-
uid Fetroleum Transportation Piping Code Stress Compliances. DOT/B31.8
Gas Transmission and Distribution Piping Systems Stress Compliances. Stan-
dard Oudine for ANSI B3l Codes.
Chapter 2
Expansion ,........17
Coefficients of Thermal
Tables. Example Problem.
Chapter 3
Allowable Stress Range for ANSI/ASME Power Piping Code 831.1
. .....
(1e83) 38
Tables.
Chapter 4
Allowable Stress Range for ANSI/ASME Petroleum Piping
Code 831.3 (19M) . . ... ....73
Thbles.
Chapter 5
Stress Intensification and Flexibility Factors tlz
Definitions. Thbles.
Chapter 6
Rotational Nozzle Flexibilities for Cylindrical Vessels . ......l?a
Thbles.
Chapter 7
hessure and Shess Ratioo . .......177
Thbles. Instructions and Examples. Branch Reinforcement. Sample Calcula_
tions for Branch Reinforcement.
Chapter 8
Ihsign Criteria for Allowable loads, Moment, and Stresses ........257
Design Criteria for Pumps with Steel Nozzles anit Casings. Design Criteria for
Pumps with Cast Iron or Aluminum Nozzles and Casings. Design Criteria ior
Tirbine Drivers wilh Steel Nozzles and Casings. Design Criteria for Thrbine
Drivers with Cast Iron or Aluminum Nozdes and Casings. Design Criteria for
Compressors with Steel Nozzles and Casings. Design Criteria for Cornpres_
sors with Cast Iron or Aluminum Nozzles and Casings. ApI Code 661 Design
Criteria for Air-Cooled Heat Exchansers.
Chapter 9
Simptified Solutions for Pipe Stress 265
Example Problem 9-1. Thbles. Example Problem 9-2.
Chapter 10
PropertiesofPipe
.........292
Definitions. Thbles.
Chapter 11
Components
Weight and Dimensions of Pipe and . . . 299
Weight of Pipe and Components. Tables.
Chapter 12
Thbles ...... ...
Allowable Pipe Span Formulas and 314
Pipe-Span Stress Limits. Pipe-Span Deflection Limits. Piping Wind Loads.
Chapter 13
Pipe Support Selection and Design . . , . . . , . 34
Pipe Supports. Spring Supports. Insulated Pipe Supports and Anchors for
Cryogenic Service. Thbles.
Chapter 14
ExpansionJoints. ........351
Fundamentalsof
Types of Joint Movements. Nomenclature and Symbols. Types of Expansion
Joints. Anchors, Guides, and Supports. Forces and Moments' Cold Springing
of Expansion Joints. Cycle Life Expectancy. Corrosion. Erosion. Calculating
Thermal Expansion. Precompression. Application, Pipe Guides and Guiding.
Iocation of Expansion Joints. End Connections. Covers. Sleeves.
Glossary ..... ....
368
. .,..373
Index
vtl
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thermal expansion coefficients. spring hangers and expan- Calk. for their assisrance in preparing this handbooki and
slon Jotnt selectlon, and piping wind loads. the American Society of Mechanical Ensineers which
generously permitted the author to use sevlral eouations
This reference book provides formulas, technical data. to develop tabulations contained in this handbook.
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petrochemical industry who often has difficulry co ecting ciated. They will contribute to the further improvement of
the required data and solutions to complete a piping stresi this reference handbook.
Victor Helguero M. , PE.
viii
Basic Theory of Pipe Stress and ANSI/ASME
Codes 831..1, 831.3, 83L.4, and 831.8
Pipe Stress Compliances
Pipe Stress Theory The bending stress due to temperature, weight of pipe,
contents, insulation, snow and ice, wind or earthquake is
calculated by the following equatron:
To understand the basic criteria of the ANSI+ pressure
piping code, it will be useful to explain the way different :
t, Vqgrr'lt*+l
stresses develop when a piping element is subjected to a
number of loading conditions. There are four main Z
l-
stresses that affe.t a piping element, as shown in Figure :
1. The following gives the intensity of these stresses and where S5 : Bending stress
the manner in which they may be combined: Ii In-plane stress intensification factor
L = Out-of-plane stress
intensif ication factor
* For reasons of space these codes will be designated ANSI codes Mi : In-plane moment, lb-in.
riroughout the text of the book, Some readers may be mor€ familiar M" : Out-of-plane moment, lb-in.
with the desisnation ANSI/ASME as indicated in the headings. :
Z Section modulus of pipe, in.3
The direct longitudinal stress due to t€mperature and
weisht is calculated as follows:
:
lJ\J" where A Metal pipe cross-sectional area, in.z
. :
s Fu Direct force, lb
t \o The longitudinal stress due to internal pressure is calcu-
lated as follows:
S, I
^PD
"P
4t'
Sr = Longitudinal stress and the sum of three where P = Internal pressure
component parts (see Equation 1-1). D = Outside diameter of pipe
Sc = Circumlerential stress
(see Chapter 10)
S, = Radial stress :
Pipe wall thickness
Ss = Shear stless
(see Chapter 10)
:
Figure 1-1. Stress-free-body diagram. S: 0 (shear)
2
Piping Stress Handbook
Both significant stresses act in the same direction; The preceding method is known as the maximum shear
therefore the stresses are "additive," i.e. theory (Iresca) and is the preferred method of the ANSI
: Code. A second method, known as the distortion-energy
S1 S6+\+Sa (1-l) theory (Von Mises), also provides good results but is not
Nofe: Inngitudinal stresses due to temperature are ex- used by the Code:
cluded from the combination when doing code calcula-
tions.
STTT$"
"'3S-+J--T-+
Circumferential stress, S., is primarily due to internal
pressufe:
S-^2:.tq,D
Radial.stress, S., is primarily due to internal pressue, Expansion Stresses
which is equal to P.
S.=P
The ANSI pressure piping code recognizes that stress
due to thermal expansion tends to diminish with time as a
Shear sfiess, S", is the sum of two component parts: tor- result of local yielding or creep. This reduction of stress
tional stress and direct shear stress (the second stress is will appear as a stress of opposite sign in the cold condi-
usually negligible). (This condition occurs in three-di- tion. This phenomenon is known as self springing. Cold
mensional piping systems.) springing is similar, and although the hot stresses tend to
diminish with time, the sum of the hot and cold stresses
ss: nT +2.0& for any one cycle will remain practically constant.. This
A sum is called the stress range, ard, the code for pressure
piping defines this allowable expansion stress range estab-
where SS: Shear stress
T: lished for thermal expansion in terms of hot and cold tabu-
Torque, lb-in.
F,: lar S values as:
Resultant shear force
z: Cross-sectional area of pipe S. : F (1.25 S" + 0.25 Sh)
Section modulus of pipe
sr:
T/22, tortional stress where S, = Allowable expansion stress range (see
Chapters 3 and 4)
While the ANSI pressure piping code considers stresses S" : Allowable stress for the cold condition
due to therrnal expansion separately from primary stresses (see Chapters 3 and 4)
due to pressure, weight, and external loadi_ngs,/it is obvi- :
Sr, Allowable stress for the hot condition (see
ous that when combined stresses formulas and a specific
Chapters 3 and 4)
yield criterion existr/stresses from all loadings should be F :
Stress range reduction factor for the cyclic
included to delermine the principal stresses before con-
condition
firming them. Resultant principal stresses at the outside
fiber are as follows:
Sr = l/2 + S. +..//4St+ (S'=TFf
[Sr
Tbtal No. of Cycles
:
. sz |2 [g + s" - "v4trTre-.l]zr Over Expected Life
7,000 and less 1.0
Ib calculate the principal stresses use 51 or 52, whichever 14,000 and less 0.9
is greater, or the following equation: 22,000 and less 0.8
45,000 and less o.7
100,000 and less 0.6
\4*
+ C;=TJ' (r-2) 250,000 and less 0.5
