PRESSURE VESSEL HANDBOOK
PRESSURE VESSEL HANDBOOK Twelfth Edition
with foreword by
Paul Buthod Professor of Chemical Engineering University of Tulsa Tulsa, Oklahoma
Eugene F. Megyesy
PRESSURE VESSEL PUBLISHING, INC. P.O. Box 35365· Tulsa, Oklahoma 74153
Copyright © by Eugene F. Megyesy Copyright 1972, 1973 by Pressure Vessel Handbook Publishing, Inc. All rights reserved. No part of this book may be reproduced in any form or by any means including information storage and retrieval systems - without permission of the publisher. Library of Congress Control Number: 2001130059 ISBN 0-914458-21-3 COPYRIGHT© 1972,1973,1974,1975,1977,1979,1981,1982,1983, 1986, 1989, 1992,1995,1998,2001 Printed and bound in the United States of America.
NOTE: This new edition of the Pressure Vessel Handbook supersedes all previous editions, effective July 1,2001. The changes over the previous Eleventh Edition have been made necessary by the revision of Codes, Standards, Specifications, etc.
FOREWORD
Engineers who design equipment for the chemical process industry are sooner or later confronted with the design of pressure vessels and mounting requirements for them.
This is very often a frustrating
experience for anyone who has not kept up with current literature in the field of code requirements and design equations.
First he must familiarize himself with the latest version of the applicable code.
Then he must search the literature for techniques
used in design to meet these codes. Finally he must select material properties and dimensional data from various handbooks and company catalogs for use in the design equations. Mr. Megyesy has recognized this problem.
For several years he
has been accumulating data on code requirements and calculational methods.
He has been presenting this information first in the form
of his "Calculation Form Sheets" and now has put it all together in one place in the Pressure Vessel Handbook. I believe that this fills a real need in the pressure vessel industry and that readers will find it extremely useful.
Paul Buthod
PREFACE This reference book is prepared for the purpose of making fonnulas, technical data, design and construction methods readily available for the designer, detailer, layoutmen and others dealing with pressure vessels. Practical men in this industry often have difficulty finding the required data and solutions, these being scattered throughout extensive literature or advanced studies. The author's aim was to bring together all of the above material under one cover and present it in a convenient fonn. The design procedures and fonnulas of the AS ME Code for Pressure Vessels, Section VIII Division I have been utilized as well as those generally accepted sources which are not covered by this Code. From among the alternative construction methods described by the Code the author has selected those which are most frequently used in practice. In order to provide the greatest serviceability with this Handbook, rarely occurring loadings, special construction methods or materials have been excluded from its scope. Due to the same reason this Handbook deals only with vessels constructed from ferrous material by welding, since the vast majority of the pressure vessels are in this category. A large part of this book was taken from the works of others, with some of the material placed in different arrangement, and some unchanged. The author wishes to acknowledge his indebtedness to Professor Sandor Kalinszky, Janos Bodor, Laszl6 Felegyhazy and J6zsef Gyorfi for their material and valuable suggestions, to the American Society of Mechanical Engineers and to the publishers, who generously pennitted the author to include material from their publications. The author wishes also to thank all those who helped to improve this new edition by their suggestions and corrections. Suggestions and criticism concerning some errors which may remain in spite of all precautions shall be greatly appreciated. They contribute to the further improvement of this Handbook. Eugene F. Megyesy
7
ASME CODE vs. THIS HANDBOOK The ASME BOILER AND PRESSURE VESSEL CODE - 2001, Sect. VIII, Div. 1 The American Society of Mechanical Engineers set up a Committee in 1911 for the purpose of formulating standard rules for the construction of steam boilers and other pressure vessels that will perfonn in a safe and reliable manner. The Code comprises these rules. It's scope includes vessels: 1. made of nonferrous materials, cast iron, high alloy and carbon steel, 2. made by welding, forging, bracing, and 3. applying a wide variety of construction methods and details. It includes all vessels where the question of safety is concerned.
PRESSURE VESSEL HANDBOOK2001, Twelfth Edition The Handbook covers design and construction methods of pressure vessels: 1. made of carbon steel, 2. made by welding 3. applying construction methods and details which are the most economical and practical, which are in accordance with the Code rules, and thus generally followed by the industry. The vast majority of the pressure vessels today fall into this category. For construction rules and details which are excluded from the scope of the Handbook, references are made to the applicable Code paragraphs to avoid neglecting them.
The Code - as it is stated in paragraph UG2 - "does not contain rules to cover all details of design and construction ... " "where details are not given, it is intended that the Manufacturer ... shall provide details of design and construction."
Details of design and construction not covered by the Code are offered by the Handbook including: Design of tall towers, wind load, earthquake, vibration, eccentric load, elastic stability, deflection, combination of stresses, nozzle loads, reaction of supports, lugs, saddles, and rectangular tanks.
"The Code is not a handbook." "It is not intended that this Section be used as a design handbook" as it is stated in the Foreword of the Code.
The updated and revised Code is published in three years intervals. Addenda, which also include revisions to the Code, are published annually. Revisions and additions become mandatory six (6) months after the date of issuance, except for boilers and pressure vessels contracted for prior to the end ofthe 6 month period. (Code Foreword)
The aim of this Handbook is to be easily handled and consulted. Tables, charts eliminate the necessity of calculations, Geometry, layout of vessels, piping codes, API storage tanks, standard appurtenances, painting of steel surfaces, weights, measurements, conversion tables, literature, definitions, specification for vessels, design of steel structures, center of gravity, design of welded joints, boIted connections, boiler and pressure vessel laws, chemical resistance of metals, volumes, and surfaces of vessels, provide good serviceability. The Handbook is updated and revised in three years intervals, reflecting the changes of Code rules, new developments in the design and construction method, and includes the revisions of its sources.
8
THE ASME CODE ASME Boiler and Pressure Vessel Code, Section VIII, Division 1 An internationally recognized Code published by The American Society of Mechanical Engineers. PRESSURE VESSEL - is a containment of solid, liquid or gaseous material under internal or external pressure, capable of withstanding also various other loadings. BOILER - is a part of a steam generator in which water is converted into steam under pressure. RULES OF DESIGN AND CONSTRUCTION - Boiler explosions around the turn of the century made apparent the need for rules governing the design and construction of vessels. The first ASME Code was published in 1914. ISSUE TIME - The updated and revised Code is published in three years intervals (2001 and so on). Addenda, which also include revisions to the Code, are published annually. Revisions and additions become mandatory 6 months after the date of issuance, except for boilers and pressure vessels contracted for prior to the end of the 6 month period. (Code Foreword) SCOPE OF THE CODE - The rules of this Division have been formulated on the basis of design principles and construction practices applicable to vessels designed for pressures not exceeding 3000 psi. Code U-l (d) Vessels, which are not included in the scope of this Division, may be stamped with the Code U Symbol if they meet all the applicable requirements of this Division. Code U-2(g) THE DESIGN METHOD - The Code rules concerning design of pressure parts are based on the maximum stress theory, i.e., elastic failure in a ductile metal vessel occurs when the maximum tensile stress becomes equal to the yield strength ofthe material. OTHER COUNTRIES' Codes deviate from each other considerably, mainly because of differences in the basic allowable design stresses. The ASME Code's regulations may be considered to be at midway between conservative and unconservative design. COMPUTER PROGRAMS - Designers and engineers using computer programs for design or analysis are cautioned that they are responsible for all technical assumptions inherent in the programs they use and they are solely responsible for the application of these programs to their design. (Code, Foreword) DESIGN AND CONSTRUCTION NOT COVERED - This Division ofthe Code does not contain rules to cover all details of design and construction. Where complete details are not given, it is intended that the Manufacturer shall provide details which will be as safe as those provided by the rules of this Division. Code U-2(g)
CONTENTS
PART I
Design and Construction of Pressure Vessels ............. 11
PART II
Geometry and Layout of Pressure Vessels .............. 257
PART III
Measures and Weights ............................................ 321
PART IV
Design of Steel Structures ....................................... 447
PART V
Miscellaneous .......................................................... 465
11
PART I. DESIGN AND CONSTRUCTIONS OF PRESSURE VESSEL 1. Vessels Under Internal Pressure ............................................ Stresses in Cylindrical Shell, Definitions, Formulas, Pressure of Fluid, Pressure-Temperature Ratings of American Standard Carbon Steel Pipe Flanges.
15
2. Vessels Under External Pressure ............................................ Definitions, Formulas, Minimum Required Thickness of Cylindrical Shell, Chart for Determining Thickness of Cylindrical and Spherical Vessels under External Pressure when Constructed of Carbon Steel.
31
3. Design of Tall Towers ............................................................ Wind Load, Weight of Vessel, Seismic Load, Vibration, Eccentric Load, Elastic Stability, Deflection, Combination of Stresses, Design of Skirt Support, Design of Anchor Bolts (approximate method), Design of Base Ring (approximate method), Design ofAnchor Boltand Base Ring, Anchor Bolt Chair for Tall Towers.
52
4. Vessel Supports........... ............... ....... .............. ...................... Stresses in Large Horizontal Vessels Supported by Two Saddles, Stresses in Vessels on Leg Support, Stresses in Vessels Due to Lug Support, Lifting Attachments, Safe Loads for Ropes and Chains.
86
5. Openings ......................................... :...................................... Inspection Openings, Openings without Reinforcing Pad, Opening with Reinforcing Pad, Extension of Openings, Reinforcement of Openings, Strength of Attachments, Joining Openings to Vessels, Length of Couplings and Pipes for Openings.
122
6. Nozzle Loads ..........................................................................
153
7. Reinforcement at the Junction of Cone to Cylinder ...............
159
8. Welding of Pressure Vessels ................................................. Welded Joints, Butt Welded Joint of Plates of Unequal Thicknesses, Application of Welding Symbols.
170
9. Regulations, Specifications .................................................... Code Rules Related to Various Services, Code Rules Related to Various Plate Thicknesses of Vessel, Tanks and Vessels Containing Flammable and Combustible Liquids, Properties of Materials, Description of Materials, Specification for the Design and Fabrication of Pressure Vesels, Fabrication Tolerances.
181
12
10. Materials of Foreign Countries ..............................................
194
11. Welded Tanks ........................................................................
203
12. Piping Codes ..................... ................ ......................... ............
208
13. Rectangular Tanks .................................................. ................
213
14. Corrosion ................................................................................
221
15. Miscellaneous ....................................................................... Fabricating Capacities, Pipe and Tube Bending, Pipe Engagement, Drill Sizes for Pipe Taps, Bend Allowances, Length of Stud Bolts, Pressure Vessell Detailing, Preferred Locations, Common Errors, Transportation of Vessels.
232
16. Painting of Steel Surfaces .....................................................
247
IN REFERENCES THROUGHOUT THIS BOOK "CODE" STANDS FOR ASME BOILER AND PRESSURE VESSEL CODE SECTION VIII, DIVISION 1 - AN AMERICAN STANDARD.
2001 EDITION
13
STRESSES IN PRESSURE VESSELS Pressure vessels are subject to various loadings, which exert stresses of different intensities in the vessel components. The category and intensity of stresses are the function of the nature ofloadings, the geometry and construction of the vessel components. LOADINGS (Code UG-22) a. Internal or external pressure b. Weight of the vessel and contents c. Static reactions from attached equipment, piping, lining, insulation, d. The attachment of internals, vessel supports, lugs, saddles, skirts, legs e. Cyclic and dynamic reactions due to pressure or thermal variations f. Wind pressure and seismic forces g. Impact reactions due to fluid shock h. Temperature gradients and differential thermal expansion 1. Abnormal pressures caused by deflagration. STRESSES (Code UG-23)
a.
Tensile stress
b. Lingitudinal compressive stress c. General primary membrane stress induced by any combination of loadings. Primary membrane stress plus primary bending stress induced by combination of loadings, except as provided in d. below. d. General primary membrane stress induced by combination of earthquake or wind pressure with other loadings. Seismic force and wind pressure need not be considered to act simulta neously.
MAXIMUM ALLOWABLE STRESS Sa = Maximum allowable stress in tension for carbon and low alloy steel Code Table UCS-23; for high alloy steel Code Table UHA-23., psi. (See properties of materials page 186-190.) The smaller of Sa or the value of factor B determined by the procedure described in Code UG 23 (b) (2)
1.5 Sa
Sa = (see above)
1.2 times the stress permitted in a., b., or c. This rule applicable to stresses exerted by internal or external pressure or axial compressive load on a cylinder.
14
STRESSES IN CYLINDRICAL SHELL
Unifonn internal or external pressure induces in the longitudinal seam two times larger unit stress than in the circumferential seam because of the geometry of the cylinder. A vessel under external pressure, when other forces (wind, earthquake, etc.) are not factors, must be designed to resist the circumferential buckling only. The Code provides the method of design to meet this requirement. When other loadings are present, these combined loadings may govern and heavier plate will be required than the plate which was satisfactory to resist the circumferential buckling only. The compressive stress due to external pressure and tensile stress due to internal pressure shall be detennined by the fonnulas: FORMULAS LONGITUDINAL JOINT
CIRCUMFERENTIAL JOINT
S _ PD 2t
2 -
D p 51 52 t
= =
= = =
NOTATION Mean diameter of vessel, inches Internal or external pressure, psi Longitudinal stress, psi Circumferential (hoop) stress, psi Thickness of shell, corrosion allowance excluded, inches
EXAMPLE
Given
D p t
=
= =
96 inches 15 psi 0.25 inches
PD SI = 4t
=
15 x 96 4 x 0.25
15 x 96
=
1440 psi
=
2880 psi
2 x 0.25 For towers under internal pressure and wind load the critical height above which compressive stress governs can be approximated by the formula:
H
=
PD 12t
where H = Critical height of tower, ft.
15
INTERNAL PRESSURE 1.
OPERA TING PRESSURE
The pressure which is required for the process, served by the vessel, at wh ich the vessel is normally operated. 2.
DESIGN PRESSURE
The pressure used in the design of a vessel. It is recommended to design a vessel and its parts for a higher pressure than the operating pressure. A design pressure higher than the operating pressure with 30 psi or 10 percent, whichever is the greater, will satisfy this requirement. The pressure of the fluid and other contents of the vessel should also be taken into consideration. See tables on page 29 for pressure of fluid.
3.
MAXIMUM ALLOWABLE WORKING PRESSURE
The internal pressure at which the weakest element of the vessel is loaded to the ultimate permissible point, when the vessel is assumed to be: (a) (b) (c) (d)
in corroded condition under the effect of a designated temperature in normal operating position at the top underthe effect of other loadings (wind load, external pressure, hydrostatic pressure, etc.) which are additive to the internal pressure.
When calculations are not made, the design pressure may be used as the maximum allowable working pressure (MA WP) code 3-2. A common practice followed by many users and manufacturers of pressure vessels is to limit the maximum allowable working pressure by the head or shell, not by small elements as flanges, openings, etc. See tables on page 28 for maximum allowable pressure for flanges. See tables on page 142 for maximum allowable pressure for pipes. The term, maximum allowable pressure, new and cold, is used very often. It means the pressure at which the weakest element of the vessel is loaded to the ultimate permissible point, when the vessel: (a) is not corroded (new) (b) the temperature does not affect its strength (room temperature ) (cold) and the other conditions (c and d above) also need not to be taken into consideration. 4.
HYDROSTATIC TEST PRESSURE
At least 1.3 times the maximum allowable working pressure or the design pressure to be marked on the vessel when calculations are not made to determine the maximum allowable working pressure. Ifthe stress value of the vessel material at the design temperature is less than at the test temperature, the hydrostatic test pressure should be increased proportionally. Hydrostatic test shall be conducted after all fabrication has been completed.
16
In this case, the test pressure shall be: 1.5 X
Stress Value S At Test Temperature Max. Allow. W. Press. (Or Design Press.)
X
Stress Value S At Design Temperature
Vessels where the maximum allowable working pressure limited by the flanges, shall be tested at a pressure shown in the table: Primary Service Pressure Rating
1501b
300lb 400lb
600lb
9001b 1500lb
Hydrostatic Shell Test Pressure
425
1100
2175
3250
1450
5400
25001b 9000
Hydrostatic test of multi-chamber vessels: Code UG-99 (e) A Pneumatic test may be used in lieu of a hydrostatic test per Code UG-I 00 Proof tests to establish maximum allowable working pressure when the strength of any part of the vessel cannot be computed with satisfactory assurance of safety, prescribed in Code UG-I 0 1. 5. MAXIMUM ALLOWABLE STRESS V ALVES
The maximum allowable tensile stress values permitted for different materials are given in table on page 189. The maximum allowable compressive stress to be used in the design of cylindrical shells subjected to loading that produce longitudinal compressive stress in the shell shall be determined according to Code par. UG-23 b, c, & d. 6. JOINT EFFICIENCY The efficiency of different types of welded joints are given in table on page 172. The efficiency of seamless heads is tabulated on page 176. The following pages contain formulas used to compute the required wall thickness and the maximum allowable working pressure for the most frequently used types of shell and head. The formulas of cylindrical shell are given for the longitudinal seam, since usually this governs. The stress in the girth seam will govern only when the circumferential joint efficiency is less than one-half the longitudinal joint efficiency, or when besides the internal pressure additional loadings (wind load, reaction of saddles) are causing longitudinal bending or tension. The reason for it is that the stress arising in the girth seam pound per square inch is one-half of the stress in the longitudinal seam. The formulas for the girth seam accordingly:
PR 1 =
2SE
See notation on page 22.
+ O.4P
P =
2SEI R - 0.41
17 NOTES
18
INTERNAL PRESSURE FORMULAS IN TERMS OF INSJDE DIMENSIONS NOTATION P
5
E
=
Design pressure or max. allowable working pressure psi = Stress value of material psi. page 189
A
R
= Joint efficiency. page 172 = Inside radius. inches
D = Inside
diameter. inches Wall thickness. inches CA. = Corrosion allowance. inches t
=
CYLINDRICAL SHELL (LONG SEAM) 1
r
/
\
\
t
+--.f-- l~ '~
PR SE-O.6P
t
R
P=
SE~_ R+O.6t
I.
Usually the stress in the long seam is governing. See preceding page.
2.
When the wall thickness exceeds one half of the inside radius or P exceeds 0.385 SE, the formulas given in the Code Appendix 1-2 shall be applied.
B
SPHERE
6
and
HEMISPHERICAL HEAD
PR 2SE-O.2P
t
P
2SE t R+O.2t
~"","~
l
R
f
I.
For heads without a straight flange. use the efficiency of the head to shell joint if it less than the efficiency of the seams in the head.
2. When the wall thickness exceeds 0.356 R or P exceeds 0.665 SE. the formulas given in the Code Appendix 1-3, shall be applied. C
2: 1 ELLIPSOIDAL HEAD
hS-~ I. ]\1 0
h = 0/4
t
I.
PD 2SE-O.2P
P=
2SEt D+O.2t
For ellipsoidal heads, where the ratio of the major and minor axis is other than 2: I, see Code Appendix 1-4(c).
19
EXAMPLES E
DESIGN DATA: p = 100 psi design pressure S = 20,000 psi stress value of SA 515-70 plate @ 500°F E = 0.85, efficiency of spot-examined joints of shell and hem is. head to shell
1.00, joint efficiency of seamless heads R = 48 inches inside radius* D = 96 inches inside diameter* t = required wall thickness, inches CA. = 0.125 inches corrosion allowance * in corroded condition greater with the corrosion allowance.
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
Determine the required thickness, t of a shell
Determine the maximum allowable working pressure P for 0.500 in. thick shell when the vessel is in new condition.
100 X 48.125 . t=20,000 X 0.85 -0.6XIOO =0.284 m.
+CA.
=
P=20,000 X 0.85 X 0.500 48 + 0.6 X 0.500
0.125 in. 0.409 in.
176 psi
Use 0.500 in. plate
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
The head furnished without straight flange. Determine the required thickness, t ofa hemispherical head. t
100X48.125 =0.142 in. 2 X 20,000 X 0.85 -0.2 XI 00 +C A.
0.125 in. 0.267 in.
Determine the maximum allowable working pressure, P for 0.3125 in. thick head, when it is in new condition. P 2 X 20,000 X 0.85 X 0.3125 -221 48+0.2XO.3125 -
. pSI
Use OJ 125 in. plate
SEE DESIGN DATA ABOVE Determine the required thickness ofa seamless ellipsoidal head. 100 X 96.25 . t 2 X 20,000 X 1.0-0.2 X 100 =0.241 m.
+CA.
0.125 in. OJ66 in.
Use 0.375 in. min. thk. head
SEE DESIGN DATA ABOVE
Determine the maximum allowable working pressure, P for 0.250 in. thick seamless head, when it is in corroded condition. P
2 X 20,000 X 1.0 X 0.250 -103 . 96.25 + 0.2 X 0.250 pSI
20
INTERNAL PRESSURE FORMULAS IN TERMS OF INSIDE DIMENSIONS
D = Inside diameter, inches
NOTATION
a = One half of the included (apex) angle, degrees L = Inside radius of dish, inches r = Inside knuckle radius. inches I = Wall thickness, inches C.A. = Corrosion allowance. inches
P = Design pressure or max. allowable working pressure psi S = Stress value of material psi, page 189
E = Joint efficiency, page 172 R = Inside radius. inches
D
CONE
AND
CONICAL SECTION
PD
t=~~----~~~~:7
2 cos a (SE-O.6P)
P= 2SEt cos a D+ 1.2t cos a
I. The half apex angle, a not greater than 30° 2. When a is greater than 30 ~ special analysis is required. (Code Appendix 1-5(g))
ASME FLANGED AND DISHED HEAD
E
(TORISPHERICAL HEAD)
0.885PL t
SEt
SE-O.IP
P
=-=0--=.8=85-=-=L=-+-0-=-."'-1t
When lIr less than 16 2/3
\ When the min. t~nsile strength of material exceeds 70,000 psi. see Code UG-32(e)
PLM
p=
t = -=-2=SE=--=0-=.2-=P
2SEt
LM+0.2t
VALUES OF FACTOR "M" L/r M
L/r M
*
1.00
1.50 1.25
1.00
1.06 1.08
1.03 7.00
8.00 1.46
2.00
2.25
1.10
2.50 2.75 1.15
1.13
1.17 10.0
9.00 8.50
7.50 1.41
I. 75
19·50
3.00 1.18
3.25 1.20
11.0 10.5
3.50
4.00
1.22 1.25 12.0
11.5
4.50 1.28
5.00 1.31
14.0 13.0
5.50 6.00 1.34 1.36 16.0
15.0
2 16]"
1.54 1.50 1.58 1.62 1.69 I. 75 1.48 1.52 1.56 I.~Q 1.65 1.72 1.77 THE MAXIMUM ALLOWED RATIO: L - D + 2t (see note 2 on facing page) 1.44
6.50 1.39
•
21
EXAMPLES DESIGN DATA: P = 100 psi design pressure S = 20,000 psi stress value of SA 515-70 plate @ 500°F E = 0.85, efficiency of spot-examined I joints ' E = 1.00, joint efficiency of seamless heads SEE DESIGN DATA ABOVE cos 30°= 0.866 Determine the required thickness, t of a cone
L = 96 inches inside radius of dish* D = 96 inches inside diameter* t = required wall thickness, inches a = 300 0ne half ofthe apex angle CA. = 0.125 inches corrosion allowance * in corroded condition greater with the corrosion allowance
SEE DESIGN DATA ABOVE
I
!
100 X 96.25 -0 "28 . t 2XO.866 (20,000 X 0.85 _0.6XlOO) - . J m.
+C.A.
Q 125 jn
Determine the maximum allowable working pressure, P for 0.500 in. thick cone, when the vessel is in new condition. P 2X20,000XO.85XO.500XO.866 96 + 1.2 X 0.500 X 0.866 152psi
0.453 in.
Use 0.500 in. plate SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE Llr = 16~ Determine the required thickness, t of a seamless ASME flanged and dished head. 0.885 x 100 x 96.125 . t=20,OOO x 1.0-0.1 XI 00 0.426 m.
+CA.
0.125 in. 0.551 in.
Determine the maximum allowable working pressure, P for 0.5625 in. thick seamless head, when the vessel is in new condition. P=
20,000 X 1.0 X 0.5625 132 psi 0.885 X 96 + 0.1 X 0.5625
Use 0.5625 in. plate SEE DESIGN DA T A ABOVE Knuckle radius r = 6 in. Llr = ~ = 16 M= 1.75 from table. Determine the required thickness t of a seamless ASME flanged and dished head. 100 X96.125 X 1.75 . t= 2 X 20,000 - 0.2 X 100 -0.421 m. 0.125 in. 0.54610. Use 0.5625 in. min. thick head
+CA.
SEE DESIGN DATA ABOVE Knuckle radius r = 6 in. Llr = 9£ = 16 M= 1.75 from table Determine the maximum allowable working pressure, P for a 0.5625 in. thick seamless head when the vessel is in corroded condition.
p= 2x20,000xl.OxO.5625 104 . 96.125x1.75+0.2 x0.4375 pSI
NOTE: When the ratio of Llr is greater than 161, fupn-Code construction) the values of M may be calculated by the formula: M = Y4 (3 + Wr)
22
INTERNAL PRESSURE FORMULAS IN TERMS OF OUTSIDE DIMENSIONS
NOTATION
= Joint efficiency, page 172 = Outside radius, inches D = Outside· diameter, inches t = Wall thickness, inches C.A. = Corrosion allowance. inches E
P = Design pressure or max. allowable
R
working pressure psi
S
= Stress va'ue of material psi, page 189
A
CYLINDRICAL SHELL (LONG SEAM)I
PR 1-
SE
+ 0.4P
SEI
P - R - O.4t
1. Usually the stress in the long seam is governing. See page 14 2. When the wall thickness exceeds one half of the inside radius or P exceeds 0.385 SE, the formulas givencin the Code Appendix 1-2 shall be applied.
B
SPHERE and HEMISPHERICAL HEAD
PR 1 -
2SE
+ 0.8P
2SEI P - R - 0.81
1. For heads without a straight flange, use the efficiency
of the head to shell joint if it is less than the efficiency of the seams in the head. 2. When the wall thickness exceeds 0.356 R or P exceeds 0.665 SE, the formulas given in the Code Appendix 1-3, shall be applied.
C
2:1 ELLIPSOIDAL HEAD PD
t=""'2"""'S=E-+--:"1-".8~P
2SEt P= ..- - D· -1.8t
1. For ellipsoidal heads, where the ratio of the major and minor axis is other than 2:1, see Code Appendix 1-4(c).
h = 0/4
23
EXAMPLES DESIGN DATA: P = 100 psi design pressure S = 20,000 psi stress value of SA 515-70 plate @ 500°F E = 0.85, efficiency of spot-examined joints of shell and hemis. head to shell
R D t
CA.
1.00, joint efficiency ofseamless heads = 48 inches outside radius = 96 inches outside diameter = Required wall thickness, inches = 0.125 inches corrosion allowance =
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE Determine the required thickness, t of a shell 100 X 48 0.283 in t 20,000 X 0.85 - 0.4 X 100 +C.A.
E
0.125 in. 0.408 in.
Determine the maximum allowable working pressure, P for 0.4375 in. thick shell when the vessel is in new condition. 20,000 X 0.85 X 0.4375 p= 155psi 48 - 0.4 X 0.4375
Use: 0.4375 in. thick plate
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE Head furnished without straight flange. Determine the required thickness, t of a hemispherical head. 100X48 0.141 in. 2 X20,000XO.85 +0.8 X 100
t
+CA.
0.125 in. 0.266 in.
Determine the maximum allowable wOFking pressure, P for 0.3125 in. thick head, when the vessel is in new condition.
p=2 X 20,000 X 0.85 X 0.3125 222 psi 48-0.8 XO.3125
Use: 0.3125 in. min. thick head
SEE DESIGN DA T A ABOVE
SEE DESIGN DATA ABOVE
Determine the required thickness t of a seamless ellipsoidal head.
Determine the maximum allowable working pressure, P for 0.375 in. thick head, when it is in new condition.
t
100X96 0.239 in. 2 X 20,000 X l.0+ l.8X 100 +CA.
Use 0.375 in. min. thick head
0.125 in. 0.364 in.
P
2 X 20,000 X 1.0 X 0.375 96-1.8 X 0.375 157psi
24
INTERNAL PRESSURE FORMULAS IN TERMS OF OUTSIDE DIMENSIONS NaTATION
D = Outside diameter, inches a = One half of the included (apex) angle. degrees L = Outside radius of dish, inches r = Inside knuckle radius. inches t = Wall thickness, inches C.A. = Corrosion allowance. inches
P = Design pressure or max. allowable working pressure psi S = Stress value of material psi, page 189
E = Joinl efficiency. page 172 R = OUlside radius, inches
D
CONE
AND
CONICAL SECTION
~
!
[ ~
t=
1
PD
P=
2 cos a (SE +0.4P)
2SEt cos a D -0.8t cos a
~
Ii::
T 0
1-
-oj
'r-'-
I. The half apex angle, a not greater than 30° 2. When a is greater than 30°,. special analysis is
required. (Code Appendix 1-5(g»
E
ASME FLANGED AND DISHED HEAD (TORISPHERICAL HEAD) WhenL/r= 16 2 /3
<,(l ~
--f t:
~
i
\!.I
t
0.885PL SE+0.8P
P
SEt 0.885L-0.8t
When L/r Less Than 16 2/3
0
\ t
When the min. tensile strength of material exceeds 70,000 psi. see Code UG-32(e)
PLM 2SE+P(M-0.2)'
2SEt P= ML -t(M-0.2)
V ALUES OF FACTOR M L/r M L/r M
•
1.00
1.50 1.25 1.06
1.00 11.03 7.00
1.08
144
1.10
8.50 1.46
2.25 1.13
9.00
8.00 17.50
1.41
1.75
2.00
11.48
2.50 1.15
1.17
10.0 9.50
1.50
2.75
1.52
3.00 1.18
1.20
11.0 10.5
1.54
3.25
1.56
3.50 1.22
THE MAXIMUM ALLOWED RATIO : L - t
=D
1.25
12.0 11.5
1.58
4.00
1.60
4.50 1.28
1.31
14.0 13.0
1.62
5.00
11.65
5.50 1.34 16.0
15.0 1.69
11.72
1.75
6.00 1.36 16t 1.77
(see note on facing page)
6.50 1.39
•
25
EXAMPLES heads 48 inches outside radius 96 inches outside diameter 30° one half of the apex angle 96 inches outside radius of dish Required wall thickness, inches 0.125 inches corrosion allowance
DESIGN DATA: P = 100 psi design pressure S = 20,000 psi stress value of SA 515-70 plate @ 500°F E = 0.85, efficiency of spot-examined joints E = 1.00, joint efficiency of seamless
t = CA. =
SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
cos 30° = 0.866 Determine the required thickness, t of a cone l00X % . t=2XO.866X(20,OOOXO.85+O.4Xl (0)=0.326 m. 0.125 in. 0.451 in.
+CA.
R
=
D = ex = L =
Determine the maximum allowable working pressure, P for 0.500 in. thick cone in new condition.
p=2 X 20,000 X 0.85 X 0.500 X 0.866 153 psi 96 -(0.85 X 0.500 X 0.866)
Use: 0.500 in. thick plate SEE DESIGN DATA ABOVE
SEE DESIGN DATA ABOVE
Llr = 16~ Determine the required thickness, t of a seamless ASME flanged and dished head.
0.885 X 100 X96 . t= 20,000 X 1.0 + 0.8 X 100=0.423 m. +C.A.
0.125 in. 0.548 in.
Determine the maximum allowable working pressure, P for 0.5625 in. thick seamless head, when the vessel is in corroded condition. (=0.5625-0.125 =0.4375
P
20,000 X 1.0 X 0.4375 0.885 X96-0.8 X0.4375
10"" . ,) pSI
Use: 0.5625 in. min. thick head SEE DESIGN DATA ABOVE Knuckle radius r = 6 in. Llr = 96 = 16 6 M= 1.75 from table. Determine the required thickness t of a seamless ASME flanged and dished head. 100X96X 1.75 . t=2 X 20,000 X 1.0+ 100(1.75-0.2) 0.419m. +CA.
0.125 in. 0.544 in.
SEE DESIGN DATA ABOVE Knuckle radius r = 6 in. Llr =
~
= 16
M= 1.75 from table. Determine the maximum allowable working pressure, P for a 0.5625 in. thick seamless head when the vessel is in corroded condition.
2 X 20,000 X 1.0 X 0.4375 P 1.75 X96-0.4375(1.75 _0.2) 104 psi
Use 0.5625 in. min. thick head NOTE: When the ratio ofLir is greater than l6~ , (non-Code construction) the values of M may be calculated by the formula: M = 14 (3 + Wr)
26
INTERNAL OR EXTERNAL PRESSURE FORMULAS NOTATION
P = Internal or external design pressure psi d
E=joint efficiency
= Inside diameter of shell, in.
S = Maximum allowable stress value of material, psi t = Minimum required thickness of head, exclusive of corrosion allowance, in. th = Actual thickness of head exclusive of corrosion allowance, in. tr = Minimum required thickness of seamless shell for pressure, in. ts = Actual thickness of shell, exclusive of corrosion allowance, in. A
CIRCULAR FLAT HEADS t = d 0.13 P/SE
V
This formula shall be applied: 1. When d does not exceed 24 in. 2. thld is not less than 0.05 nor greater than 0.25 3. The head thickness, th is not less than the shell thickness, ts B
t=dVCPISE
C = 0.33tr/ ts
c
D
C min. = 0.20
2 t,min. nor less than 1.25ts need not be greater than t
If a value of tr/ ts less than 1 is used in calculating t, the shell thickness t s shall be maintained along a distance inwardly from the inside face of the head equal to at least
2..[cii: Non-circular, bolted flat heads, covers, blind flanges Code UG-34; other types of closures Code UG-35
27
INTERNAL OR EXTERNAL PRESSURE EXAMPLES DESIGN DATA P = 300 psi design pressure E =joint efficiency d = 24 in. inside diameter of shell S = 17,100 psi maximum allowable stress value of SA-515-60 plate tr = 0.243 in. required thickness of seamless shell for pressure. ts = 0.3125 in. actual thickness of shell. DETERMINE THE MINIMUM REQUIRED THICKNESS, t
=
t
=
d "0.13 P/SE
1.146in.
24 " 0.13 x 300117,100x 1
Use 1.25 in. head Checking the limitation of
l.25 24
d
= 0.052
The ratio of head thickness to the diameter of the shell is satisfactory SEE DESIGN DATA ABOVE 0.243
tr
=
C
0.33 -[
=
0.33
0.3125
s
=
t
d
JCP/SE
=
24
=
0.26
~ 0.26 x 300/17,100'(
1
=
l.620 in.
Use 1.625 in. plate Using thicker plate for shell, lesser thickness will be satisfactory for the head. Is =
C
=
I =
0.375 in. tr
0.33 -t- = 0.33 s
d .jCP/SE
=
24
0.243 0.375
=
0.214
oJ 0.214 x 30
Use 1.625 in. plate The shell thickness shall be maintained along a distance 2 ~ from the inside face of the head
2 "24 x 0.375 = 6 in.
28
PRESSURE - TEMPERATURE RATINGS FOR STEEL PIPE FLANGES AND FLANGED FITTINGS American National Standard ANSI B 16.5-199611998 ADDENDA
Class 150 lb. 300 lb. 400 lb. 600 lb. 900 lb. 1,500 lb. 2,5001b Hydrostatic test 450 1,125 1,500 2,225 3,350 5,575 9,275 pressure, psig Temperature, F MAXIMUM ALLOWABLE NON-SHOCK PRESSURE PSIG. -20 to 100 285 740 990 1,480 2,220 3,705 6,170 200 260 675 900 1,350 2,025 3,375 5,625 3,280 5,470 300 230 655 875 1,315 1,970 400 1,900 3,170 845 1,270 200 5,280 635 500 600 650 700
170 140 125 110
600 550 535 535
800 730 715 710
1,200 1,095 1,075 1,065
1,795 1,640 1,610 1,600
2,995 2,735 2,685 2,665
4,990 4,560 4,475 4,440
750 800 850 900
95 80 65 50
505 410 270 170
670 550 355 230
1,010 825 535 345
1,510 1,235 805 515
2,520 2,060 1,340 860
4,200 3,430 2,230 1,430
950 1,000
35 20
105 50
140 70
205 105
310 155
515 260
860 430
Ratings apply to NPS Yz trough NPS 24 and to materials: A 105 (1) A 350 Gr. LF2 (1) A 350 Gr. LF6 Cl. 1 (4) A 216 Gr. WCB (1) A 515 Gr. 70 (1) A 516 Gr. 70 (1) (2) A 537 Cl. 1 (3) NOTES: (1) Permissible, but not recommended for prolonged use above 800 OF. (2) Not to be used over 850 OF. (3) Not to be used over 700 oF. (4) Not to be used over 500 oF. Flanges of ANSI B 16. 5 shall not be used for higher ratings except where it is justified by the design methods of the Code. Ratings are maximum allowable non-shock working pressures expressed as gage pressure, at the tabulated temperatures and may be interpolated between temperatures shown. Temperatures are those on the inside of the pressure-containing shell of the flange. In general, it is the same as that of the contained material. Flanged fittings shall be hydrostatically tested.
29
PRESSURE OF FLUID STATIC HEAD The fluid in the vessel exerts pressure on the vessel wall. The intensity of the pressure when the fluid is at rest is equal in all directions on the sides or at bottom of the vessel and is due to the height of the fluid above the point at which the pressure is considered. The static head when applicable shall be added to the design pressure of the vessel. The tables below when applicable shall be added to the design pressure of the water. To find the pressure for any other fluids than water, the given in the tables shall be be mUltiplied with the specific gravity of the fluid in consideration.
Pressure in Pounds per Square Inch for Different Heads of Water
I
Head Feet 0 10 20 30 40 50 (i)
70 00 'Xl
0 4.33 8.66 12.99 17.32 21.65 25.98 30.31 34.64 38.97
1 0.43 4.76 9.09 13.42 17.75 22.08 26.41 30.74 35.07 39.40
2 0.87 5.20 9.53 13.86 18.19 22.52 26.85 31.18 35.51 39.84
3 1.30 5.63 9.96 14.29 18.62 22.95 27.28 31.61 35.94 40.27
4 1.73 6.06 10.39 14.72 19.05 23.38 27.71 32.04 36.37 40.70
5 2.16 6.49 10.82 15.15 19.48 23.81 28.14 32.47 36.80 41.13
6 2.60 6.93 11.26 15.59 19.92 24.25 28.58 32.91 37.24 41.57
7 3.03 7.36 11.69 16.02 20.35 24.68 29.01 33.34 37.67 42.00
8 3.46 7.79 12.12 16.45 20.78 25.11 29.44 33.77 38.10 42.43
9 3.90 8.23 12.56 16.89 21.22 25.55 29.88 34.21 38.54 42.87
NOTE: One foot of water at 62° Fahrenheit equals .433 pound pressure per square inch. To find the pressure per square inch for any feet head not given in the table above, multiply the feet times .433.
Heads of Water in Feet Corresponding to Certain Pressure in Pounds per Square Inch Pressure, Lbs. 0
0
1
2
3
4
5
6
7
8
9
18.5 4.6 2.3 11.5 13.9 16.2 20.8 6.9 9.2 23.1 25.4 27.7 30.0 32.3 34.6 36.9 39.3 41.6 43.9 48.5 50.8 53.l 55.4 57.7 60.0 62.4 64.7 46.2 67.0 20 71.6 73.9 78.5 80.8 83.l 85.4 87.8 69.3 90.1 76.2 30 92.4 94.7 97.0 99.3 101.6 103.9 106.2 108.5 110.8 113.2 40 115.5 117.8 120.1 122.4 124.7 127.0 129.3 131.6 133.9 136.3 50 (i) 138.6 140.9 143.2 145.5 147.8 150.l 152.4 154.7 157.0 159.3 70 161.7 164.0 166.3 168.6 170.9 173.2 175.5 177.8 180.1 182.4 184.8 187.l 189.4 191.7 194.0 196.3 198.6 200.9 203.2 205.5 00 207.9 210.2 212.5 214.8 217.l 219.4 221.7 224.0 226.3 228.6 'Xl NOTE: One pound of pressure per square inch of water equals 2.309 feet of water at 62° Farenheit. Therefore, to find the feet head of water for any pressure not given in the table above, multipy the pressure pounds per square inch by 2.309.
10
30
TABLES F or quick comparison of required plate thickness and weight for various materials and at a different degree of radiographic examination. A Stress values at temperature -20° to 500 OF. SA53 B SA 515-60 SA 516-60 14,535 17,100
SA285 C 85% J. E. 100% J. E.
13,345 15,700
SA515-70 SA 516-70 17,000 20,000
B Ratios of Stress Values 13,345 13,345 14,535 15,700 17,000 17,100 20,000
-
0.92 0.85 0.79 0.78 0.67
14,535 1.09 -
0.92 0.86 0.85 0.73
-
17,000 1.27 1.17 1.08
0.93 0.92 0.79
-
17,100 1.28 1.18 1.09 1.01
0.99 0.85
0.86
15,700 1.18 1.08
-
20,000 1.49 1.37 1.27 1.18 1.17 -
Table A shows the stress value of the most frequently used shell and head materials. Table B shows the ratios of these stress values. EXAMPLE: 1. For a wessel using SA 515-70 plate, when spot radiographed, the required thickness 0.4426 inches and the weight of the vessel 12600 lbs. 2. What plate thickenss will be required, and what will the weight of the vessel be using SA 285-C plate and full radiographic examination:
In case 1. The stress value of the material 17,000 In case 2. The stress value of the material 15,700 The ratio of the two stress values from Table B= 1.08 In this proportion the required plate thickness and the weight of the vessel will be increased. 0.4426 x 1.08 = 0.4780 in. 12600 x 1.08 = 13608 lb.
31
EXTERNAL PRESSURE DESIGN PRESSURE When Code Symbol is to be applied, the vessel shall be designed and stamped with the maximum allowable external working pressure. It is recommended that a suitable margin is provided when establishing the maximum allowable external pressure to allow for pressure variation in service. Code UG-28(f). Vessels intended for service under external working pressure of 15 psi and less may be stamped with the Code Symbol denoting compliance with the rules for external pressure provided all the applicable rules of this Division are also satisfied. Code UG-28(f). This shall not be applied if the vessel is operated at a temperature below minus 20° F, and the design pressure is determined by the Code UCS-66(c)(2) or Code UHA-51(b) to avoid the necessity of impact test. Vessels with lap joints: Code UG-28(g) Non-cylindrical vessel, jacket: Code UG-28(i).
TEST PRESSURE Single-wall vessels designed for vacuum or partial vacuum only, shall be subjected to an internal hydrostatic test or when a hydrostatic test is not practicable, to a pneumatic test. Code UG-99(f). Either type of test shall be made at a pressure not less than 1Yz times the difference between normal atmospheric pressure and the minimum design internal absolute pressure. Code UG-99(f). Pneumatic test: Code UG-l 00. The design method on the following pages conform to ASME Code for Pressure Vessels Section VIII, Div. 1. The charts on pages 42-47 are excerpted from this Code.
32
EXTERNAL PRESSURE FORMULAS NOTATION P External design pressure, psig. ~ ~_ Maximum allowable working pressure, psig. ll. Outside diameter, in. L0 the length, in. of vessel section between: 1. circumferential line on a head at one-third the depth of the head-tangent line, 2. stiffening rings 3. jacket closure 4. cone-to-cylinder junction or knuckle-to-cylinder junction of a toriconical head or section, 5. tube sheets (see page 39) t Minimum required wall thickness, in.
=
=
=
A.
1"1
~
,-"----' -
....---1111- r-
CYLINDRICAL SHELL Seamless or with Longitudinal Butt Joints When D/ / equal to or greater than 10 the maximum allowable pressure:
Pa=
48 3eD o Il)
The value of B shall be determined by the following procedure: 1. Assume a value for t; (See pages 49-511) Determine LI Do and D ~ 1/
VESSEL WITHOUT STIFFENING RING
B.
~
~ a:::
iii
~-:..--:
"'"
--~
Do
~
z
Z ~
\I. \I.
~
~H-----~----H--~--~
~'
-----,..
2. Enter Fig. G (Page 42) at the value of LIDo' Enter at 50 when LIDo is greater than 50, and at 0.05 when LIDo is less than 0.05.
3. Move horizontally to the line representing Dolt. From the point of intersection move vertically to determine the value of factor A . 4. Enter the applicable material chart (pages 43-47) at the value of A. Move vertically to the appltcable temperature line-. 5. From the intersection move horizontally and read the value of B. Compute the maximum allowable working pressure, P If the maximum allowable working pressure is smaller than the design pressure, the design procedure must be repeated increasing the vessel thickness or decreasing L by stiffening ring. -For values of A falling to the left of the applicable temperature line, the value of P can be calculated by the formula: Q'
Q
Pa =
VESSEL WITH STIFFENING RING
2AE 3(D.lt)
When the value of Dolt is less than 10, the formulas given in the Code UG-28(c)(2) shall be applied.
33
EXAMPLES DESIGN DATA
P = IS psig. external design pressure Do = 96 in. outside diatmeter of the sheIl Length of the vessel from tangent line to tangent line: 48 ft. 0 in. = 576 in. Heads 2: I e11ipsoidal Material of shell SA - 285 C plate Temperature 500 0 F E = Modulus of elasticity of material, 27,000,000 psi. @ 500 of (see chart on page 43) Determine the required sheil thickness. Assume a shell thickness: t = 0.50 in. (see page 49) Length L = 592 in. (length of shell 576 in. and one third of the depth of heads 16 in.) LlDo= 592/96=6.17 D/I= 96/0.5 = 192 A=0.00007 from chart (page 42)determined by the procedure described on the facing page. Since the value of A is falling to the left of the applicable temperature-line in Fig. CS-2 (pg. 43), P" _ 2AE/3(D/ I) = 2 x 0.00007 x 27,000,000/3 x 192 = 6.56 psi. Since the maximum allowable pressure Pais smaller than the design pressure P stiffening rings shall be provided. Using 2 stiffening rings equally spaced between the tangent lines of the heads, Length of one vessel section, L = 200 in. (length of shell 192 in. plus one third of depth of head 8 in.)
.
..,-1
co
\0
B = 3000 from chart (page 43 )
"0 ,
determined by the procedure described on facing page.
-
I::
'",
II::
'"
I-
" •'-Ci
"0
co
'00 v
'-Ci
~\... ~
V
N
..j
Jco
Dolt = 96/0.5 = 192 LlD.= 200/96 = 2.08 A = 0.00022 from chart (page 42)
Po = 4B/3(D/I)
= 4 x 3000/3 x
192 = 20.8 psi.
Since the maximum allowable pressure Po is greater than the design pressure P, the assumed thickness of shell using two stiffening rings, is satisfactory. See page 40 for design of stiffening rings.
34
EXTERNAL PRESSURE FORMULAS NOTATION P External design pressure psig. P Maximum allowable working pressure psig. Do Outside diameter of the head, in. Ra Outside radius of sphere or hemisphereical head, O.9Do for ellipsoidal heads, inside crown radius of flanged and dished heads, in. t Minimum required wall thickness, inches. E Modulus of elasticity of material, psi. (page 43) Q
SPHERE and HEMISPHERICAL HEAD The maximum p = B allowable pressure: (Ro / I) The value of B shall be determined by the following procedure: 1. Assume the value for t and calculate the value of A using the formula: AF--Q. 125/( R n / I ) (see page 49) 2. Enter the applicable material chart (pages 43-47) at the value of A. Move vertically to the applicable temperature line. * 3. From the intersection move horizontally and read the value of B. *For values of A faIling to the left of the applicable temperature line, the value of Pa can be calculated by the formula:P n = O.0625E/{R o I t)~ If the maximum allowable working pressure P computed by the formula above, is smaller than the design pressure, 'a greater value for t must be selected and the design procedure repeated. Q
Q
2:1 ELLIPSOIDAL HEAD The required thickness shall be the greater ot the following thicknesses. (1) The thickness as computed by the formulas given for internal pressure using a design pressure 1.67 times the external pressure and joint efficiency E =1.00. (2) The thickness proofed by formula Pa= BIRo It whereR,,=0.9 Du , and B to be determined as for sphere.
ASME FLANGED AND DISHED HEAD TORISPHERICAL HEAD
The required thickness and maximum allowable pressure shall be computed by the procedures given for ellipsoidal heads. (See above)Romaximum=D"
35
EXAMPLES DESIGN DATA:
P = 15 psig external design pressure Do = 96 inches outside diameter of head Material of the head SA-285C plate 500 0 F design temperature
Determine the required head thickness. SEE DESIGN DATA ABOVE Assume a head thickness: A
=
Ro
= 48.00 in.
0.125/( 48.00/0.25)~0.00065
From Fig. CS-2 (page 43) B facing page. Pa
t. = 0.25 in.
=
8500/(48.00/0.25)
=
8500 determined by the procedure described on the
= 44.27 psi.
Since the maximum allowable working pressure Pais exceedingly greater than the design pressure P, a lesser thickness would be satisfactory. For a second trial, assume a head thickness: t = 0.1.875 in. Ro = 48.00 in. A B
= 0.125/(48.00/0.1875) = 0.0005 = 6700, from chart (page 43), Pa = BI(R/I) = 67001256 = 26.2 psi.
The assumed thickness: t = 0.1875 in. is
SEE DESIGN DATA ABOVE.
sati~factory.
Procedure (2.)
Assume a head thickness: (= 0.3125 in.. Ru = 0.9 x 96 = 86.4 in. A = 0.125/(86.4/0.3125) = 0.00045 B = 6100 from chart (page 43 ),p .. - BI(Ra/ 1)1= 6100/276 = 22.1 psi. Since the maximum allowable pressure p .. is greater than the design pressure P the assumed thickness is satisfactory.
SEE DESIGN DATA ABOVE. Procedure (2.) Assume a head thickness: t =0.3125 in., Ra=.Do = 96 in. A =0.125/(96/0.3125) =0.0004 B = 5200 from chart (page 43), P = BI (Ro / t) = 5200/307 = 16.93 psi. Q
Since the maximum allowable pressure p .. is greater than the design pressure P the assumed thickness is satisfactory.
36
EXTERNAL PRESSURE FORMULAS CONE
AND
CONICAL SECfION
Seamless or with Bull Joints
WHEN a IS EQUAL TO OR LESS THAN 60· and Dlte ~ 10 The maximum allowable pressure:
P"
=
48 3(D,/t,.)
I. Assume a value for thickness,
I~
The values of B shall be determined by the following procedure: 2. Determine fe' Lt<, and the ratios Lei DJ and
Dltt 3. Enter chart G (page 42) at the value of LI D, (LID,) (Enter at 50 when LID, is, greater than 50) Move horizontally to the lme representing Dr/t. From the point of intersection move vertically and read the value of A. 4. Enter the applicable material chan at
NOTATION A B a
determined from = factor fig.UGO-2B.O (page 42
factor determined from = charts (pages 43-47) = one half of the included
(apex) angle, degrees D{= outside diameter at the large end, in. D.= outside diameter at the small end, in. E = modulus of elasticity of material (page 43) L = length of cone, in. (see page 39) Le = equivalent length of conical section, in.(L/2)(l +DsfDt ) external design pressure, P psi. Pa = Maximum allowable working pressure, psi t minimum required thickness, in. effective thickness, in. te
=
= = =t cos a
the value of A· and move vertically to the line of applicable temperature. From the intersection move horizontally and read the value of B . S. Compute the maximum allowable working pressure, P /I • If P /I is smaller than the design pressure, the
design, the design procedure must be repeated increasing the thickness or decreasing L by using of stiffening rings. -For values of A falling to the left of the applicable line, the value of P can be calculated by the formula:
P" - 2A£/3(D,II,.) For cones having D /t ratio smaller than 10, see Code UG-33 (O(b) WHEN a IS GREATER THAN 60° The thickness of the cones shall be the same as the required thickness for a flat head. the diameter of which equals the largest outside diameter of the cone. Provide adequate reinforcing of the cone-tocylinder juncture. See page I S9
37
EXAMPLES DESIGN DATA
P = 15 psi external design pressure Material of the cone SA 285-C plate 500 F design temperature CONICAL HEAD O(
=
96 in.
Ds =0
a = 22.5 degrees
Determine the required thickness, t Length, L = (O,I2)/tana= 48/ .4142 = 115.8, say 116 in 1. Assume a head thickness, t, 0.3125 in. 2.te =t cosa=0.3125 x .9239 = 0.288; L~ =Ll2 (l+D lOt> = 11612 x (1 + 0/96) = 58 L./O,=58/96 =0.6 D(lle = 96/.288 = 333 3. A = 0.00037 (from chart, page 42) 4. B = 5,200 (from chart, page 43) 5
_
. P" -
48 3(/),/(,)
D,
4 x 5,200 20 8 . 3(333) = . pSI.
Since the maximum allowable pressure is greater than the design pressure, the assumed plate thickness is satisfactory. CONICAL SECTION (See design data above)
0, = 144 in.
Os =96 in. a =30 deg. Determine the required thickness, Length, L=[(DrD,)I2]/tana =24/.5774=41.6 in. 1. Assume a head thickness, t, 0.375 in. 2. Ie = t cosa.=0.375 x 0.866=0.324
Le=(L/2)(l
+ D/D,) =41.612 x
+ 96/144) = 34.67
(l
LeID, =34.67/144=0.241 D[it e = 144/0.324=444 3. A =0.00065 (from chart, page 42, 4. B = 8,600 (from chart, page 43) 24 144-96 5 _ 48 4 x 8600 2 . p .. - 3(01/t e) 3 X (144/0.324) 144 = 25.8 psi. Since the maximum allowable pressure P is greater than the design pressure P, the assumed thickness is satisfactory. Q
EXAMPLES FOR CONICAL HEAD. WHEN
ex
IS GREATER THAN 60°
ARE GIVEN AT FLAT HEADS
38
NOTES
39
EXTERNAL PRESSURE FORMULAS
t
L
\.-.J~ Use L in calculation as shown when the strength of joints of cone to cylinder does not meet the requirements described on pages 163 - 169 It will result the thickness for the cone not less than the minimum required thickness for the joining cylindrical shell.
l
L
t----IJ f L L
I
Use L in calculation as shown when the strength of joints of cone to cylinder meets the requirements described on pages 163-169
"
40
EXTERNAL PRESSURE DESIGN OF STIFFENING RINGS NOTATION A
:= Factor determined from the chart (page 42) for the material used in the stiffening ring.
As
=
Cross sectional area of the stiffening ring, sq. in.
Do
=
Outside Diameter of shell, in.
E
= Modulus of elasticity of material (see chart on page 43)
Is
=
Required moment of inertia of the stiffening ring about its neutral axis parallel to the axis of the shell, in.4.
I',.
=
Required moment of inertia of the stiffening ring combined with the shell section which is taken as contributing to the moment of inertia. The width of the shell section 1.10 Wt in.4. o
Ls
=
The sum of one-half of the distances on both sides of the stiffening ring from the center line of the ring to the (1) next stiffening ring, (2) to the head line at 113 depth, (3) to a jacket connection, or (4) to cone-to-cylinder junction, in.
P
=
External design pressure, psi.
t
=
Minimum required wall thickness of shell, in.
I. Select the type of stiffening ring and determine its cross sectional area A. II. Assume the required number of rings and distribute them equally between jacketed section, cone-to-shell junction, or head line at 113 of its depth and determine dimension, Ls III. Calculate the moment of inertia of the selected ring or the moment of inertia of the ring combined with the shell section (see page 95). IV. The available moment of inertia of a circumferential stiffening ring shall not be less than determined by one of the following formulas: l' = Do 2L s (t+A/L)A I = Do 2Ls (t+A/L)A \' 10.9 .v 14 The value of A shall be determined by the following procedure: 1. Calculate factor B using the formula:
B= 3/. [ PDo ] , 4 t+AlLs 2. Enter the applicable material chart (pages 43 _A7) at the value of B and move horizontally to the curve of design temperature. When the value of B is less than 2500, A can be calculated by the formula: A = 2BIE. 3. From the intersection point move vertically to the bottom of the chart and read the value of A. 4. Calculate the required moment of inertia using the formulas above. If the moment ofinertia ofthe ring or the ring combined with the shell section is greater than the required moment of inertia, the stiffening ofthe shell is satisfactory. Otherwise stiffening ring with larger moment of inertia must be selected, or the number of rings shall be increased. Stiffening ring for jacketed vessel: Code UG-29 (f)
41
EXAMPLES DESIGN DATA: P = 15 psi, external design pressure. Do = 96 in., outside diameter of the shell. Length of the vessel from tangent line to tangent line: 47 ft. 8 in. = 572 in. Heads 2: 1 ellipsoidal Material of the stiffening ring SA-36 Temperature SOO°F E Modulus of elasticity of material, 27,000,000 psi, @ SOO°F (see chart on page 43) t = 0.500 in. thickness of shell 96" ~
I. An angle of 6 x 4 As = 3.03 sq. in.
N
V 00
in ~
~
-r-.-
~
-.:t
~
~
ctI
-
""\ -
~ rt
f - _ . _ - -f-
-I- -
t-
--
selected.
II. Using 2 stiffening rings equally -.:t ~
- -
spaced between one-third the depths of heads (see figure), Ls = 196 in. III. The moment of intertia of the selected angle: 11.4 in.
~
--~-
\0
00
-.:t
5h6
-
1. The value of Factor B: B = lit [PDol(t + AILs)] = y.. [15x96/(0.S + 3.03/196)] ;:::2095
00
in
2. Since the value of B is less than 2500, A =2BIE= 2 x 209S127,000,000 = 0.00015
IV. The required moment of inertia:
I ;::: [Do 2L s(t+ AslLl A];::: 96 2 x 196 x (O.S + 3.03/196) x 0.00015;::: 997· 4 s 14 14 . m.
Since the required moment of inertia (9 t97 in.4) is smaller than the moment of inertia of the selected angle (11.4 in.4) the vessel is adequately stiffened. Stiffening rings may be subject to lateral buckling. This should be considered in addition to the required moment of inertia. See pages 95-97 for stiffening ring calculations.
42 I
50.0 40.0
P p_p .....0 . 0
35.0
;;- ;--;;
30.0 2S.0
8 g
0;
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FACTOR A
THE VALUES OF FACTOR A USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE
.1
I toI3~J1~ _ I7
I
UP
V
./
V
V
IIi.- i............. V i
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. / .-
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~
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E=24.5xl06 E = 22.8 x 10 6 E = 20.B)( 10 e
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o
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VII
4.000
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-.......,
•• 4-
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.S .........
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3,500
~
3,000
O ..c(])o.. ..... 0.. :z .;::on .S :::l
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r---.... ....... ......
en 0 t<::l ._ ...... u ....... (]) (]) . . . . . c ......
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I
./
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18.000
700 F-
V
C
B E '0
20.000
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.....
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l..- i---'I"""
t.,.....- L-
.- ~
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V J rI
-
25,000
0 ......
~
~
2.500
.1
FACTOR A
THE VALUES OF FACTOR B USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE The values of the chart are applicable when the vessel is constructed of carbon steel and the specified yield strenth 30,000 psi. and over. To this category belong the following most frequently used materials: SA - 283 C SA - 515} II d SA - 53 - B Type 405 } S . I S I SA - 285 C SA - 516 A Gra es SA _ 106 _ B Type 410 tam ess tee
DESIGN
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I i JT up to 300 F
V
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700 F-
16,000
800 F_
14.000
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10,000
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9,000 8,000
./
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I
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t::
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:l0.000 18,000
I I-
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~
./
I
SOO F
25,000
3,000
1
OCJ)~§:
Z '1: ._ ::s
S 6 7 89
2,500 ,1
FACTOR A
THE VALUES OF FACTOR B USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE *The values of the chart are applicable when the vessel is constructed of austenitic steel (18Cr-8Ni, Type 304) (Table 1 on page 190)
25.000
Q)
C
Q)
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.8 S t;
:;>0.000
~ ~ C - ee Vl ._ 0 ee
18.000 up to 100 F
-II
......
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V ~
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./ ~~ ~V ~
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E E E E E
= 28.0 = 25.9 = 23.8 = 22.4 = 20.3
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9il I F
16,000
1,200 F
12.000
4-:':::2 Q) 0-
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FACTOR A
THE VALUES OF FACTOR B USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE *The values of the chart are applicable when the vessel is constructed of austenitic steel (18CR-8Ni-Mo, Type 316)(Table 3 on page 190)
~------------------------------------------------------------------------------------------------~I~
DESIGN
I
I
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vv
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r
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--
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....... 1-"'" ~
f-'""i""'"
f-'""
f-'"~
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9.000
B,OOC
Bod F
7,00e
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5,000
4,000
3,500
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FACTOR A
THE VALUES OF FACTOR B USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE *The values of the chart are applicable when the vessel is constructed of custenitic steel (lSCR-SNI-O, 03 max. carbon, Type 304L) (Table 2 on page 190)
;...
B
...... Q) 0 ro ~ ...... ..s:::: ~ Q) Q) Q) 0. ..s::::-:5..s::::a ~ 4- ...... Q) o ..s:::: ...... U'J ...... Q) Q) "'0 .- ..s:::: U'J s:: ~ ...... ro Q) 4U Q) s:: 0 s:: ..s::::.S "'0 ~ c:: .. 4-UQ) ~ 0 ~ ;... E-o ...... ;... Q) ..s::::Q)o. O OJ)...... 0. .......-Ij
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I
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Q) s:: Q) ..s::::ro..s:::: ...... Q) ......
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..- I -
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9.000 8.000
7.000 6.000
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12.000
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111
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up to 100 F
/I,.,.
r-.
1II
~
~r-
...... V
-
~ r-
fo-" ........
...... ~~
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V rJ
...... ,.,..
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J 1J j
(\)
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FACTOR A
THE VALUES OF FACTOR B USED IN FORMULAS FOR VESSELS UNDER EXTERNAL PRESSURE *The values of the chart are applicable when the vessel is constructed of austenitic steel (I SCR-SNi-Mo-O.03 max. carbon, Types 316L and 317L) (Table 4 on page 190)
~------------------------------------------------------------------------------------~I~
DESIGN
48
EXTERNAL PRESSURE CONSTRUCTION OF STIFFENING RINGS LOCATION Stiffening rings may be placed on the inside or au tside of a vessel.
SHAPE OF RINGS The rings may be of rectangUlar or any other sections.
CONSTRUCTION It is preferable to use plates in constructing a composite-section stiffener ring, rather than using standard structural shapes. The reason for this lies not only in the difficulties of rolling heavy structural shapes, but also because of the necessity to adjust the ring to the curvature of the shell. For large diameter vessels the maximum permissible out of roundness can result in a 1 - 2 inch gap between the shell and the ring. This can be eliminated if the vertical member of the ring is cut out of the plate in sections. The sections can be flame cut, instead of rolled and then butt-welded together in place.
DRAIN AND VENT Stiffener rings placed in the inside of horizontal shells have a hole or gap at the bottom for drainage and at the top for vent. Practically one half of a 3 inch diameter hole at the bottom and I V2 inch diameter hole at the top is satisfactory and does not affect the stress conditions. Figure A. For the maximum arc of shell left unsupported because of gap in stiffening ring, see Code Figure UG.29.2.
WELDING According to the ASME Code (UG 30): Stiffener rings may be attached to the shell by continuous or intermittent welding. The total length of intermittent welding on each side of the stiffener ring shall be: 1. for rings on the outside, not less than one half the outside circumference of the vessel; 2. for rings on the inside of the vessel, not less than one third of the circumference of the vessel.
Where corrosion allowance is to be provided, the stiffening ring shall be attached to the shell with continuous fillet or seal weld.ASME. Code (UG.30.) Max. Spacing 12 t for internal ring 8 t for external ring
Figure A EXAMPLE:
RINGS OUTSIDE RINGS INSIDE
1
J: Figure B
Y4" x 3" 19. fillet weld on 6" ctrs. Y4" x 2" 19. fillet weld on 6" ctrs.
The fillet weld leg-size shall be not less than the smallest of the following: 1/4 in, the thickness of vessel wall or stiffener at the joint.
49
CHARTS FOR DETERMINING THE WALL THICKNESS FOR FORMED HEADS SUBJECTED TO FULL VACUUM Using the charts, trials with different assumed thicknesses can be avoided. The charts has been developed in accordance with the design method of ASME Code, Section VIII, Division 1. . 70 .65
.60 .55
300 .50
.45
:~ Y
1
i~ 700 •
.40
Isoo .35 'JIll
. 30
&
.
. i,;.l. I
.25 .20
.....
. 15
•
.10
.05
.00 10 20
30
40
50
60
70
80
90
100 110 120 130140 150 160170 180 190200
SPHERICAL, ELLIPSOIDAL, FLANGED AND DISHED HEADS (Specified yield strength 30,000 to 38,000 psi, inclusive) To find the required head thickness: 1. Determine R, 2. Enter the chart at the value of R, 3. Move vertically to tempeTature line, 4. Move horizontally and read t.
t R
Do
Required head thickness, in. For hemispherical heads, the inside radius, in. For 2: 1 ellipsoidal heads 0.9xDo For flanged and dished heads, the inside crown radius, in. Rmax=Do Outside diameter of the head, in.
50
CHARTS FOR DETERMINING THE WALL THICKNESS FOR VESSELS SUBJECTED TO FULL VACUUM
I'" 500.
.0-. .~~
EO.
~ ~ f---
300 of ....-- c-- c- 500 of ~" ~~f'-.,. ....... f- -700 of ~ ,./ ..--800 of "~ ~ .;;:< 0 ~ ~ 900 of ~ ~ ~ ./ NK~ ~~ ~ ~~~ -.....:::: ~~
400.
"'' '\
ns.
215.
315.
215.
"""
115.
3
..
130.
120.
10.
50.
&
1
~
•
I.
2
3
4
5
&
LID
~
iJj ~ ~1 /1 I~ 1I 11/ I I / I / ~t.: /1/// ~ ~ bI fcI I i / / / / V //; ~/; ~/ II't~Vi 10/' leo.: ¥.1 j' ./ / / / v VI V V / W2 ~VI 'II J y l?~I ~ W 0 ~ j / / /;/ .;// / / / yv ~ ~v/ / V / L/ ? ~ V / ~/ / / / / J v v .~ ~ / . /V /' / ......./ ' / .~ v .........-v /"..,/ .........- ~ --::v k ..-vV .--
«
,/
125.
100.
10.
!/
140.
~
5
I rlJ '/ ,/1/ / If I /' II' / II VJ II, 11/II II I I I I I I I I I I Ij~ III Z ,/1 If I I / V / / _1/ -~ ~ (II 'II IlL illl II J I II / I
150.
100.
150.
--..::::::~~
125.
100.
115.
~ ~~
I !SO.
150.
If'
140.
130.
120.
110.
100.
~.
80.
10.
e
T
•
---
0
A
CYLINDRICAL SHELL (See facing page for explanation)
5
~
0 ....l ....l
"':t"
[/)
.... &0-
0
:t 50.
40.
30.
EU Z
"'....l" II
.....l 20.
I-"'
5
U
"'"
,./
..
Z 0 1= [/)
,/
..,-
i
e
7
•
Q
10. 10.
51
CHARTS FOR DETERMINING THE WALL THICKNESS FOR VESSELS SUBJECTED TO FULL VACUUM .10
.1$
.20
.25
.30
.35
.45
.4)
.50
.eo
.55
.&5
.70
.15
.80
.85
,go
.SJ5
S2S. 500.
415. A6O. oG5.
400.
315. 350.
.....
-0 0
325. lOO.
215. 250. 225. 200.
115. ISO.
\ \ \\ \\ \\ l\ \ i\ \ 1\ \ 1\ \ 1\ \ 1\\ .~. \ \ ~\ 1\ \ 1,\ \ Io~ .f€. !\ \ \ \ 1\.\ ~~ ~. ~~ -1 1\ \ \ \ 1\ \ \ ~ ~~ ~~ I'<.,~ ~ \ \ \ 1\ \ 1\" f<1."<. ~'" v'~ ""-" ~ \ \ 1\ \ \ I\o~ .~ ~" ~'" ~ f'o..-~ ~ ~ f'o..-""-.. ~ ~ ~\ \ \ \ 1\ ~ "~ ~~ ~' ~ ~ ~ "'-....' '""""""- 0 f'<..' ~ \ \ f\ -~ 1' -.""" \b '" ,,"""- ~ ~ ~ ~ t': ~ f'o..-" \ \ ~ ~. ~ f\v ~ r-... ..... \ \ \ \ 1\ \ 1\ \ \ \ \ \ ~\ \ \ \
'y
\
'\ .}
\ ~.
1\.,.,.
~ ~ .10
.15
.20
~
'\ rx ~
'\
\: '\
125. 100.
~,.,
1'0
§\
.>
"""
""
,25
r-....., .30
~
"" ~
f'o..-
'" " '" "" '""" t-..... ......... t-.....
~ r--....
.............. 1--..
~ .35
.4)
.45
'"
"" ."" ""
,"""I"-.. ~'
"'-....
"r--
"
~ .............. r-.............. ........
r---
...............
I--I-- r-.:::-....... i--- r--. r-... r--
['---...... '-.....
'"-...
r-- h-. r-- 1-;,.,.. r--- ~
.SO
.55
500.
415.
315.
215.
~...... --......:::~ ~ r--:::: ~ I'--..... ~ :::-...... ~ ~ r--:::: ~
""--
i'--.
1.00 S2S.
.eo
.e5
.10
.15
I--
r::- r-::: r-- .:::=
-- --
------ r-- ::----
.80
~=
~
.85
,go
.Q5
115.
,so. '25. '00. 1.00
t = REQUIRED SHELL THICKNESS, IN.
CYLINDRICAL SHELL
(Specified yield strength 30,000 to 38,000 psi, inclusive) To find the required shell thickness: 1. Enter lower chart (facing page) at the value of L 2. Move horizontally to curves representing Do 3. Move vertically to temperature line 4. Move horizontally and read Dolt 5. Enter chart above at the value of Dolt 6. Move horizontally to curve D 7. Move vertically down and read the value of t NOTATION Do L
Required shell thickness, in. Outside diameter of shell, in. Length of the vessel or vessel section, taken as the largest of the following: 1. Distance between the tangent lines of the heads plus one third of the depth of the heads if stiffening rings are not used, in. 2. The greatest distance between any two akjacent stiffening rings, in. 3. The distance from the center of the first stiffening ring to the head tangent line plus one third of the head depth, in.
The charts are from: Logan, P. 1., "Based on New ASME Code Addenda ... Chart Finds Vessel Thickness," HYDROCARBON PROCESSING, 55 No.5, May 1976 p. 217. Logan, P. J., "A Simplified Approach to . . . Pressure Vessel Head Design," HYDROCARBON PROCESSING, 55 No. 11, November 1976 p. 265. Copyrighted Gulf Publishing Co. Houston. Used with permission.
52
DESIGN OF TALL TOWERS WIND LOAD The computation of wind load is based on Standard ANSIIASCE 7-95, approved 1996. The basic wind speed shall be taken from the map on the following pages. The basic wind speed is 105 mph. in Hawaii and 125 mph. in Puerto Rico. The minimum design wind pressure shall not be less than 10 lb.lsq. ft. When records and experience indicates that the wind speeds are higher than those reflected in the map, the higher values of wind speed shall be applied. The wind pressure on the projected area of a cylindrical tower shall be calculated by the following formula. F = qz G e{A{
Table 6-1 ANSI/ASCE 7-95 STANDARD (Numbers of tables and paragraphs are references to this Standard.)
L
(D x H)
I
I
Projected area oft ower, sq. ft. height oflower considered. ft. outside diameter of tower, ft.
L...-_ _
Shape factor = 0.8 for cylindrical tower (Table 6-7)
'---- Gust response factor = (G h & GJ* (Para. 6.6) When the tower is located: in urban, suburban areas, Exposure B 0.8; in open terrain with scattered obstruction, Exposure in flat, unobstructed areas, Exposure D 0.85. L...-_ _ _
e 0.85;
Velocity pressure at height z above ground, lb.lsq. in. 0.00256 KzKzt V2 I, lb./sq. ft. (Table 6-1)
II
~ Design Wind Force. lb. on projected area of tower. (Para. 6.2)
Importance factor ~ 1. 0 for structures that present low hazard to human life in event offailure (Para. 6.2). Wind speed, mph. (Map 6-1)
'- Topographic factor = 1.0 when wind speed-up over hills and escarpment is not present. (Para. 6.5.5) '--
Velocity Pressure Exposure Coefficient* Exposures B, e & D (Table 6-3) * See tables below for values of q and for combined values of Gh, G z, and Kz in Exposures B, e, and D. VELOCITY PRESSURE, q Basic wind speed, mph, V 1 70 I 80 I
J120 I
37
1130 44
I
I I
53
DESIGN OF TALL TOWERS WIND LOAD (Continued)
COEFFICIENT G (Gust response factor combined with Exposure Coefficient) HEIGHT Above Ground, ft. 0-15 20 40 60 80 100 140 200 300 500
EXPOSUREB 0.6 0.7 0.8 0.9 1.0 1.1 1.2 1.4 1.6 1.9
EXPOSUREC 1.1 1.2 1.3 1.4 1.5 1.6 1.7 1.9 2.0 2.3
EXPOSURED 1.4 1.5 1.6 1.7 1.8 1.9 2.0 2.1 2.2 2.4
The area of caged ladder may be approximated as 1 sq. ft. per lineal ft. Projected area of platform 8 sq. ft. Users of vessels usually specify wind pressure for manufacturers without reference to the height zones or map areas. For example: 30 lb. per sq. ft. This specified pressure shall be considered to be uniform on the whole vessel. The total pressure on a tower is the product of the unit pressure and the projected area of the tower. With good arrangement ofth-e equipment, the exposed area of the wind can be reduced considerably. For example, by locating the ladder 90 degrees from the vapor line. EXAMPLE: Determine the wind load, F DESIGN DATA: the wind speed, V
= kOOm.p.h
= 6 ft. diameter of tower, D = 80 ft. height of tower, H the tower located in flat, unobstructed area, exposure: D
I
I
The wind load, F=qz xG x CI AI = q from table = G from table = Shape factor
26 psf 1.8 0.8
Area, Ar= DH = 6 x 80 = 480 sq. ft. F = 26 x 1.8 x 0.8 x 480 = 17,971 lbs.
54
MAP OF WIND SPEED, V (miles per hour)
Alaska Note: For coastal areas and islands, use nearest contour.
. \140 100 130 110120
ANSI/AASCE STANDARD 7-95 Courtesy of American Society of Civil Engineers
55
MAP OF WIND SPEED, V (miles per hour)
90 100 110 120
Special Wind Region •
Population Center
Location Hawaii Puerto Rico Guam Virgin Islands American Samoa Notes: 1. Values are 3-second gust speeds in miles per hour at 33 ft. above ground for Exposure C category and are associated with an annual probability of 0.02. 2. Linear interpolation between wind speed contours is permitted. 3. Islands and coastal areas shall use wind speed contour of coastal area. 4. Mountainous terrain, gorges, ocean promotories, and special wind regions shall be examined for unusual wind conditions.
V, mph 105 125 170 125 125
56
DESIGN OF TALL TOWERS WIND LOAD Computation of wind load as alternate method based on standard ASA A5S.1-1955. This standard is obsolete but still used in some codes and foreign countries. The wind pressure at 30 ft. level above ground for the United States is shown on the map on the facing page. The table below gives the wind pressures for various heights above ground for the areas indicated by the map. WIND PRESSURE Pw WHEN THE HORIZONTAL CROSS SECTION SQUARE OR RECTANGULAR* MAP AREAS HEIGHT ZONE ft. 20 25 30 40 45 50 35 25 40 25 30 35 less than 30 15 20 30 35 40 45 50 30 to 49 20 25 45 50 55 60 50 to 99 25 30 40 45 55 60 70 75 100 to 499 30 40
*Multiply values of P w with O.SO when the horizontal cross section is hexagonal or octagonal and with 0.60 when the horizontal cross section is circular or elliptical.
EXAMPlE:
Find the wind pressure P w from map. The vessel is intended to operate in Oklahoma, which is in the wind pressure map area marked 30. In this map area the wind pressures for various height zones are: In the height zone less than 30 ft.
25 lb. per sq. ft.
In the height zone from 30-49 ft.
30 lb. per sq. ft.
For a cylindrical tower these values sha11 be multiplied by shape factor 0.6, then the wind pressure in different zones will be 15 and IS lb. per sq. ft. respectively If many pieces of equipment are attached to the tower it is advisable to increase the shape factor (according to Brownell) up to 0.S5 for a cylindrical vessel. Users of vessels usually specify the wind pressure for manufacturers without reference to height zones or map areas. For example: 30 lb. per sq. ft. This specified pressure shall be considered to be uniform on the whole vessel. Relation between wind pressure and wind velocity, when the horizontal cross section is circular, is given by the formula: P w = 0.0025 x Vw 2
where
P w = wind pressure lb. per sq. ft. Vw = wind velocity mph
EXAMPLE:
Wind of 100 mph velocity exerts a pressure: P w = 0.0025 x Vw 2 = 25 lbs. per sq. ft. pressure on the projected area of a cylindrical vessel at a height of 30 feet above ground. The total wind pressure on a tower is the product ofthe unit pressure and the projected area of the tower. With a good arrangement of equipment the exposed area of the wind can be reduced considerably. For example, by locating the ladder 90 degrees from the vapor line.
___
___
.. ___
I 110·
-----1-I -.~-
'3·
li:
a::
~
o
Io!j
~
Z
CI
~
~
m
en en
e
~
m i • • • SANTA ANA WINDS - . - CHINOOK WINDS AAA
COl.UMBIA RIVER GORGE WINDS
• • • WASATCH MOUNTAIN WINDS
ALLOWABLE RESULTANT WIND PRESSURES COMIINEO INWARD AND OUTWARD I'RESSURES U G:O : : : - - , ----10".~.
:~I~:;r..EGR~ORA~U.:~C~~:: O::~~~RT
\
~~. VI
The map based on the records of the United States Weather Bureau and developed by the National Bureau of Standards.
DESIGN
-...l
58 DESIGN OF TALL TOWERS
WIND LOAD (Continuation) FORMULAS SHEAR
MOMENT
. REQUIRED STRI<,SS THICKNESS
t=
12M R 2 nSE
NOTATION
H
hi
~_..L.h·~r_:~ :~
= Width of the vessel with insulation etc., ft. D[D2 = Efficiency of the welded joints. E = Lever ann, ft. h[h2 = Distance from base to section under consideration, ft. hT H,H[H2 = Length of vessel or vessel section, ft. = Maximum moment (at the base) ft. lb. M = Moment at height hT, ft. lb. MT Pw
= Wind pressure, lb. per sq. ft.
R
=
S
= Stress value of material or actual stress psi.
V t
Mean radius of vessel, in.
= Total
shear, lb.
= Required thickness, corrosion excluded, in.
EXAMPLE: Given: D[ = 4'-0" D2 = 3'-0" H[ = 56'-0" H2 = 44'-0" hT = 4'-0" P w = 30 psf Determine the wind moment hI = HI12 = 28'-0" h2 = HI + (H212) = 78'-0" Pw x D x H = V x h = M Lower 30 x 4 x 56 = 6720 x 28 = 188,160 Section Upper Section - 30 x 3 x 44 = 3,960 x 78 = 308,880 V = 10,680 M 497,040 ft. lb. Total
J 2
Moment at the bottom tangent line MT = M - hT (V - 0.5 P wD j hT) = 497,040 - 4 (10,680 - 0.5 x 30 x 4
1£1
~
3' -6"
•
I;:..!...I
7t[)1
t-~/ t ,......,.. "0 "0
'"
-l
..... o c. o f-o
II
:t:
Platform
x 4) = 455,280 ft. lb.
EXAMPLE: Given: D j = 3 ft. 6 in. H = 100 ft. 0 in. P w = 30 psf Determine the wind moment hI = HI2 = 50 ft. 0 in.
hT
=
v X hI = PwxDjxH= = 10,500 x 50 = Vessel 30 x 3.5 x 100 = 2,940 = 49 = Ladder 30 x 98 lin. ft. = 240 x 96 = Platform 30 x 8 lin. ft. V = 13,680 M = Total Moment at the bottom tangent line Mr = M - hr (V - 0.5 P w D j hr ) = 692,100 - 4 (13,680 - 0.5 x 30 x 3.5 x 4) =
4 ft. 0 in.
M 525,000 144,060 23,040 692,100 ft. Ib
638,220 ft. lb. SEE EXAMPLES FOR COMBINED LOADS ON PAGE: 69
59 DESIGN OF TALL TOWERS
WEIGHT OF THE VESSEL The weight of the vessel results compressive stress only when eccentricity does not exist and the resultant force coincides with the axis of the vessel. Usually the compression due to the weight is insignificant and is not controlling. The weight shall be calculated for the various conditions of the tower as follows: A. Erection weight, which includes the weight of the: Equipments:
I. shell
2. 3. 4. 5. 6. 7. 8. 9. 10.
heads internal plate work tray supports insulation rings openings skirt base ring anchor ring anchor lugs II. miscellaneous 12. + 6% of the weight of items I through II for overweight of the plates and weight added by the wei dings
13. 14. 15. 16. 17. 18.
insulation fireproofing platform ladder piping miscellaneous
Erection weight: the sum of items 1 through 18. B. Operating weight, which includes the weight of the: I. vessel in erection condition 2. trays 3. operating fiquid
c.
Test weight, which includes the weight of the: I. vessel in erection condition 2. test water
The compressive stress due to the weight given by:
s=
w et
where
S = unit stress, psi W = weight of vessel above the section under consideration, lb. e = circumference of shell or skirt on the mean diameter, in. t = thickness of the shell or skirt, in.
The weight of different vessel elements are given in tables beginning on page- 374
DESIGN OF TALL TOWERS
VIBRATION As a result of wind, tall towers develop vibration. The period of the vibration should be limited, since large natural periods of vibration can lead to fatigue failure. The allowable period has been computed from the maximum permissible deflection. The so called harmonic vibration is not discussed in this Handbook since the trays as usually applied and their supports prevent the arising of this problem. FORMULAS
Period of Vibration:
T sec.
T= 0.0000265
Maximum Allowable Period of Vibration, Ta sec.
~=O.80
(-ff)2 P,
~WH ~
NOTATION D = Outside diameter of vessel, ft. H = Length of vessel including skirt, ft. g
= 32.2 ft. per sec. squared, acceleration
t = Thickness of skirt at the base, in. V = Total shear, lb. Cw, see page 61 W = Weight of tower, lb. w =
Weight of tower per foot of height, lb.
EXAMPLE Given:
Determine the actual and maximum allowable period of vibration
D = 3.125 ft. 0 in. H = 100 ft. 0 in.
= 32.2 ft/sec 2 t = 0.75 in. V = 1440 lb. W = 36,000 lb. in operating condition w = 360
g
T=0.0000265(100:?
\3.125)
..y 360x3.125 0.75
_/36000 x 100
Ta=0.80 \I 1440x32.2
= 1.05 sec.
=7.05 sec.
The actual vibration does not exceed the allowable vibration.
Reference: Freese, C. E.: Vibration of Vertical Pressure Vessel ASME Paper 1959.
61 DESIGN OF TALL TOWERS
SEISMIC LOAD (EARTHQUAKE) The loading condition of a tower under seismic forces is similar to that of a cantilever beam when the load increases uniformly toward the free end. The design method below is based on Uniform Building Code, 1997 (UBC). FORMULAS SHEAR
F,~!
V-F,
M= {Ft X H + (V - Ft ) X (2HI3)] Mx={FtXX] forX::S HI3
~/
Hh
I
Mx ={Ff X H + (V - Ff ) X (X-HI3)]
t JH
-LJ (a) Seismic Loading Diagram
MOMENT
for X> HI3
Base Shear The base shear is the total horizontal seismic shear at the base of a tower. The triangular loading pattern and the shape of the tower shear diagram due to that loading are shown in Fig. (a) and (b). A portion of F t of total horizontal seismic force V is assumed to be applied at the top of the tower. The remainder of the base shear is distributed throughout the length of the tower, including the top. Overturning Moment The overturning moment at any level is the algebraic sum of the moments of all the forces above that level. NOTATION -' N . I ffi' C = umenca coe IClent = 2.355 T2i3 (need not exceed 2.75) C = Numerical coefficient = 0.035
I.
D=Outside diameter of vessel, ft.
v
.1
(b) Seismic Shear Diagram
Base Shear
E = Efficiency ofweldedjoints
F f = Total horizontal seismic force at top ofthe vessel, lb. determined from the following formula: F f = 0.07 TV (Ff need not exceed 0.25 V)
=0, for T :sO. 7 H = Length of vessel including skirt, ft.
62 DESIGN OF TALL TOWERS
SEISMIC LOAD (EARTHQUAKE) (Continuation)
NOTATION I
= Occupancy importance coefficient (use 1.0 for vessels)
M = Maximum moment (at the base), ft-lb.
Mx = Moment at distance X, ft-lb. R = Mean radius of vessel, in.
Rw = Numerical coefficient (use 2.9 for vessels) S
.. D
= Site coefficient for soil characteristics
A soil profile with either: a) A rock-like material characterized by a shear-wave velocity greater than 2,500 feet per second or by other suitable means of classification. S = 1.0
I
b)Stiff or dense soil condition where the depth is less than 200 ft. S = 1. A soil profile with dense or stiff soil conditions, where the soil depth exceeds 200 feet. S = 1.2. A soil profile of 40 feet or more in depth and containing more than 20 feet of soft to medium stiff clay, but not more than 40 feet of soft clay. S = 1.5. A soil profile containing more than 40 feet of soft clay. S = 2.0. = Allowable tensile stress of vessel plate material, psi. =
Fundamental period of vibration, seconds
=c t xH%
= Required corroded vessel thickness, in.
v
= Total seismic shear at base, lb.
W = Total weight of tower, lb. X
= Distance from top tangent line to the level under consideration, ft.
Z
= Seismic zone factor, 0.075 for zone 1 0.15 for zone 2A 0.2 for zone 2B 0.3 for zone 3 0.4 for zone 4 (see map on the following pages for zoning).
63 DESIGN OF TALL TOWERS
SEISMIC LOAD (EARTHQUAKE) EXAMPLE
Given: Seismic zone: 2B
Z=O.2
D = 37.5 in. = 3.125 ft.
X= 96 ft,. 0 in.
H= 100 ft., 0 in.
W= 35,400 lb.
Determine: The overturning moment due to earthquake at the base and at a distance X from top tangent line. First, fundamental period of vibration shall be calculated. T=C xHY4=0.035 x 100 314 = 1.1 sec. t
and
1=1,
S=1.5, Rw=2.9,
C= 1.25S = 1.25 x 1.5 = 1.76<2.75 T213 1.1213 V= ZIC x W= 0.2 x 1 x 1.76 x 35,400=4,296 lb. Rw 2.9
Ff = 0.07 TV = 0.07 x 1.1 x 4,296 = 330 lb. M= [FfH + (V - F f ) (2HI3)] =
[330 x 100 + (4,296 - 330)(2 x 100/3)] = 294,756 ft. - lb. X >
If-' thus
Mx = [Ff X+ (V-Ff ) (X - HI3)] =
[330 x 96 + (4,296 - 330) (100-33)] = 281,138 ft. -lb.
64
SEISMIC ZONE MAP OF THE UNITED STATES
... ... er, 0'1
U
== ~ ~
=
~
:I
f"I
a..
~ C. C':I
.c:
'! :aU = ~
~
c. c.
-< '"
"0
0
.~
•
~ .\ ·c~ ~
.c: .... ~
~
:s.... '"
= =
'"C':I ~
C':I
a..
~
65
66 DESIGN OF TALL TOWERS
ECCENTRIC LOAD
Towers and their internal equipment are usually symmetrical around the vertical axis and thus the weight of the vessel sets up compressive stress only. Equipment attached to the vessel on the outside can cause unsymmetrical distribution of the loading due to the weight and result in bending stress. This unsymmetrical arrangement of small equipment, pipes and openings may be neglected, but the bending stresses exerted by heavy equipment are additional to the bending stresses resulting from wind or seismic load.
FORMULAS
~. . I
MOMENT M= We
I
i
I
w
e
=
E M
= = = =
R
S t W
= =
STRESS
REQUIRED THICKNESS 12We
S_12We -nR2(
(=
R 1 n SE
NOTATION Eccentricity, the distance from the tower axis to center of eccentric load, ft. Efficiency of welded joints. Moment of eccentric load, ft. lb. Mean radius of vessel, in. Stress value of material, or actual bending stress, psi Thickness of vessel, excluding corrosion allowance, in. Eccentric load, lb.
EXAMPLE Given:
e R t W
= = = =
4 ft. 0 in. 15 in. 0.25 in. 1000 lb.
Determine moment, M, and stress, S. Moment, M = We = 1000 X 4 = 4000 ft. lb. 12 X 1000 X 4 12 We S=---= = 272 psi 3.14 X 15 2 X 0.25 'IT R2 t
When there is more than one eccentric load, the moments shall be summarized, taking the resultant of all eccentric loads.
67
Design of Tall Towers ELASTIC
STABILITY
A tower under axial compression may fail in two ways because of instability: I. By buckling of the whole vessel (Euler buckling) 2. By local buckling In thin-walled vessels (when the thickness of the shell is less than one-tenth of the inside radius) local buckling may occur at a unit load less than that required to cause failure of the whole vessel. The out of roundness of the shell is a very significant factor in the resulting instability. The formulas for investigation of elastic stability are given in this Handbook, developed by Wilson and Newmark. Elements of the vessel which are primarily used for other purposes (tray supports, downcomer bars) may be considered also as stiffeners against buckling if closely spaced. Longitudinal stiffeners increase the rigidity of the tower more effectively than circumferential stiffeners. If the rings are not continuous around the shell, its stiffening effect shall be calculated with the restrictions outlined in the Code UG-29 (c). FORMULAS ALLOWABLE STRESS (S)
Without Stiffener Ay
. Id . ) 1 500 ,000 Iit (= S =, <"31 yte pomt
•
dy
!
i
l
~ S I Ix
=
= 18 in. = 0.25 in.
R I
Given:
Ay dy
= =
y
=
t
1 sq. in. 24 in.
.~ The equivalent thickness of the shell when circumferentially d stiffened, in. y
EXAMPLE Determine the allowable compressive stress (S)
1
+ 0.04
1,500,000 x R
I
=
1,500,000 x 0.25 20 833 18 =,
Determine the allowable compressive stress stiffener rings S
+ -24 =
= 0.25
+
S =
Longitudinal stiffener is not used, then: Ix = t = 0.25 in. I
~ (= 1 . Id ) = 1,500,000 R "tytx <"3 yte P•
NOTATIONS: Cross sectional area of one logitudinal stiffener, sq. in. Cross sectional area of one circumferential stiffener, sq. in. Distance between logitudinal stiffeners, in. Distance between circumferential stiffeners, in. Mean radius of the vessel, in. Allowable compressive stress, psi Thickness of shell, in. Ax The equivalent thickness of the shell when longitudinally I + d; stiffened, in .
Iy = t
Given:
S
= = = == = == =
Ax Ay dx
J
!
With Stiffener
=
using
1,500,000 ~ =
R
yx
1 500 000 , 1~ VO.25 x 0.29 =
(S)
. pSI
= 22.438
PSI
0.29
Reference: Wilson, W. M., and Newmark N. M.: The Strength of Thin Cylindrical Shells as Columns, Eng. Exp. Sta. Univ. Ill. bull. 255, 1933.
68 DESIGN OF TALL TOWERS
DEFLECTION
Towers should be designed to deflect no more than 6 inches per 100 feet of height. The deflection due to the wind load may be calculated by using the formula for uniformly loaded cantilever beam. FORMULA
tlM
=
D1 E H I
= = =
R
= = =
t
Pw
=
NOTATIONS Maximum deflection (at the top), in. Width of the tower with insulation, etc. ft. Modulus of elasticity, psi Length of vessel, included skirt, ft. R3 7T t, moment of inertia for thin cylindrical shell (when R> lOt) Mean radius of the tower, in. Thickness of skirt, in. Wind pressure, psf
EXAMPLE
Given: D 1 = 2 ft., 6 in. E = 30,000,000 H = 48 ft., a in. I = R3 7T 0.3125 P w = 30 psf R = 12 in. t = 0.3125 in.
Determine tlie maximum deflection: tlM
d
M
-
30 x 2.5 x 48 (12 x 48)3 8 x 30,000,000 X 12 3 x 3.14 x 0.3125
=
1.69 in.
The maximum allowable deflection 6 inches per 100 ft. of height: 48 x 6 for 48'-0" = - - - = 2.88 in. 100 Since the actual deflection does not exceed this limit, the designed thickness of the skirt is satisfa(,tory.
A method for calculating deflection, when the thickness of the tower is not constant, given by S. S. Tang: "Short Cut Method for Calculating Tower Deflection". Hydrocarbon Processing November 1968.
69
DESIGN OF TALL TOWERS
COMBINATION OF STRESSES The stresses induced by the previously described loadings shall be investigated in combination to establish the governing stresses. Combination of wind load (or earthquake load), internal pressure and weight of the vessel: Stress Condition At leeward Stress due + Stress due - Stress due
At windward side + Stress due to wind + Stress due to into press .. - Stress due to weight
side to wind to int. press. to weight
Combination of wind load (or earthquake load), external pressure and weight of the vessel: Stress Condition At windward side
+ Stress due to wind Stress due to ext. press. Stress due to weight
At leeward Stress due Stress due Stress due
side to wind to ext. press. to weight
The positive signs denote tension and the negative signs denote compression. The summation of the stresses indicate whether tension or compression is governing. It is assumed that wind and earthquake loads do not occur simultaneously, thus the tower should be designed for either wind or earthquake load whichever is greater.
Bending stress caused by excentricity shall be summarized with the stresses resulting from wind or earthquake load. The stresses shall be calculated at the following locations: 1. 2. 3. 4.
At At At At
the bottom of the tower the joint of the skirt to the head the bottom head to the shell joint changes of diameter or thickness of the vessel
The stresses furthermore shall be examined in the following conditions: 1. 2. 3.
During erection or dismantling During test During operation
Under these different conditions, the weight of the vessel and consequently, the stress conditions are also different. Besides, during erection or dismantling the vessel is not under internal or external pressure. For analyzing the strength of tall towers under various loadings by this Handbook, the maximum stress theory has been applied.
70
COMBINATION OF STRESSES (cont.) The bending moment due to wind is decreasing from the bottom to the top of the tower, thus the plate thickness can also be decreased accordingly. Table A and Figure B are convenient aids to find the distance down from the top of the tower for which a certain thickness is adequate. 0.5 1.0 1.8 0.53
tjtp
m tjtp
m
0.7 0.84 2.0 0.50
0.6 0.91 1.9 0.51
0.8 0.79 2.2 0.48
0.9 0.74 2.4 0.46
1.0 0.71 2.6 0.44
1.1 0.67 2.8 0.42
1.2 0.64 3.0 0.41
1.3 0.62 3.3 0.39
1.4 0.60 3.6 0.37
1.5 0.58 4.0 0.35
1.6 0.56 4.5 0.33
1.7 0.54 5.0 0.32
T ABLE A, VALUES OF FACTOR m Since the longitudinal stress due to internal pressure is one half of the circumferential stress, one half of the required wall thickness for internal pressure is available to resist the bending force of the wind. From Table A, using factor m can be found the distance X down from the top tangent line within which the thickness calculated for internal pressure satisfactory also to resist the wind pressure. X = H x m tp = The required thickness for internal pressure (Hoop Tension) in. tw = The required thickness for wind pressure at the bottom head joint to shell, in.
t
X
-
=
0.233 in., tw = 0.644 in. t.Jtp = 0.644/0.233 == 2.7 100 ft. From Table m = 0.43 and X = mH = 0.43 x 100 = 43 ft.
~ H
EXAMPLE:
0.0
=
Figure B shows the moment diagram of a tower under wind pressure. The diagram can also be used to select the appropriate plate thickness at various heights.
0.1 I-0.21\-
::c Ii ~
~I-\ 0.4 0.3
\
~
0
f-o O.S ~
0
f-o
::c
0.6
0
til
::c
EXAMPLE: At the height ofO. 71 H the required thickness is 0.5 times the thickness required at the bottom. If the required thickness is: = 0.250 in. for internal pressure, Ip = 0.625 in. for wind load, tw at the bottom required =0.750 in. 1/2 + tw
0.7 0.8
'-
"" 0,.
"
~
at height 0.71 H; 0.5 X 0.750 thickness for internal pressure t/2 required thickness at 0.71 H
0.9
-
1.0 0.1 0.2 0.3 0.4 O.S 0.6 0.70.8 0.9 1.0
Ratio of plate thickness required at the bottom (t,/2 + ~) to thickness required at the considered heIght.
Fig. B
= 0.375
in.
= 0.125 in. =
0.500 in.
71
DESIGN OF TALL TOWERS
EXAMPLE - A Required thickness of cylindrical shell under internal pressure and wind load. 2' - 6"
~
DESIGN CONDITIONS D = 2 ft. 0 in. inside diameter of vessel D J = 2 ft. 6 in. width of tower with insulation, etc. E = 0.85 efficiency of welded joints H = 48 ft. 0 in. length of tower hr = 4 ft. 0 in. distance from the base to the bottom head to shell joint P = 250 psi internal pressure Pw = 30 psf wind pressure R = 12 in. inside radius of vessel S = I 5700psi stress value of SA 285 C material at 200°F temperature V = Total shear lb.
o
.,. QQ
II
.,.
:c
N
II
-
.c
No allowance for corrosion. Minimum required thickness for internal pressure considering the strength of the long seams: PR 250 X 12 3,000 . t = SE _ 0.6P = 15700 X 0.85 - 0.6 X 250 = 13,195 = 0.228 m. Minimum required thickness for internal pressure considering the strength of the girth seams: PR 250 x 12 3,000. t = 2SE + O.4P = 2 x 15,700 x 0.85 + 0.4 x 250 = 26,790 = 0.112 m. Required thickness for longitudinal bending due to wind pressure. Moment at the base (M):
Pw x D J x H = V x h J = M 30 x 2.5 x 48 = 3,600 x 24 = 86,400 ft. lb. Moment at the bottom seam (Mr) Mr
= =
M - hr (V - 0.5 P w D J hT ) = 86,400 - 4 (3,600 - 0.5 x 30 x 2.5 x 4) 86,400 - 13,800 = 72,600 ft. lb. = 72,600 x 12 = 871,200 in. lb.
Required thickness: t = ~ = _ _ _ _8:..,.;.7. .;;,.1:..::,2. :,.00:.. .--_ _ _ -
R2
'TT
SE
871,200 - 0 145 in 122 x 3.14 x 15,700 x 0.85 - 6,037,135 - . .
The required thickness calculated with the strength of the bottom girth seam: For wind pressure For int. pressure TafAL
0.145 in 0.112 in. 0.254
This is greater than the thickness calculated with the strength of the longitudinal seam therefore, this minimum thickness 0.257 in. shall be used.
For simple vessels where the moment due to wind is small, the above calculation is satisfactory. Vessels which are subject to larger loadings may need closer investigation with respect also to economical viewpoints. See pages 76-84 for skirt, base and anchor bolt design.
72 DESIGN OF TALL TOWERS
EXAMPLE B Required thickness of cylindrical shell under combined loadings of internal pressure, wind and weight of tower. •
3'-6"
~~
DESIGN DATA
+-E~yform ~
r--r"
D DI
E hT
"tl "tl
...'" -l
o
H P
Co
o
f-o
Pw
II
::t:: II
= =
= = =
R
= =
S
=
V
=
Head:
.i;
-~
= 3 ft. 0 in. inside diameter
cm
=
3 ft. 6 in. width of vessel with insulation. allowance for piping. etc. 0.85 efficiency of welded seams 4 ft. 0 in. distance from the base to the bottom head to shell joint. 100 ft. 0 in. length of tower 150 psi internal pressure 30 psf wind pressure 18 in. inside radius of vessel 15700psi stress value of SA-285C material at 200°F temperature Total shear, lb. 2: I seamless elliptical Circumference of shell on the mean diameter. in. (corrosion allowance not required)
Minimum required thickness for internal pressure considering the strength of the longitudinal seam of shell. PR t = -SE---0-.6-P =
150 x 18 15700 x 0.85 _ 0.6 x 150 = 0.204 in. Use 0.25 in. plate
Minimum required thickness for internal pressure considering the strength of the circumferential seam of shell. PR 150 x 18 == 0.101 in. t = = 2------------------------2SE + 0.4P x 15700 x 0.85 + 0.4 x 150 Minimum required thickness for head PD t
= -2S-E---0-.2-P- =
Wind Load Vessel Platform Ladder
150 x 36 2 x 15700 x 0.85 _ 0.2 x 150 = 0.203 in.
Pw x D, x H 30 x 3.5 x 100 30 x 8 lin. ft. 30 x 98 lin. ft. Total shear
V X hI 10,500 x 50 240 x 96 = 2,940 x49 =
= = V=
13,680
M
=
M
= 525,040 = 23,040
=
144,060
= 692,100 f1. lb. moment at
base Moment at the bottom head seam (M T) MT I
=M
- hT (V - 0.5 P wDlhT) = 692,100 - 4 (13680 - 0.5 x 30 x 3.5 x 4)
= ~ =
R2
1T
SE
12 x 638,220 18 2 x 3.14 x 15700 x 0.85 =
Try 0.750 in. plate for the lower courses
=
638,220 f1. lb.
7,658,640
13~583,556
For int. pressure
=
0.564
0.101 0.665 in.
73
EXAMPLE B (CONT.) ~
'0 '0 ~
-
-
01)
f'4
ci I - -
I--
'0
'0
'0
(..
~
f'I
~
'0 01)
r--
ci
-
i
Q
I--
01)
~ N
.....
ci I--
--
'0
~-
~
...
Shell 40 x 97 32 x 195 24 x 294
Head top 0.3125 nom. bot. 0.8125 nom. Int. plate work 1ray supports Insulation rings Opening
+
6%
Say
The preliminary calculation of the required wall thickness shows that at the bottom approximately 0.75 in. plate is required, to withstand the wind load and internal pressure, while at the top the wind load is not factor and for internal pressure (hoop tension) only 0.25 plate is satisfactory. For economical reasons it is advisable to use different plate thicknesses at various heights of the tower. The thickness required for hoop tension (0.25 in.) serves to resist also the wind load to a certain distance down from the top. Find this distance (X) from table A, Page 70 tw/tp = 0.564/0.204 = 2.7 then X = 0.43 x H = 43 ft. can be found the required From diagram B, Page 70 thickness and length of the intennediate sheD sections. Using 8 ft. wide plates, the vessel shall be constructed from: (5) 0.25 thick 8 ft. wide courses 40 ft. (4) 0.50 thick 8 ft. wide courses 32 ft. (3) 0.75 thick 8 ft. wide courses 24 ft. 96 ft. Total WEIGHT OF THE TOWER (See tables beginning on page 374 ) 3880 Skirt 4 x 195 6240 Base ring 7056 Anchor ring 160 Anchor lugs 393 800 llO 220 900 19759
1184 20943 lb. 21,000
+
6%
Say
Trays Operating liquid
+ Erection Wt.
600 2400 3000 lb. 33,000 lb.
TOTAL OPERATING WEIGHT: 36.000 lb. Test water + Erection Wt.
42,000 lb. 33,000 lb.
TOTAL TEST WEIGHT: 75,000 lb. For weight of water content, see Page 416
260 120 1880 113 1993 2000 lb.
4600
Insulation Platfonn Ladder Piping Say
TarAL ERECTION WEIGHT: 33,000 lb.
780 720
1160 2800 1400 9960 10,000 lb.
74
EXAMPLE B (CONT.) Checking the stresses with the preliminary calculated plate thicknesses:
Stress in ·the shell at the bottom head to shell joint: Plate thickness 0.75 in. PD 150 X 36.75 Stress due to internal pressure
Stress due to wind Stress due to weight, in erection condition in operating condition
S
=-
= 1837 psi 4 x 0.75 12 X 638,220 - 9 . S - ~ - R2 1T t - 18.3752 X 3.14 x 0.75 - ,632 pSI W 31,000 S = -- = = 358 psi Cmt 115.5 x 0.75 S
=~ =
4t
=
Cmt
34,000 115.5 x 0.75
= 392 psi
COMBINA TION OF STRESSES WINDWARD SIDE LEEW ARD SIDE IN EMPTY (ERECTION) CONDITION
Stress due to wind Stress due to weight
+ 9,640 -
Stress due to wind Stress due to weight
358
+ 9,282 psi (No into pressure during erection) Stress due to int. press. S tress due to wind Stress due to weight
- 9,640 358 - 9,998 psi
IN OPERATING CONDITION + 1,837 Stress due to wind + 9,640 Stress due to weight + 11,477 392 Stress due to int. press. + 11,085 psi
- 9,640 392 -~10,032
+ 1,837 - 8,195 psi
The tensile stress 11,085 psi in operating condition on the windward side governs. The allowable stress for the plate material with 0.85 joint efficiency is 13,345 psi. Thus the selected 0.75 in. thick plate at the bottom of the vessel is satisfactory. Stress in the shell at 72 ft. down from the top of tower. Plate thickness 0.50 in. -r"----~......
Stress due to wind.
U
-r-- ~
9
N
r-II
:..::
Pw x D I x X
9 0 r--
9 00 \0
x
= V x -2 = Mx
30 x 3.5 x 72 = 7,560 x 36 30 x 8 lin.-ft. = 240 x 68 30 x 70Iin.-ft. = 2,100 x 35 Total Moment Mx 12 Mr = 12 x 361,980 s = R2 1T t 18.252 x 3.14 x 0.50 Stress due to internal pressure (As calculated previously) Total Shell Platform Ladder
= 272,160 = 16,320 = 73,500 = 361,980 ft.-lb. 8,303 psi 1,837 10,140 psi
The calculation of stresses at the bottom head has shown that the stresses on the windward side in operating condition govern and the effect of the weight is inSignificant. Therefore without further calculation it can be seen that the tensile stress 10,140 psi does not exceed the allowable stress 13,345 psi. Thus the selected 0.50 in. thick plate is satisfactory.
75
EXAMPLE B (CONT.)
Stress in the shell at 40 ft. down from the top of the tower. Plate thickness 0.25 in.
~ ...,;--
0
~
0
0
II
00
~
I"")
><
Stress due to wind .
...
Pw
~~
0
";c I"")
X
D}
X
X = V
X
x
2"
=
Mx
30 X 3.5 X 40 = 4,200 x 20 = 84,000 10 x 8 lin. ft. = 240 x 36 = 8,640 30 x 38 lin. ft. = 1,140 x 19 = 21,660 = 114,300 ft.-lb. Total Moment Mx 12 Mr = 12 x 114,300 s = R2 'IT t = 5,316 psi 18.1252 x 3.14 x 0.25 Stress due to internal pressure (As calculated previously) 1,837 psi Total 7,153 psi Shell Platform Ladder
The 0.25 in. thick plate for shell at 40 ft. distance from top of the tower is satisfactory. No fUrther calculation is required on the same reason mentioned above.
76
DESIGN OF SKIRT SUPPORT A skirt is the most frequently used and the most satisfactory support for vertical vessels. It is attached by continuous welding to the head and usually the required size of this welding determines the thickness of the skirt. Figures A and B show the most common type of skirt to head attachment. In the calculation of the required weld size, the values ofjoint efficiency given by the Code (UWI2) may be used. FORMULA 12MI' W t= +-R2 ;rrSE D ;rrSE
NOTATIONS D= Outside diameter of skirt, in. E = Efficiency of skirt to head joint.
(0.6 for butt weld, Fig. A, 0.45 for lap weld, Fig. B) M= Moment at the skirt to head joint, ft. lb. R T= Outside radius of skirt, in. Stress value of the head or skirt material whichever S is smaller, psi. Required thickness of skirt, in. t W= Weight of the tower above the skirt to the head joint, in operating condition.
B
NOTE: Using extremely high skirt, the stresses at the base may govern. To calculate the required thickness of the skirt, in this case the above formula can be used, considering the moment and weight at the base; E = I. EXAMPLE Given the same vessel considered in Example B. D = 37.5 in. E = 0.60 for butt joint
Mr= 638,220 ft. lb.
S = 15,700 stress value of SA - 285 - C plate W = 31,000Ib.
R = 18.75 in.
Determine the required skirt thickness. Forwind:
12 MI' 12 X 638,220 t= R2 ;rrSE + 18.75 2 X3.14X 15,700XO.6
=0.736 in.
For weight:
W t=DX3.14XSE
=0.028 in.
31,000
3.75X3.14XI5700XO.6 TOTAL Use 13/16" thick plate for skirt.
=0.764 in.
REFERENCES: Thermal stresses are discussed in these works: Brownell. Lloyd E .. and Young, Edwin H., "Process Equipment Design,".John Wiley and Sons, Inc., 1959. Weil, N.A., and J. J. Murphy Design and Analysis of Welded Pressure Vessel Skirt Supports. Asme. Trans. Industrial Engineering for Industry, Vol. 82, Ser. B., Feb., 1960.
77 DESIGN OF ANCHOR BOLT
Vertical vessels, stacks and towers must be fastened to the concrete foundation, skid or other structural frame by means of anchor bolts and the base (bearing) ring. The number of anchor bolts. The anchor bolts must be in multiple of four and for tall towers it is preferred to use minimum eight bolts. Spacing of anchor bolts. The strength of too closely spaced anchor bolts is not fully developed in concrete foundation. It is advisable to set the anchor bolts not closer than about 10 inches. To hold this minimum spacing, in the case of small diameter vessel the enlarging of the bolt circle may be necessary by using conical skirt or wider base ring with gussets. Diameter of anchor bolts. Computing the required size of bolts the area within the root of the threads only can be taken into consideration. The root areas of bolts are shown below in Table A. For corrosion allowance orie eighth of an inch should be added to the calculated diameter of anchor bolts. For anchor bolts and base design on the following pages are described: 1. 2.
An approximate method which may be satisfactory in a number of cases. A method which offers closer investigation when the loading conditions and other circumstances make it necessary.
TABLE A
Bolt Size
Y2 % %
Ys
1 1Ys 1~
1% 1~
1% 1% 1% 2 2~ 2~
2%
3
*
Bolt • Root Area SQ. in.
0.126 0.202 0.302 0.419 0.551 0.693 0.890 1.054 1.294 1.515 1.744 2.049 2.300 3.020 3.715 4.618 5.621
m Dimension in.
12
13
7/8 1 1-1/8 1-1/4 1-3/8 1-1/2 1-3/4 1-7/8 2 2-1/8 2-1/4 2-3/8 2-1/2 2-3/4 3-1/16 3-3/8 3-5/8
5/8 3/4 13/16 15/16 1-1/16 1-1/8 1-1/4 1-3/8 1-1/2 1-5/8 1-3/4 1-7/8 2 2-1/4 2-3/8 2-5/8 2-7/8
For bolts with standard threads.
TABLE B NUMBER OF ANCHOR BOLTS Diameter of Bolt circle in.
24 42 60 84 108 132
to to to to to to
36 54 78 102 126 144
Minimum
Maximum
4 8 12 12· 16 20
4 8 12 16 20 24
TABLE C MAXIMUM ALLOW ABLE STRESSES FOR BOLTS USED AS ANCHOR BOLT Specifica tion Number
Diameter in.
Max. allow. Stress psi.
SA307 SA193B 7 SA 193 B16 SA193B 7 SA 193 B16
All diameters 2 Yz and under 2 Yz and under Over 2 Yz to 4 incl. Over 2 Yz to 4 incl.
15,000 19,000 17,000 18,000 15,000
78
DESIGN OF ANCHOR BOLT (Approximate Method) A simple method for the design of anchor bolts is to assume the bolts replaced by a continuous ring whose diameter is equal to the bolt circle. The required area of bolts shall be calculated for empty condition of tower. FORMULAS Maximum Tension Ib./lin. in.
T
Required Area of One Bolt Sq. - in.
BA
Stress in Anchor Bolt psi.
Ss
T- 12M _ W - As Cs
Ss
TC s
= BA N
NarATION = Area within the bolt circle, sq. in. = Circumference of bolt circle in. = Moment at the base due to wind or earthquake, ft. lb. = Number of anchor bolts = Maximum allowable stress value of bolt material psi. = Weight of the vessel during erection, lb.
AB CB M N SB
W
EXAMPLE Given bolt circle AB CB M W
SB N
=
30 in.; then:
Determine the size and number of required anchor bolts.
=
707 sq. in. 94 in. 86400 ft. lb. = 6000 lb. during erection. = 15000 psi. the maximum allowable stress value of the anchor bolt material. = 4 number of bolts. (See Table B on the Preceding Page)
= =
T
=
12 x 86,400 6000 707 - ~
=
1,402 lb.llin. in.
- . 2 196 sq. In. . BA = 1,402 x 94 15,000 x 4 From Table A. Page 77 the root area of 2" bolt is 2.300 sq. in. Adding 0.125 in. for corrosion, use: (4) 2W' bolts. Checking stress in anchor bolt: SB
x 94 = 14324 si 2.300 x 4 ' P
= 1,402
Since the maximum allowable stress is 15,000 psi, the selected number and size of bolts are satisfactory.
79
DESIGN OF BASE RING (Approximate Method) The formulas below are based on the following considerations: 1. The bearing surface of the base ring shall be large enough to distribute the load uniformly on the concrete foundation and thus not to exceed the allowable bearing load of the foundation. 2. The thickness of the base ring shall resist the bending stress induced by wind or earthquake.
-r-f- '."
man.
I, 3
t8
~
2
_Dj
W.fi 0l I
1..-0 0
FORMULAS Maximum Compression Ib'/Iin., in.
P = 12M+lf c As Cs
Approximate Width of Base Ring, in. Approximate Thickness of Base Ring, in. Bearing Stress, psi Bending Stress, psi
1- Pc
-lb
til
=0.321 1
S - PeCs
I - Au
S2
3 X SI t ~ t l/
NOTATION AN = Area of base ring = 0.7854 (D2o - D2) sq. in. A\" = Area within the skirt, sq. in. C\" = Circumference on 0.0. of skirt, in.
.f, = Safe bearing load on concrete, psi. See Table E, on Page 80
II = Cantilever inside or outside, whichever is greater, in. II I] = Dimensions, as shown on sketch above.-(Forminimum dimensions see Table A on page 77) M = Moment at the base due to wind or earthquake, ft. lb. W = Weight of vessel during operation or test, lb. Given: M= 86,400 ft. lb. f, = 500psi from Table E, Page 80 Anchor bolts: (4) 2 114 in. 0.0. of skirt: 24.625 in. ThenA,=476 sq. in. C.\.= 77 in.
EXAMPLE Determine the minimum width and thickness of base ring for operating condition. J>..
12X86,400 7,500=2275Ib/l"_' 476 + 77 ' . m. m.
1=25~~5 =4.55 in.,
but from Table A, page 77 the minimum dimension for I, = 2314 in. and for 13= 2 114 in.,use 6Vz in. wide base ring. th = 0.32 X 5 = l.60 in Checking stresses: Use 1% in. thick baseTing 2,273 X77 305 p'si SI 574 3 X 305 X 52 = 10,167 psi Bearing stress S] Bending Stress \.5 2 Using SA 285 C plate for base ring, 15,700 psi allowable stress can be taken. Thus the width and thickness of the base ring are satisfactoy. The stresses should be checked also for test condition.
80
DESIGN OF ANCHOR BOLT AND BASE RING
When a tower is under wind or earthquake load, on the windward side tensional stress arises in the steel and on the opposite side compressive stress in the concrete foundation. It is obvious then that the area of the bolting and the area of the base ring are related. As the anchor bolt area increased, the base ring area can be decreased. With the design method given here, the minimum required anchor bolt area for a practical size of base ring can be found. The strength of the steel and the concrete is different, therefore, the neutral axis does not coincide with the centerline of the skirt. Design procedure: 1. Determine the value of k 2. Calculate the required size and number of anchor bolts. See page 77 Table B 3. Determine the inside and outside diameter of the base ring 4. Check the stresses in the anchor bolts and foundation 5. If the deviation between the allowable and actual stresses are too large, repeat the calculatidn 6. Calculate the base ring thickness 7. Use gu sset plates, anchor chairs or compression ring if it is necessary for better stress distribution in the base ring or skirt
D
k
0.00 .05 .10 .15 .20 .25 .30 .35 .40 .45 .50 .55 .60 .65 .70 .75 .80 .85 .90 .95 1.00
TABLE D Values of Constants as Functions of K j Cc Ct
z
3.142 3.008 2.887 2.772 2.661 2.551 2.442 2.333 2.224 2.113 2.000 1.884 1.765 1.640 1.510 1.370 1.218 1.049 0.852 0.600 0.000
0.500 .490 .480 .469 .459 .448 .438 .427 .416 .404 .393 .381 .369 .357 .344 .331 .316 .302 .286 .270 .250
0.000 0.600 0.852 1.049 1.218 1.370 1.510 1.640 1.765 1.884 2.000 2.113 2.224 2.333 2.442 2.551 2.661 2.772 2.887 3.008 3.142
0.750 .760 .766 .771 .776 .779 .781 .783 .784 .785 .785 .785 .784 .783 .781 .779 .776 .771 .766 .760 .750
TABLE F Bending moment per unit length of section of a plate perpendicular to X and Y axes respeotively. Use greater value, Mx or My.
Ij{, 0.000 0.333 0.500 0.667 1.000 1.500 2.000 3.000 00
TABLE E Properties of Concrete Four Mixtures Ultimate 28 day Strength psi Allowable compr. Strength fc psi Safe bearing load fb psi Factor n
Mx
0.000 0.OO781c b2 0.0293/cb 2 0.0558/c b2 0.09721c b2 0.123 /c b2 0.131 /c b2 0.133 /c b2 0.133 Ic b2
My
-
0.5001c If 0.428/cli 0.319/c Ii 0.227/c 0.1191c It 0.1241c b2 0.1251c b2 0.125/c b2 0.1251c b2
NOTE: See notation on facing JUl,ge.
2000
2500
3000
3750
800
1000
1200
1500
500
625
750
938
15
12
10
8
n
81
DESIGN OF ANCHOR BOLT AND BASE RING FORMULAS
I"
Value of constant, k dimensionless
Min.
11 12
13_
tB
Total required area of anchor bolts Bt sQ. - in.
~
Relationship between max. allowable compressive stress at the outside edge of base ring and at the bolt circle.
~
t Tensile load on anchor bolts, Ft lb. Tensile stress in anchor bolts, Sa, psi.
r-f;lr;
+.-.1 H-
b
tB
~
I
•
II V///-
W
t
~
- 1 + (S./n/cb)
B(=2n
12M- Wzd C,S.jd 2kd+ I
Ic =lcbTkd
2kd /eh =ie 2kd + I F._M-WzD ,jD
S-~ • - t,re,
Thickness of a ring which has an area equal to the area of anchor bolts, ts, in. Compression load on the concrete, Fc, lb.
'1
1
k-
t
S
= !it... nd
Fc=F,+ W
Compressive stress in the concrete at the bolt circle. fcb psi.
r.. Fe . eb = (14 + nt,) rCc
Relationship between tension in steel and compression in concrete.
S. = n/c
Base ring thickness without gusset plate, tB, in . Base ring thickness with gusset plate, tB, in.
tB
=
(B=
II
J 31c/S
y6Mmax
--S-
NOTATION b
r
=
The distance between gusset plates, measured on arc of bolt circle in. Total area required for anchor bolt sq. in. Constants, see Table D on the preceding page. Diameter of anchor bolt circle, in. Diameter of anchor bolt circle, ftCompressive stress in the concrete at the outer edge of the base ring, psi. Compressive stress in the concrete at the bolt circle, psi. Constant, see Table D on the preceding page. I - t f in. = width of the base ring, in. Moment at the base due to wind or earthquake ft. lb. M. or M,. whichever is greater. See Table F on the preceding page. Ratio of 'modulus of elasticity of steel and concrete Es/Ec. See Table E. Radius of bolt circle, in.
Sa
=
Allowable tensile stress on anchor bolts, psi.
S
Maximum allowable stress value of base plate, psi. Weight of the tower at the base, lb. = Constant. See Table D on the preceding page.
= = B, Ce,C, = = d = D
fe feb j 14
= = = = = =
M Mmax = n
W
z
= =
82
DESIGN OF ANCHOR BOLT AND BASE RING
EXAMPLE DETERMINE: The size and number of anchor bolts; The width and thickness of base ring.
DESIGN DATA: = 5 ft., 0 in. diameter of anchor bolt circle. = 60 in. diameter of anchor bolt circle. n = 10, ratio of modulus of elasticity of steel and concrete (Table E. Page 80) fe = 1,200 psi allowable compr. strength of concrete (Table E, Page 80) S = 15,000 psi allowable stress value of base ring. Sa = 18,000 psi allowable tensile stress in bolts. W = 36,000 lb. weight of the tower. M = 692,100 ft. lb. moment at the base.
D d
I
~.
1
=
+~
1
nfeb
2kd
feb = fe
t 1
2kd
=
1,200
1
+
r07ffhl
1 = 8"
t
SOLUTION: Assume 8 in. wide base ring and a compressive stress at the bolt circle,
k =
2"
T
IBl
feb =
I
"1
1,000 psi.
Then the constants from Table Dare: Ce = 1.640 Cr = 2.333 = 0.783 j = 0.427 z
1 = 0.35 18,000 lOx 1,000
2 x 0.35 x 60 = 1,008 psi 2 x 0.35 x 60 x 8
This is in sufficient agreement with the assumed value of feb = 1,000 psi
Required area of anchor bolts _ 12M - Wzd _ 6 12 x 692,100 - 36,000 x 0.427 x 60 - 2 0 . B-2 7T .28 - 3.5 sq. In. r Cr Sa jd 2.333 x 18,000 x 0.783 x 60 Using 12 anchor bolts, the required root area for one bolt 23.50112 = 1.958 in. From Table A 17/s in. diameter bolt would be satisfactory but adding 'Is in. for corrosion, use (12) -2 in. diameter anchor bolts. Tensile load on the anchor bolts M - Wz D 692,100 - 36,000 x 0.427 x 5 Fr = jD = 0.783 x 5 = 157,150 lb. Tensile stress in the anchor bolts ~
Sa
= trC =
~
s
7T
d
=
23.50 _ . 3.14 x 60 - 0.125 tn. 14
=
+ 10
X
Compressive load on the concrete:
/.eb
. pSI
r
s
I
157,150 0.125 x 30 x 2.333 = 17,960
=
= (I 4
+
Fe nl) r C = (7.875 s
e
I - Is
=
193,150 0.125) 30
8.0 - 0.125 = 7.875 in. 430 X
1.640 =
. pSI
83
DESIGN OF ANCHOR BOLT AND BASE RING EXAMPLE (Cont.) Checking value of kwhich was calculated with assumed values ofiel> = 1,000 psi and Sa= 18,000. Then the constants from Table Dare: 1 k=-- = = 0.19 Cc = 1.184 1 + Sa 1 + 17,960 C I = 2.683 10 X430 nicl> j = 0.775 z == 0.461 F = M- WzD = 692,100-36,000 X 0.461 X 5 = 157 1921b
0.775 X 5
jD
I
_ Sa -
,.
FI _ 157,192 624 . CI - 0.125 X 30 X 2.683 - 15, PSt
fIr
Fc= FI + W= 157,192 + 36,000 = 193,192 lb. 193,192 (7.875+ IOXO.125)30X 1.184
596 psi
Compressive stress in the anchor bolts: Sa= nicl> = lOX 596 = 5,960 psi Compressive stress in the concrete at the outer edge of the base ring: 2kd + I
ft· =icl> X 2kd
2 X 0.19 X 60 + 8 = 596 X 2 X 0.19 X 60
805 psi
Required thickness of base ring I} = 6 in. {Ji
~
= I} V.:J.h l S= 6
J3X805 . 15,000 2.406 m.
To decrease the thickness of the base ring, use gusset plates. Using (24) gusset plates, the distance between the gussets:
-785".1 1 b -- Jrd 24 - . 'b
6 - 0 764 - 7.85.
-
from Table F: MI/IIIX= M),= 0.196ft·I/=0.196 X 805 X 62 = 5680 in. lb. tR =
J61~,~~g
1.5076 in. Use I1h in., thick base plate.
84
ANCHOR BOLT CHAIR FOR TALL TOWERS
The chairs are designed for the maximum load which the bolt can transmit to them. The anchor bolt size and base plate shall be calculated as described on the foregoing pages. All contacting edges of the plates shall be welded with continuous fillet weld. The leg size of the fillet weld shall be one half of the thinner joining plate thickness.
E '//'
'//' l' .(J'
........-r---+-t-D
DIMENSIONS inches Anchor
A
B
C
D
E
1
P/4
)1 Is
PIs 2 2 1/s
3 3 3 4 4 4
112 112 112
6 6
21/2 21/2 21/2 3 3 3 3 1/2 3 1/2 3 1/2 4 4
3/4 3/4 1 1 Jl/4 Jl/4 Jl/2 )1/2 P/4 P/4
7 7
5 5
bolt diam
)114
PIs )112 ISIs P/4
2 3 /s
PIs
2 5 /s
2 21/4 21/2 2 3/4 3
2 3/4 3 3 1/4 3 1/2 3 3/4
21/4 21/2
5 5 5
sIs sIs sIs 314 314 314 1 1 )114 Jl/4
2 21/2 21/2
F
G
P/4
P/2
13 /s
ISIs
Jl/2
P/4
ISIs
PIs 2 2 1/s
13/4
PIs 2 2 1/s 21/4 21/2 2 3/4 3 3 1/4
21/4 2 3/s 21/2 2 3/4 3 3 1/4 3 1/2
The above table is taken from Scheiman A.D. Short Cuts to Anchor Bolting and Base Ring Sizing. Petroleum Refiner, June 1963.
85
86
STRESSES IN LARGE
HORIZONTAL VESSELS SUPPORTED BY SADDLES
The design methods of supports for horizontal vessels are based on L. P. Zick's analysis presented in 1951. The ASME published Zick's work (pressure Vessel and Piping Design) as recommended practice. The API Standard 2510 also refers to the analysis of Zick. The British Standard 1515 adopted this method with slight modification and further refinement. Zick's work has also been used in different studies published in books and various technical periodicals. The design method of this Handbook is based on the revised analysis mentioned above. (Pressure Vessel and Piping; Design and Analysis, ASME, 1972) A horizontal vessel on saddle support acts as a beam with the following deviations: 1. The loading conditions are different for a full or partially filled vessel. 2. The stresses in the vessel vary according to the angle included by the saddles. 3. The load due to the weight of the vessel is combined with other loads. LOADINGS: 1. Reaction of the saddles.
It is a recommended practice to design the vessel
for at least a full waterload. 2. Internal Pressure. Since the longitudinal stress in the vessel is only one half of the circumferential stress, about one half of the actually used plate thickness is available to resist the load of the weight. 3. External pressure. If the vessel is not designed for full vacuum because vacuum occurs incidentally only, a vacuum relief valve should be provided especially when the vessel outlet is connected to a pump. 4. Wind load. Long vessels with very small tlr values are subject to distortion from wind pressure. According to Zick "experience indicates that a vessel designed to 1 psi. external pressUre can successfully resist external loads encountered in normal service." 5. Impact Loads. Experience shows, that during shipping, hardly calculable impact loads can damage the vessels. When designing the width of the saddles and the weld sizes, this circumstance is to be considered.
87 LOCATION OF SADDLES. The use of only two saddles is preferred both statically and economically over the multiple support system, this is true even if the use of stiffener rings is necessary. The location of the saddles is sometimes determined by the location of openings, sumps, etc., in the bottom of the vessel. If this is not the case, then the saddles can be placed at the statically optimal point. Thin walled vessels with a large diameter are best supported near the heads, so as to utilize the stiffening effect of the heads. Long thick walled vessels are best supported where the maximal longitudinal bending stress at the saddles is nearly equal to the stress at the midspan. This point varies with the contact angle of the saddles. The distance between the head tangent line and the saddle shall in no case be more than 0.2 times the length of the vessel. (L) Contact Angle (J The minimum contact angle suggested by the ASME Code is 1200 , except for very small vessels. (Code Appendix 0-6). For unstiffened cylinders under external pressure the contact angle is mandatorily limited to 120° by the ASME Code. (U0-29). Vessels supported by saddles are subject to: 1. Longitudinal bending stress 2. Tangential shear stress 3. Circumferential stress
88 STRESSES IN VESSELS ON TWO SADDLES
H~ 'h
A •
u]~.~
L
t. -4...
Q
,
:.a~ §.~
Z
Q
z
I.i.I
=:I
..J ~
Z
Q
:l ~
i3 z
0
..J
Q UJ VlZ QUJ
Vl c:lZ Q;:J UJ-l z-l UJUJ u..:I: u.. Vl -0::
t;;o
-lVl -l'-' UJZ :I:VlO:: 0:: 0
e:
:;'<'"
~C2" " ~I\ 0
~
<
,; ~
~=
Max. Allow. Stress
FORMULAS
ut.:)
AT THE SADDLES (Tension at the Top.
AR'-) QA( l-I+ 1+
Compression
at the Bottom)
SI= +
2AL 4H 3L
*KR2 ts
·See note on facing page AT MIDSPAN (Tension at the Bottom Compression at the Top)
( R'U
-H'
QL 1+ 2
1 + 4H 3L 'IT R2 ts
4
S =+ I
4~
IN SHELL
Vl
IN SHELL
_ K3 Q
S2 -
(
RtS
L - 2A ) L + 0/3 H
SI
<: (;)(t/R)[2 - (2/3)(IOO)(t/R)]
S2 shall not exceed 0.8 times the allowable stress value of vessel material.
NOTE: Use formula with factor K2 if ring not used or rings are adjacent to the saddle. Use formula with factor K3 if ring used in plane of saddle.
ADDI· TlONAL STRESS IN HEAD
Q
AT BOTTOM OF SHELL
In compression the stress due to internal pressure minus 8 1 shall not exceed one half of the compression yield point of the material or the value given by:
83 plus stress due to internal pressure shall not exceed 1.25 times the allowable tensile stress value of head material.
S = K4Q 2 RtS
IN HEAD
AT HORN OF SADDLE
In tension S 1 plus the stress due to internal pressure (PR/2 t s) shall not exceed the allowable stress value of shell material times the efficiency of girth seam.
)
IN SHELL
~1------1I--------------t
~
NOTATION: All dimensions in inches Q = Load on one saddle lbs. R = Radius of shell S = Stress pound per sq. inch ts = Wall thickness of shell th = Wall thickness of head (Excluding corrosion allow.) K = Constant, see page 90 () = Contact angle of saddle degree
3K6Q
4ts(b+I.5~)-~
84 shall not exceed LSO times the allowable tensile stress value of shell material. 85 shall not exceed 0.5 times the compression yield point of shell material.
89 STRESSES IN VESSELS ON TWO SADDLES
NOTES: Positive values denote tensile stresses and negative values denote compression. E : Modulus of elasticity of shell or stiffener ring materiaI.pound per square inch.
The maximum bending stress Sl may be either tension or compression. Computing the tension stress in the formula for S 1, for factor K the values of K 1 shall be used. Computing the compression stress in the formula for Sl' for factor K the values of Kg shall be used. When the shell is stiffened, the value of factor K = 3.14 in the formula for Sl. The compression stress is not factor in a steel vessel where t/R ~ 0.005 and the vessel is designed to be fully stressed under internal pressure. Use stiffener ring if stress S 1 exceeds rhe maximum allowable stress.
If wear plate is used, in formulas for S2 for the thickness ts may be taken the sum of the shell and wear plate thickness, provided the wear plate extends R/l 0 inches above the horn of the saddle near the head and extends between the saddle and an adjacent stiffener ring.
In unstiffened shell the maximum shear occurs at the horn of the saddle. When the head stiffness is utilized by locating the saddle close to the heads, the tangential shear stress can cause an additional stress (S3) in the heads. This stress shall be added to the stress in the heads due to internal pressure. When stiffener rings are used, the maximum shear occurs at the equator. If wear plate is used, in formulas for S4 for the ~ickness ts may be taken the sum of the shell and wear plate thickness and for ts may be taken the shell thickness squared plus the wear plate thickness squared, provided the wear plate extends R/l 0 inches above the horn of the saddle, and A""-R/2. The combined circumferential stress at the top edge of the wear plate should also be checked. When checking at this point: ts = shell thickness, b = width of saddle fJ = central angle of the wear plate but not more than the included angle of the saddle plus 12 0 If wear plate is used, in formulas for S5 for the thickness ts may be taken the sum of the shell and wear olate thickness, provided the width of the wear plate equals at least b + 1.56v'"'Rt; If the shell is not stiffened, the maximum stress occurs at the horn of the saddle. This stress is not be to added to the internal pressure-stress. In a stiffened shell the maximum ring-compression is at the bottom of shell. Use stiffener ring if the circumferential bending stress exceeds the maximum allowable stress.
90
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO SADDLES
VALUES OF CONSTANT K (Interpolate for Intermediate Values)
*K I = 3.14 if the shell is stiffened by ring or head (A CONTACT ANGLE
Kl*
K2
0.335 0.345 0.355 0.366 0.376 0.387 0.398 0.409 0.420 0.432 0.443 0.455 0.467 0.480 0.492 0.505 0.518 0.531 0.544 0.557 0.571 0.585 0.599 0.613 0.627 0.642 0.657 0.672 0.687 0.702 0.718
1.171 1.139 1.108 1.078 1.050 1.022 0.996 0.971 0.946 0.923 0.900 0.879 0.858 0.837 0.818 0.799 0.781 0.763 0.746 0.729 0.713 0.698 0.683 0.668 0.654 0.640 0.627 0.614 0.601 0.589 0.577
f)
120 122 124 126 128 130 132 134 136 138 140 142 144 146 148 150 152 154 156 158 160 162 164 166 168 170 172 174 176 178 180
K3
K4
0.880 0.846 0.813 0.781 0.751 0.722 0.694 0.667 0.641 0.616 0.592 0.319 - 0.569 For 0.547 Any 0.526 Con0.505 Tact Angles 0.485 0.466 8 0.448 0.430 0.413 0.396 0.380 0.365 0.350 0.336 0.322 0.309 0.296 0.283 0.271 0.260
< R/2)
K5
0.401 0.393 0.385 0.377 0.369 0.362 0.355 0.347 0.340 0.334 0.327 0.320 0.314 0.308 0.301 0.295 0.289 0.283 0.278 0.272 0.266 0.261 0.256 0.250 0.245 0.240 0.235 0.230 0.225 0.220 0.216
K6
See chart on facing page
K7
K8
0.760 0.753 0.746 0.739 0.732 0.726 0.720 0.714 0.708 0.702 0.697 0.692 0.687 0.682 0.678 0.673 0.669 0.665 0.661 0.657 0.654 0.650 0.647 0.643 0.640 0.637 0.635 0.632 0.629 0.627 0.624
0.603 0.618 0.634 0.651 0.669 0.689 0.705 0.722 0.740 0.759 0.780 0.796 0.813 0.831 0.853 0.876 0.894 0.913 0.933 0.954 0.976 0.994 1.013 1.033 1.054 1.079 1.097 1.116 1.137 1.158 1.183
91
STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY TWO SADDLES VALUES OF CONSTANT ~
.1J~
.1
9-1 ~J
.1
' '6.~s~
I I II
0.05
9·.1~
I II
lOG
004
1/
II J 11 0.04
I
I
I I
II I 1/ II
.c
~
J.
~
8
.( :03]
.14 P"
~
II I I
8·1S0~
1111 1/11 J 1/
0.03
-
:0.032
IL II
~
II III I II 1111
~ >
8.160 ,-- 0026 I I _LI I
,I III/ I II II
1/
1/
0.02
11I1 1/ 1/
I
LI I I f I I f 1 I I
1/
8.?='I80'o
II
I
-.i
.1
...0.ai7
M J II 1/ 'I V r II/If 1/
r- 0.013
0.01
I 1
8'= bbJ-l , 6.022
J
I-
0~(jl1 ~
rill
-
O~u&,i
111/
/
""
- 0.008
I
./1
~g.~
00=9. . .0054 -~'0;0044
I 1
I I
I 1 1
0.0
0.5
~
1.0 RATIO AIR
l.S
OJ) @R
2.0
92 STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY NO SADDLES EXAMPLE CALCULATIONS Design Data A = 48 in. distance from tangent line of head to the center of saddle b = 24 in. width of saddle H = 21 in. depth of dish of head L = 960 in. length of vessel tanAan. P = 250 psi. internal design pressure Q = 300,000 lb. load on one saddle R = 60 in. outside radius of shell ts = 1.00 in. thickness of shell 9 = 120 deg. contact angle Shell material: SA 515-70 plate Allowable stress value 17,500 psi. Yield point 38,000 psi. Joint Efficiency: 0.85
LONGITUDINAL BENDING STRESS (S,)
Stress at the saddles 2
60 _ 212 ) 1 - - 48 + ---.;~--=:;-=-300,000 x 48 -
1-
960
2x48x960
---=-.:~---.,;...:..-~.:.....--
1 + 4 x 21
(
3x 960
.
= S22 pSI.
O.33S x 60 1 x 1
Stress at midspan
QL 1 + 2 R2 [} H2 _ 4A~ 4 (
1
4H
+ 3L
L
Sl=----~--rr~R~l~ts----~~
300.000 x 960
~ + 2 _60_~_-_~_P _ 4 x 48) 1 + 4 x 21
4
3.14
960
3x960
X
602
X
1
=
499 5
The sum of tensional stresses: 4959 + 7500 = 12,459 psi It does not exceed the stress value of the girth seam: 20,000 X 0.85 = 17,000 psi Compression stress is not a factor since fiR> 0.005; 1/60 = 0.017
. PSI
93 STRESSES IN LARGE HORIZONTAL VESSELS SUPPORTED BY 1WO SADDLES EXAMPLE CALCULATIONS (cont.) TANGENTIAL SHEAR STRESS
(S~)
Since A (48» Rl2 (6012), the applicable formula: 1.171 x 300,000 ( 960 - 2 x 48 ) 60 x 1 960 + 4/3 x 21 52 =
= 5,120psi
does not exceed the stress value of shell material multiplied by 0.8; 20,000 X 0.8 16,000 psi
CIRCUMFERENTIAL STRESS Stress at the horn of saddle (5.)
Since L (960)
> 8R(480),
5=Q • 4Is(b+I.56..fiits) -
AIR
=48/60 = 0.8;
A(48) > RI2 (6012), the applicable formula:
JK,Q 11:
K:= 0.036 (from chart) 3 x 0.036)( 300,000
300,000 5. =-
4 x 1 (24 + 1.56 .J 60
x 1)
2t
: = 20,000 psi
S.j does not exceed the stress value of shell material multiplied by 1.5; 20,000 x 1.5 = 30,000 psi
Stress at bottom of shell
(S5)
K1 Q
Ss=--_"':"-_-'::== Is (b + 1.56VRtsJ Ss=
0.760 x 300,000 1 (24 + 1.56 J 60)( 1
)
6319' =-, PSt
does not exceed the compression yield point multiplied by 0.5; 38,000 )( 0.5 := 19,000 psi
S5
94 STIFFENER RING FOR LARGE HORIZONTAL VESSELS SUPPORTED BY SADDLES Ring
I
NOTATION. A = Cross sectional area of ring plus the effective area of shell, in 2 I = Moment of inertia, inj:J K = Constant, see next page Q = Load on one saddle, lbs. R = Radius of shell, in. S6 = Max. combined stress, psi. (J = Contact angle, degree
/\
;:
))
'I
rill IJ
II
:;
Ii
I
I
Ii
4Q MAX. STRESS
TYPE OF RING
Max. Allow Stress
FORMULAS
Ring Inside. Compression at the Shell Governs B I Ir+I.SL.uyn.l. ~Rts ~
~ ~
I
w
~ C
>12d
i
~
and Ring
Ring Outside. ~~:l~s at the
I ·r \ led
Ir
J
-...;:.1'
i-
~__
'===~~~ _ I .
Ir+I.S~ I
I
D I
Ring Outside. Stress at the S =_ K9 Q KJ 0 QR Tip of the 6 A II d Ri 'ng Ring Inside. Compression S =- K9Q_ KJ oQR de at the Shell 6 A lie Governs ~~--~~--~--------------~ Ring Out-side. K Q K QR ~tress at the S =-~ + -~ Shell 6 A lie
t. -t .J1-i»m l-=P '4" I
~
~
1r
I 2 (Ir+I.S6V"Rl sl • I"
S=_K9Q+KJoQR 6 A lie
•.
K Q
Ring Inside.
K
QR
~~~~s at the
S6 =-
Ring Inside. Stress at the Tip of the Ring
S =_~9 Q _ KJ 0 QR 6 A lid
A + -T;c
i
~ -:;; ~
]
.~
v. -
.~ ~ ... ..c:
:.a :.a] ~
-~~ ;>
~ ~
C; ~
·c .e 8aD ~ .S ...
~0 'C :::::
0~
~
] ..: .S 0 0 ~ c.. ;:3 "'0
~I-plr------------------+----~--------~~--------------------~ ~~
~
2(lr+I.5~) •
~
I
~ ~
• I
I
L::t
y- ~~
~ddle _P1f21·
Ring Outside. Compression at the Shell Governs
S =_ K9Q _ KJ oQR 6 A lie
~~ v.
v.
~ ~
~~
+ •.1 ::§ 0 ~.-pp-rI-~-S-ad-d-Ie-----j--------+-~Ri~.-n-g-l-n-sl-.d-e-.----~--------------------~ : § and
Ring
~'"d.'".;~
~
:&1,"I
f...d
2 (Ir+l5~
Jd
I
~~~~satthe
S6=_KAQ+K1I/~R
~l
Stress at the Tip of the Ring
S=_K9Q_KJoQR 6 A lid
.s.s-
,t---Ri='""'·n-g~In-s....,.id....,.e-.----+---------------------.............~ ~
95
STIFFENER RING FOR LARGE HORIZONTAL VESSELS SUPPORTED BY SADDLES VALUES OF CONSTANT, K (Interpolate for Intermediate Values) Contact Angle e
120°
130°
140°
150°
160°
170°
180°
.34
.33
.32
.30
.29
.27
.25
.053
.045
.037
.032
.026
.022
.017
NOTES: 1. In figures & formulas A-F positive signs denote tensile stresses and nega-
tive signs denote compression. 2.
The first part of the formulas for S6 gives the direct stress and the second part gives the circumferential bending stress.
3.
If the governing combined stress is tensional, the stress due to internal pressure, PR shall be added. ts
CALCULATION OF MOMENT OF INTERIA (I) 1. Determine the width of shell that is effective to resist the circumferential bending moment. The effective width = 1.56~; 0.78~ on both sides of stiffener ring. 2.
Divide the stiffener ring into rectangles and calculate the areas (a) of each rectangle, including the area of shell connection within the effective width. Add the areas (a) total area = A.
3.
Multiply the areas (a) with the distances OJ from the shell to the center of gravity of the rectangles. Summarize the results and denote all AY
4.
Determine the neutral axis of the stiffening ring, the distance (C) from the shell to the neutral axis C = ~y
5.
Determine the distances (h) from the neutral axis to the center of gravity of each rectangle of the stiffener.
6.
Multiply the square of distances (h 2) by the areas (a) and summarize the results to obtain AH2.
7.
Calculate the moment of inertia Ig of each rectangle Ig = width and d = the depth of the rectangles.
8.
The sum of AH2 and Ilg gives the moment of intertia of the stiffener ring and the effective area of the shell. See example calculations on the following pages.
fl3, where b = the
96
STIFFENING RINGS Moment ofInertia (I) - Example Calculations (All dimensions in inches - R = 72 in. outside radius of shell)
1 = 0.78.JRd; = 0.78 -.J72 x 0.5 = 4.68
AREACDIg b~ d3 9.86xO.5 3 =0103· 4 12 12 . Ill.
AREAQ)lg b J.,3 3 ~ 0.5 x 6 = 9 00· 4 12 12 . Ill.
MARK OF AREAS
2
AREA a 4.93 3.00
TOTAL
A=7.93
I
c
Y
axy
h
h2
a x h2
0.25 3.50
1.23 10.50
1.23 2.02
1.51 4.08
7.44 12.24
AY=I1.73
-
= AY = 11.73 = 1 48 A 7.93 .
-
.h.di 12 0.10 9.00
AH2=19.68 Jg=9.10
-
1= AJ{2 + 19 = 19.68 + 9.10 = 28.78 in.4 1 - 1.56
-fiid; =
1.56 -/72 x 0.25 = 6.618 AREACDIg 3
d !l.L.J 12 -
13.74 x 0.25 3 - 002· 4 12 - . Ill.
AREA(2)
2b2~
= 0.50 x 6 3 12
--
12
=
900· 4 . Ill.
bet
OF AREAS
AREA a
y
axy
h
2 h
axh2
12
CD
3.43
0.125
0.43
1.455
2.12
7.27
0.02
(2)
3.00
3.250
9.75
1.670
2.79
8.37
9.00
TOTAL
A =6.43
MARKS
-
C=AY = 10.18 = 1 58 A 6.43 .
AY= 10.18
-
-
AH2= 15.64 Jg=9.02
I=AH2 + Ig= 15.64 + 9.02 = 24.66 in.
4
97
STIFFENING RINGS Moment of Inertia (/) - Example Calculations (All dimensions in inches - R = 72 in. outside radius of shell)
cJ
b3 =4.00
L
--=r=----r----rr""""""'--
~~
~
-.i
AREA CD Ig b d! 9 86 0 53 on...l......l...=. x. r12 12
0
~
II O""l::!
I=0.78-{RJl=
1
~ 3 /hr~t---x-----'0.78~72 x 0.5=4.68 I/G ~ ~--~~--------------~ N 6 Vv 1 I~ Vv ~ ..s:: X--lf-7
and Ring
\0
.".
~ II
'"
b2= 1=4.68IU·)1 1=4.68
on
AREA
MARK OF
a 4.93 3.00 2.00 A=9.93
AREAS 1 2 3
TOTAL
c
6
3
b 3 d'= 4 x 0.5 =004'
II
::.:
12
:;=;
~ 7 ""l::!
4
h2
a x h2
0.25 3.50 6.75 -
1.23 10.50 13.50 AY=25.23
2.29 0.96 4.21
5.24 0.92 17.72
25.83 2.76 35.44 AH=64.03
-
:a ~
bd-'
12 0.10 9.00 0.04 Jg=9.14
1= AJ{2 + Ig = 64.03 + 9.14 = 73.17in.4
1 - 1.56 Wid; = ~I 1.56 \172 x 0.25 = 6.618
V/ /(3)%;.z;t-·-'--::-:-Pl--r~
m.
h
02511=6.618
0 0
.
axy
= AY = 25.23 = 254 A 9.93 .
.,;"
12
Y
m----.c--r--:-J.1-~ ~LQ=~3=8.00lbL~1 P2~1 \0
4
AREAQ)Ig
N
b l = 9.86
o
0 103'
. m. 'IT' +--____::::--______________--1 ~ g; 0 ~ AREAQ)Ig SHELL~ ~ ~ ~ b ct!. 0 5 63 ~ '" --.l...J...-~-900· 4 ~~SV///A0::::-::::- :~ ~ 12 12 - . m.
I~ r- -I:--""l::! - -
o
~
~ ./1
"g i:G r/l '"
>k
%
I
%
/..,
§ ;g
..s::A }
on r-
AREA CD Ig b 1d13 _ 13 •74 x. 025 3 _002' . In. 4 12 12 -
\0 -;7; e;;-1 a-7;r"': -'r-~--X-:%r---~ x '--,~ ~ 'IT' ~------------I
~
Shell ___.
N
"
~"'
..s:: r-.i II
0
~
AREAQ) Ig b d3 3 4 22_0.50x6 _9.00in. 1212 -
on
on N
~...; ~
I!.,
/~
//
5~~hh* b2+1~6.868
~
b2+I~6.868
II
bl-13.74
~
bet'
AREA a
y
axy
h
2 h
a xh2
12
1
3.43
0.125
0.43
2.59
6.72
23.09
0.02
2
3.00
3.250
9.75
0.53
0.28
0.84
9.00
3
2.00
6.375
12.75
3.66
13.40
26.80
0.01
TOTAL
A = 8.43
-
AY=22.93
MARKS OF
AREAS
C=AY = 22.93 = 272 A 8.43 .
-
-
AH2 =50.73 Jg= 9.03
1= AH2 + Ig = 50.73 + 9.03 = 59.76 in.4
98
DESIGN OF SADDLES WEAR PLATE HORN OF SADDLE MAX. EFFECTIVE AREA
1.
The saddle at the lowest section must resist the horizontal force (F). The effective cross section of the saddle to resist this load is one third of the vessel radius (R).
F=KlIQ, Where
Q= the load on one saddle, lbs. KII
= constant as tabulated.
The average stress shall not exceed two thirds ofthe compression yield point ofthe material. (See example below.)
Contact Angle
.318
EXAMPLE: Diameter of vessel = 8' - 6" Weight of vessel = 375,000 Ibs. Q = 187,500 Ibs. Saddle material: SA 285 C Web plate thickness = 0.25 in. Contact angle = 1200 KIt = 0.204 from table above Rl3 = 51/3 = 17 inches Force, F = K/l X Q = 0.204 x 187,500 = 38,250 lb. To resist this force the effective area of web plate = Rl3 x 0.25 38,250/4.25 = 9,000 Ibs. per square inch. The allowable stress = ~ x 30,000
= 4.25 in?
= 20,000 psi.
The thickness of the web plate is satisfactory for horizontal force (F). 2. The base plate and wear plate should be thick enough to resist longitudinal bending over the web. 3. The web plate should be stiffened with ribs against the buckling.
99 EXPANSION AND CONTRACTION OF HORIZONTAL VESSELS
I:
. Ii. SADDLES ,BOLTS
i'
i
a
.1
2
ct
BOLTS SADDLES
t---+
+.-~
EXPANDING VESSEL
CONTRACTING VESSEL
I
For thermal expansion and contraction, one of the saddles, preferably the one on the opposite side of the pipe connections, must be allowed to move. In this saddle for the anchor bolts slots are to be used instead of holes. The length of the slots shall be determined by the expected magnitude of the movement. The coefficient of linear expansion for carbon steel per unit length and per degree F =0.0000067. The table below shows the minimum length of the slot. Dimension "a" calculated for the linear expansion of carbon steel material between 70 0 F and the indicated temperature. When the change in the distance between the saddles is more than 3/8" inch long, a slide (bearing) plate should be used. When the vessel is supported by concrete saddles, an elastic, waterproof sheet at least 1/4" thick is to be applied between the shell and the saddle. MINIMUM LENGTH OF SLOT (DIM. "a")
a8
'0
41
:a "0
1i3 "0 c
'"
[/)
(:;01
'"
The width of the slot equals the diam. of anchor bolt + ~".
DISTANCE BETWEEN SADDLES
Ft. 10 20 30 40 50 60 70 80 90 100
FOR TEMPERATURE of
-50 100 200 300 0 0 1/4 1/4 3/8 3/8 1/2 1/2 5/8 5/8
0 0 1/8 1/8 1/4 1/4 1/4 3/8 3/8 3/8
0 1/4 3/8 3/8 1/2 5/8 3/4 3/4 7/8 1
400
1/4 3/8 3/8 5/8 5/8 7/8 3/4 1-1/8 1 1-3/8 1-1/4 1-5/8 1-3/8 1-7/8 1-1/2 2-1/8 1-3/4 2-3/8 1-7/8 2-5/8
500
600
700
800
900
3/8 3/4 1-1/8 1-1/2 1-5/8 2-1/8 2-1/2 2-7/8 3-1/4 3-5/8
1/2 1 1-3/8 1-7/8 2-1/4 2-3/4 3-1/8 3-5/8 4 4-1/2
5/8 1-1/8 1-5/8 2-1/8 2-5/8 3-1/8 3-5/8 4-1/8 4-5/8 5-1/8
3/4 1-1/4 1-5/8 2-3/8 3 3-5/8 4-1/4 4-7/8 5-3/8 6
3/4 1-3/8 2 2-1/2 3-3/8 4-1/8 4-5/8 5-3/8 6 6-5/8
100
SADDLE FOR SUPPORT OF HORIZONTAL VESSELS
,"min.
---t......-H
~~--------A--------~~
The design based on: 1. the vessel supported by two saddles 2. to resist horizontal force (F) due to the maximum operating weight ofvessel as tabulated. 3. the maximum allowable stress is % of the compression yield point: % of 30,000 = 20,000 psi. 4. the maximum allowable load on concrete foundation SOO psi. S. the minimum contact angle of shell and saddle 120°. Weld: 1;4" continuous fillet weld all contacting plate edges. Drill and tap 1;4" weep holes in wear plate. At the sliding saddle the nuts of the anchor bolts shall be hand-tight and secured by tack welding.
SEE FACING PAGE FOR DIMENSIONS
101
SADDLE NOMINAL DlAM. OF VESSEL FT. - IN.
DIMENSIONS
NO. OF RIBS
PLATE THICKNESS INCHES WEB, BASE WEAR FLANGE, G K RIBSH
MAXIMUM WEIGHT ON VESSEL
A FT.-IN.
B FT.-IN.
C IN.
D IN.
E FT.-IN.
BOLT DlAM. INCH
0-1O~
1-0
4
4
0-3~
~
0
Y4
Y4
-
42000
1-2
1-~
1-1
4
4
0-4
~
0
Y4
Y4
-
50000
1-4
1-2
1-2
4
4
0-5
~
0
Y4
Y4
-
56000
1-6
1-3~
1-3
4
4
0-6
~
0
62000
1-5~
1-4
4
4
0-6~
~
0
-
70000
1-10
1-7
1-5
4
0-7
~
0
76000
1-9
1-6
4
0-7~
Y2
0
Y4 ';4
-
2-0
6 6
Y4 Y4 ';4
-
1-8
Y4 Y4
Y4
-
84000
2-2
1-1O~
1-7
4
6
0-8
~
0
';4
90000
2-~
1-8
4
6
0-8~
~
0
~
Y4 ';4
Y4
2-4
98000
2-6
2-2
1-9
4
6
0-9
~
0
~
Y4
Y4 ';4
2-8
2-4
1-10
4
~
0
~
Y4
Y4
112000
2-5
1-11
6
6 11
0-9~
2-10
0-10
~
0
~
Y4
Y4
128000
3-0
2-6~
2-0
6
11
0-11
~
0
~
';4
Y4
134000
3-2
2-9 2-11
2-1 2-2
6
11
1-0
%
0
Y2
Y4
Y4
144000
6
11
1-1
%
0
~
210000
3-~
2-3
6
11
1-2
%
0
~
i i
3
3
220000
3
252000
1-0
3-4 3-6 4-0
3-6
2-6
6
11
1-4
3
%
0
%
8"
1-6
%-
0
%
3
8"
%
I
%
%
1
%
1
%
i i i
4-6
3-11
3-0
6
II
5-0
4-4
3-3
6
11
5-6
4-9~
3-6
6
11
1-8 1-10
18
2-0
%
2-2 2-4
%
1
%
~
1
1
%
1 1
6-0
5-2~
3-9
9
6-6
5-8
4-0
9
18
7-0
6-1
4-3
9
18
9
18 18
2-6
1
2-8
I
18 18
2-10
1 1
2
1';4
2
7-6
6-6
8-0
6-Il~
4-6 4-9
8-6
7-4~
5-0
9
9
9-0
7-9~
5-3
9
9-6
8-3~
9 9
24
3-0
2
8" 8" 8"
104000
i
282000
3
312000
~
344000
8" 8
~
402000
3
436000
~
~
470000
%
~
502000
1
~
i i
1 1
~
~
760000
~
~
806000
%
~
852000
8
8" 8
536000
10-0
8-8
5-6 5-9
24
3-2 3-4
lY4
2
I 1
%
~
896000
10-6
9-1~
6-0
9
24
3-6
IY4
2
1
%
~
940000
11-0
9-6~
6-3
9
24
3-8
IY4
2
1
%
~
986000
11-6
10-0
6-6
9
24
3-10
IY4
3
1
%
~
1030000
12-0
10-5
6-9
9
24
4-0
IY4
3
1
%
Y2
1076000
102
STRESSES IN VESSELS ON
LEG SUPPORT
,t\
,/ I .\
I
tff-\\
/ R!
I
VIEW A-A
NOTATION: W = Weight of vessel, pounds n = Number oflegs Q = W Load on one leg, pounds n R Radius of head, inch H Lever arm ofload, inch Dimension of wear plate 2A.2B S Stress, pound per square inch t Wall thickness of head, inch Factors, see charts K
c c
i4.B,inch Radius of circular wear plate, inch
D
1.82 k
R
# t
LONGITUDINAL STRESS:
CIRCUMFERENTIAL STRESS:
NOTES: Positive values denote tensile stresses and negative values denote compression. Computing the maximum tensile stresses, in formulas for SI' S2 and K I . K J• Kj and K J denote negative factors and K 2• K 4• K6 and Ks denote positive factors. Computing the maximum compression stresses in formulas for SI' S2 and K I • K 2• K J• K 4• K j • K 6• K7 and Ks denote negative factors.
The maximum tensile stresses SI' and S2' respectively, plus the tensile stress due to internal pressure shall not exceed the allowable tensile stress value of head material. The maximum compression stresses Sf. and S2' respectively, plus the tensile stress due to internal pressure shall not exceed the allowable compression stress value of head material.
103
STRESSES IN VESSELS ON LEG SUPPORT
0.30
\
1\
0.25
\
\
0.20
~ 0.15
.,/
......
"-
~
r-.....
-
K """" r-.... I--
0.05
......
o
V
"
~
~ 0.10
.,/KI
,
1\
14")
"""" .....
............ t......
~~~~~~ oooo~~
-
r---~
r--
tr: ~
o N
D
VALUE OF K 1 , & Ks
0.35 0.30 I,Q
~ ~
0.25 0.20
~
0.15 0.10 0.05
\
\ ~ \
V
1\
\
K2
.,/
\;
\
v
,./"
v K6
K r-.....
\ ...............
............
t-- 1-0.. ~~~~~~ oooo~~
r---
tr: ~
0
N
VALUE OF K2 , & K6
D
104
STRESSES IN VESSELS ON LEG SUPPORT
0.20-1--+--1-+--+--+-+--+-_-+-_-+-_-+-_-4-_-1
~t--. 0.15 ~~
I
/K3
'"
r/~~~~~~,/~~--~~---r--l
'"
0.1 0~/1-+--I-+-+-+-I--",",,~--+---+--+----1---I 0.05
"~
K7
./
/ ~~~~~~
"!
0000--
-
o
o
N
M
D
0.60 -++r-+-+--+-+-It--+--+---+--I---+__--I QQ
~
~~
0.50 +-1+-+--+--+--+-+---+----+---+---+---+---1 0.40 -It-4f--1--+-+--+--+----+---+---+--+---I----I 0.30
+t-t+l_+_~.......,.v--+-K_s+--_+_-_+_-_t_--t--_I \\V'-
0.20 ~,~--+-_+_+-It--+--+---+--I---+__--I
\ 1\ V 0.10 -+-f->od--t"""d--t-t-::--"'+--_t_--t--_t_--t--_I f'... ___ :: k __ r-K4
oL..+--'--'-+':~::::j;;;~=+=::;;;;;;j-=-I--+--......t
C"! ~ ~ ~ ~ C"! 0000--
"!
0
-
N
VALUE OF K4 , & KS
D
105
STRESSES IN VESSELS ON LEG SUPPORT EXAMPLE CALCULATIONS DESIGN DATA W = 800,000 lb. weight ofvessel n = 4, number of legs
W 800,000 Q = --;; = - 4 - = 200,000 lb. load on one leg R = 100 inch, radius of head H = 5 inch, lever arm of load 2A = 30 inch, 2B = 30 inch, dimensions of wear plate t = 1.8 inch thickness of head cos IX = 0.800 P = 100 psi, internal pressure Head material: SA 515 -70 Allowable stress value: 20,000 psi Joint Efficiency: 0.85 Yield Point: 38,000 psi Factors K (see charts):
C = {AS = ..J 15 x 15 = 15 inch D= 1.82
C _ fR
R "
15 _
rwo " 1:8 =2.0-,
t = 1.82 100"
K j = 0.065, K5 = 0.020,
K 2 = 0.030 K6= 0.010
K3= 0.065 K7= 0.022
K4 = 0.025 Ks = 0.010
LONGITUDINAL STRES: 1.) Maximum tensile stress: Sf =
~ [cos
IX
(-K j + 6K2 ) +
Z~ ~ (-
K3 + 6K 4 ) ]
S = 200,000 [0.800 (- 0.065 + 6 x 0.030) +2.. - I 100 j 1.82 100 -" 1.8 (-0.065 x 6 x 0.025) ] =+7,634 psi The stress due to internal pressure: PR 100xl00 .
2t
2 x 1.8
+ 2778
PSt
The sum of tensional stresses: 7.634 + 2.778 = 10,412 psi It does not exceed the stress value of the girth seam: 20,000 x 0.85 = 17,000
106
STRESSES IN VESSELS ON LEG SUPPORT EXAMPLE CALCULATIONS 2.) Maximum compressional stress: Sf
=7
[cos oc(-K,-6K2) +
~~ ~ (-KJ -6K)]
_ 200,000 [ --L_/IOO ] 1.82 0.800 (-0.065-6x 0.030) + 100 -\I IT (- 0.065-6x 0.025)
Sf -
=
-
17,044 psi
The stress due to internal pressure: PR
Tt =
100 x 100 2 x 1.8 = + 2,778
The sum of stresses: - 17,044 + 2,778 =
-
. pSI
14,266 psi
It does not exceed the stress value of the girth seam: 20,000 x 0.85 = 17,000 psi
Circumferential stress: 1.) Maximum tensile stress:
_~[ I J i )] (2 cos oc(-K j + 6Kr,) + H R -\I _ (-K--6K N
S2 -
S2
=
200,000 [ 5 -/100 ] 1.82 0.800 (-0.020 + 6x 0.010) + 100 -\I TI (- 0.022+6x 0.010) = + 2,849 psi
The stress due to internal pressure: PR 100x 100_ 2778 . 2t = 2 x 1.8 - + , pSI The sum of tensile stresses: - 2,849 + 2,778 = - 5,627 psi It does not exceed the stress value of the girth seam: 20,000 x 0.85 = 17,000 psi
2.) Maximum compressional stress:
S2=~ [cos cc(-K S2=
j
-6Kr,) +
~~ ~(-K--6KN)]
200,000 [ ---L_/IOO ] 1.82 0.800 (-0.020-6x 0.010) + 100-\1 T.8(-0.022-6xO.01O)
= - 5,837 psi
107
STRESSES IN VESSELS ON LEG SUPPORT EXAMPLE CALCULATIONS The stress due to internal pressure: PR 100 x 100 2 778 . 2t = 2 x l.8 = + , pSI The sum of stresses: - 5,837 + 2,778 = - 3,059 psi It does not exceed the stress value of the girth seam:
20,000 x 0.85
=
17,000 psi
108
LEG SUPPORT
Notch out angles to clear seam -~n
SECTION A-A
.---t -, VESSEL DIA 2'-6" 3'-0" 3'-6" 4'-0" 4'-6" 5'-0" 5'-6" 6'-0" 6'-6" 7'-0" 7'-6"
1 max
VESSEL HEIGHT MAX
ANGLE SIZE
8'-0"
3" X 3" x 3/8"
10'-0"
3.5" X 3.5" x 3/8"
6"
14'-0"
4" X 4" X 112"
7"
16'-0"
5" X 5" X 112"
W
4" 5'-0"
10" 7'-0"
18'-0"
6" X 6" X 5/8"
1'-0"
109
STRESSES IN VESSELS DUE TO
LUG SUPPORT
~
r-Ri
Ul--r-r
r 28 "I
41""'
:J[[]
!
H "" ..!L. ~t-----+---~-
:
Q
I
Q
T UN STIFFENED SHELL
NOTATION: W = Weight of vessel, lb n = Number of lugs W Q = - = Load on one lug, lb
n R = Radius of shell, in H = Lever arm of load. in
STIFFENED SHELL
2A, 2B = Dimensions of wear plate
S = Stress, pound per sq. in t = Wall thickness of shell, in C = shape factor, see table K = Factors, see charts
D=
d R
,,3rT V
A
WNGITUDINAL STRESS:
S = + 1
-
QH D R2t
NOTE: In tension S1 plus the stress due to internal pressure PRJ2t shall not exceed the stress value of shell material times the efficiency of girth seam.
CIRCUMFERENTIAL STRESS: S 2
=
+ -
QH
DR 2 t
NOTE: In tension S2 plus the stress due to internal pressure PRJt shall not exceed the stress value of shell material multiplied by 1.5.
110 STRESSES IN VESSELS DUE TO LUG SUPPORT
12
r-... "'-
~
1/
~
"~
J
rl
10
~ ~
,I '-,..-
-J
f-- f -
4
i-
j
~
2
~V~1/V
Il
I
1/
II
J
o r. . . I"
o
•
~
~
'~
-- ~~Po f--
~~
t/'
II
........
-'-
~-
1I
-
~
t7 V-
~
,
~
---- ._- -_.
~
'\
P
~
_._-
0.10
~
~~
-
f---
..",.,..
""""
-
r\ "' \ ~
~~
~
..... r--..
r- !-
~~
t--
;:
-- f--
-- .- -
- -- -
0.15
-
--
0.20
o VALUE OF K]
f-- f--
\.
""-" !"-
-f-
1\
\.
a.D.: ---
~
-- "" ",~
70 )
-
I--
f"'.
" r\
r\.
f-- f--
~ f---
~
~ I\.
"""....
- 1-
'1 II
1---
~
.......
,,
~
" '" I'
~
I-- ~
0.05
I""'oi ~
I'
1/ .",
~:;'n ..
- "P ~ 'r\. '\
~
,/ ~ ,,;t! --- - ;,;.- ~ ~
-j rJrJl/ v l? ~ '/
~
1\
!--
fI'
I
""
V
~
)
II [l
I--
f-- f--
II
"J I[
, /--II
i'-
II
~
'\
..........
V
8
6
~
1\
0.25
111
STRESSES IN VESSELS DUE TO WG SUPPORT
0.12
~~
t' ~ 0.10 ~ ~ ,,\ '\
'" , ~
:~ ~
~
~ '\
~ ~l\ [\ '\ ~ [\ r\ ~ 1\
\',V\'
0.08
'\,\
1\.'
' ~\ 1\ \
\
0.06
1\
~
,f\
~
\
~\
~
--
~
~
""" \.
0.04
l\.
,~\ ~ ~ I\. f\." ,\ \ ,K\ ~ , ~r" ; \ \ ~ "-
:\
~-
'\
f---.
---
\ f---
~
~
0.02
~
--
--
f--
'\
~"'" ~ IL l' re 7
.~
~
D ~
. ~O
~
- -- -
-
----
o
._.-
0.05
--.--- ---
-
.
-
~
-. r-.. ~ ~ -" ~ ~C r\ ... r"- ~ ~.. r--.. ~:--... '""'" "~ f'... ~ . ~ r-... :--... ......I--
f---
~.
~
-- . - --
o
~
-
-
.J
~
....... ....... O( .i'oo """'- ...... ......
0.10
~ .......
0.15
,
to-
" --- - ----~
..... .....
~
f-
0.20
((2 0) VALUE OF K2
r"'-- r--.
~
0.25
112
STRESSES IN VESSELS DUE TO LUG SUPPORT
35 '-
,
1/ 1\ I
4
1\
II
30
J
\
I
rn
J J I
~
25
I
I
t-t--
t~I
t--
'---l-}
, -~-
II
t---
10
-llI-
j
'I
~,
li~ ,,7 /.
o
"1 'f-r 7" 1--' ~---
o
--
--
-
"'"!o
/ 'f
"
~ 1-"""
'7
-- -
0.05
~ ---
::J
,
.,.
\ \~
~ ':/
--
-
/
,,'~
~\, '7 ~ \
r" ~ ,\
~
-
~
~,
\
--
--
--
-- --
---
- -- -
~ 7 1\ \ [\ I"'" ~ ~ \ i\ rs S ~D ~ K .'\
~-
---
-
-
-- - -- --- --- r--
-
1---- '---
-----~
--- .... - - -
--
I---
~
~
" --
2 -- - ~
f-
-\'"\
\
-
I /. -1/ 7
t
rJ
5
~-
- I- t .J
~
\'
-
I
15
--
,
\
I
J
e_
\
,
~
J I
20
---
\
()/ ~~
I r---
, S -
--- ~ -.....;
--
--
~
po ~ 1,.000" r--
,....
........
~~
-5 fL-
-- t--
~~ ~ ~
r-
-
~
1---
-
"'"-~~~ """r--.~ ~~ ~
- ~ ~ ~~ ~~
---
----
-- I--
1----
~
~
~
r---r--., ~ --- r-r--.
i"""" ~ ......
r--. ......
-- -
1---
-----
---~
r-I---
---r-- -- ---
--
0.10
0·15
0.20
o VALUE OF K3
0.25
113
STRESSES IN VESSELS DUE TO LUG SUPPORT
0.08 ~~
1'\ ~ ~ .....
0.06
~ ~ ~ ~. ~ ~ t\.: ~ ~ ~~~~
,
\\ ,,\[\ ~
\'\ ~~\ \'\ "", f:,(1 t-- Sl ~~i~ " !\ " , ~" ~- ......
0.04
~.-
.....
~
"
'("
~,
\ !\ '0,
0.02
~
-
"
.....
... ~
"-
'~.)
........ <~~ r-
o
tL ,
r--. """-
'a, '11 " r-r-
0.10
0.05
....... ............ ......
r--. .....
r"o ~ PC v
o
~
~
~ ~
--
~
r-- r--.
-- -- --- - - 1
~ ~ .....
"'U ..... .....
.....
......
r-- ~ r-- r-~ '~
'"'-
r-I-r-o ~
0.15
0.25
VALUE OF K4 BIA
112
1
2
Rlt
C}
C2
C3
C4
50
0.72
1.03
0.95
1.07
100
0.68
1.02
0.97
1.06
200
0.64
1.02
1.04
1.05
300
0.60
1.02
1.10
1.04
50
1
1
1
1
100
1
1
1
1
200
1
1
1
1
300
1
1
1
1
50
0.85
1.10
0.85
0.92
100
1.15
1.07
0.81
0.89
200
1.32
0.98
0.80
0.84
300
1.50
0.90
0.79
0.79
VALUE OF C
114
STRESSES IN VESSELS DUE TO LUG SUPPORT EXAMPLE CALCULATIONS DESIGN DATA W = 1,200,000 lb. weight of vessel n = 4 number of lugs W 1,200,000 3 000 Q = -;; = 4 = 00, lb. load on one lug R = 90 in, radius of shell = 5 in, leverarm of load 2A = 30 in, 2B = 30 in, dimensions of wear plate t = 1.5 in, thickness of shell p = 100 psi internal pressure
H
Shell material: SA - 515-70 Allowable stress value 20,000 psi Yield point 38,000 psi Joint Efficiency: 0.85 Shape factors C, (see table): 90 R/t = ~ = 60, B/A = 15115) = 1,0 C]
=
C2
=
C3
= C4 = 1.0
The factors K, (see charts) D =
d ~3 / ~ R
VA
K] = 2.8,
12 ~3 {fJ =
=
90
V 15
K2 = 0.025,
Q 6
.1 7,
R/t = ~ 1.5
60
K4 = 0.021
K3 = 6.8
Longitudinal Stress:
s]
300,000
x 5
X
90 2
= 0.167
( X
1
x 2.8 + 6 0.025 x 90 1 x 1.5
1.5
+ __--.:0~..!..:I6~7_ _ _ )( 90 2 2 (1.17 + 15/15) 5 x 15
)
Stress due to internal pressure: PR 100 x 90 2t 2 x 1.5 = 3000 psi
= 11,795
+
psi
The sum of tensional stresses: 11,7:95 + 3000 = 14,795 psi
It does not exceed the stress value of the girth seam: 20,000 x 0.85 = 17,000 psi.
115
STRESSES IN VESSELS DUE TO LUG SUPPORT Circumferential Stress: S2
=±
Q~
DR t
( C3 K3
+6
R ) C4 t K4
300,000 x 5 ( S2 = 0.167 X 902 x 1.5 1 x 6.8 Stress due to internal pressure: PR 100 X 90 6000" = pSI 1.5
+6
0.021 x 90 :\ 1 x 1.5 -; = 10,616 psi
The sum of tensional stresses: 10,616 + 6000 = 16,6l6 psi
It does not exceed the stress value of shell material multiplied by 1.5: 20,000 X 1.5 = 30,000
116
LUG SUPPORT FOR INSULATED VESSELS
t
,
,/
L
T I
',.-
I,
L
l
~ ~.
~b/~ It
b
.,
TT -
--tk~
_t
LL
lMaximum Allowable Load on One Lug, Lbs.
600
t1--
~~ DIMENSIONS
Weight of One Lug, Lbs.
II
b
bl
h
hI
k
IF
t
w
1,400
6Y2
5
5Y2
3%
4
%
5Y4
Y4
Y4
7
2,200
6%
5Y2
6
5
5Y4
%
5Y2
Y4
Y4
9
3,600
8Y4
6%
7 1/4
6%
7
%
6%
Y4
Y4
16
5,600
lOY4 8%
9Y4
9%
91"s
1
8Y2
Y4
Y4
24
9,000
12Y2 10% 11 Y2 14Y4 14%
1
lOY2
%
%
58
ITYs
1
11 Y2
%
%
72
1Y4
12Y2
Y2
%
126
22%
Pis
14
%
Y2
165
29
1%
16Y2
%
Y2
235
14,000
13% 11 Y2 12Y4
22,000
15Y2
36,000
17Y2 14% 15Y2
56,000
20Y2 17Y2 18Y2 28%
90,000
22% 18Y2 19Y2 31 Y2 32Y4
1%
18
%
Y2
388
140,000
25Y4 20Y2 21 Y2 34% 35%
2
20
%
Y2
482
13
17
13% 18Ys 18% 22
All dimensions are in inches Stresses in vessel shall be checked. Use wear plate if necessary
117
LUG SUPPORT
FOR UNINSULATED VESSELS
f L"
,
,
"""
T I
'F
i
r
'"
~b,~ It
b
-1kl--
-I
IT -
1-+-1
LL
Maximum Allowable Load on One Lug, Lbs.
600
11--
-r:-~ DIMENSIONS
Weight of One Lug, Lbs.
I]
b
bl
h
h]
k
If
t
w
1,400
2Yz
2
2~
4
4%
%
1~
3/16
full
1
2,200
314
2~
3
51;4
57/ 16
%
2
3h6
full
2
3,600
4
31;4
3%
6%
616/](;
%
2~
3/16
full
4
5,600
5%
5%
61;4
9%
10
1
4
1;4
1;4
9
9,000
7%
7
7%
141;4 149h6
1
5~
5/16
1;4
21
14,000
9Y2
8~
91;4
17
175/16
1
6~
5h6
1;4
28
22,000
10
9~
101;4
18
183/8
11;4
7
3fs
1;4
45
36,000
12
11~
12~
22
22~
11;4
9
~
3/16
80
56,000
15
15
16V4
28~
79 1/ H 1V4
12
9/ 16
3/ 8
148
90,000
16~
15%
17
31~
321/8 PI.!
13
5/ 8
3/ 8
218
18
17~
18%
14
5/ 8
3/ 8
260
140,000
34Yz 3Sl/8
All dimensions are in inches. Stresses in vessel shall be checked. Use wear plate if necessary.
2
118
LIFTING LUG
D·l
H
l"~
ex:
r t--._._._._._._.+ VESSEL WEIGHT (Lbs)
D (In)
'-I--.J-.--.
T (In)
R (In)
H (In)
L (In)
12,000
1
12
112
5
10
20,000
ll/x
%
2
6
10
-::r
30,000
Pix
1
21/x
50,000
Pix
11;4
212
7
12
70,000
21/x
11;4
312
8
12
100,000
212
112
412
9
16
150,000
-''"
p~
5
WELD (Min)
6
10
10
16
~--d
s::
..c:;:l ."t:::: 0
:::
~
-V
ca
-0::::
::::9 0) 0) > ::: 0 ...... o 0)
1-0:::: OJ)t;:::
0:)0
> s::
0)'-
.D
200,000
4
2
6
12
18
250,000
41;4
2
612
13
18
300,000
412
212
7
14
20
00
,;;;-
-x .Dca ga 0)
a~
Notes: 1. All dimensions are in inches. 2. The design is based on conditions: a. ex: = 45° maximum b. Minimum tensile strength oflug material 70,000 psi. c. Direction of force is in the plane oflugs. 3. Use wear plate if necessary to eliminate buckling due to normal or sudden loading.
119
LIFTING ATT ACHMENTS
•. /*
__ ~SHACKLE
:
"
\."
~ ::r:
.'
" \ \.
I / :!
I I
I
I
I
I
E:b~~.+=f '.
t
-
U
V//////////~
.Jfr'
/O.~
CQ
/
<
LUG
I?';\ ."\... '\::.~
"-
tD1
oV///////ft/////////A'
MINIMUM DIMENSIONS OF LIFTING LUGS USING SHACKLE Load Lbs.
Shackle Pin Diam. D
710 5/16 1060 3/8 1600 7/16 2170 1/2 2820 58 34 4420 6375 78 8650 1 11300 1-1 8 13400 1-1 4 16500 1-3 8 20000 1-1/2 23750 1-5/8 32350 2 42500 2-1/4 54000 2-1/2 67600 23/4 81000 3 97000 3-1/4
Hole Diam. in Lug Dl 38 7/16 1/2 5/8 3/4 7/8 1 1-1/8 1-1 4 1-3 8 1-1 2 1-5/8 1-3/4 2-1 8 2-3/8 2-5/8 2-7/8 3-1/8 3-3/8
Sheared Edge H
A
.50 .56 .63 .69 .94 1.13 1.19 1.31 1.50 1.63 1.75 1.88
.65 .73 .82 .90 1.22 1.47 1.55 1.70 1.95 2.12 2.28 2.45
2.25 2.56 2.81 2.94
2.93 3.33 3.66 3.82
All dimensions in inches,
I Rolled Gascut
B
78 1-1 8 1-1 4 1-1 2 1-3 4 2 2-1 4 2-7 16 2-5 8 2-7/8 3-1 16 3-3 4 4-18 4-9/16 5 5-7/16 5-7/8
Arm of Moment E
.84 .97 1.16 3/4 1.44 7/8 1 1.75 2.12 1-1/8 1-1 4 2.25 1-1 2 2.59 1-5 8 2.94 1-3 4 3.06 1-7 8 3.62 4.06 2 2-3 16 4.19 2-5 8 4.75 5.25 3 3-1 4 6.00 3-9 16 7.00 3-7 8 8.61 4-1/4 9.74
120 LIFTING ATTACHMENTS (cont.) RECOMMENDED MATERIAL: A 515-70, A 302 or equivalent. The thickness, and length of the lifting lug shall be determined by calculation: WELD: When fillet welds are used, it is recommended that throat areas be at least 50 per cent greater than the cross sectional area of the lug. To design the lugs the entire load should be assumed to act on one lug. All possible directions of loading should be considered (during shipment, storage, erection, handling.) When two or more lugs are used for multileg sling, the angle between each leg of the sling and the horizontal should be assumed to be 30 degrees. EYE - BOLT Threaded fasteners smaller than 5/8" diameter should not be used for lifting because of the danger of over torquing during assembly. -M!IOA--~W
Commercial eyebolts are supplied with a rated breaking strength in the X direction. For loadings other than along the axis of the eyebolt, the following ratings are recommended. These are expressed as percentage of the rating in the axial direction. X = 100% Y = 33% Z = 20% W = 10%
EXAMPLE: An eyebolt of 1 in. diameter which is good for 4960 lb. load in tension (direction x) can carry only 4960 x 0.33 = 1637 lb. load if it acts in direction y. The above dimensions and recommendations are taken from C. V. Moore: Designing Lifting Attachments, Machine Design, March 18, 1965.
•Assuming shear load only thru the minimum section, the required thickness may be calculated by the formula:
p
t= - - - - - -
28 (R-D f2.J 1
where
t =required thickness of lug, in. P
8
=load, lbs.
=allowable shear stress, psi.
See page 459 for design of weld and length of lug.
121
SAFE LOADS FOR ROPES AND CHAINS
The stress in ropes and chains under load is increasing with the reduction of the angle between the sling and the horizontal. Thus the maximum allowable safe load shall be reduced proportionally to the increased stress. If the allowable load for a single vertical rope is divided by the cosecant of the angle between one side of the rope and the horizontal, the result will indicate the allowable load on one side of the inclined sling. Example: The allowable load for a rope in vertical position is SOOO lb. If the rope applied to an angle of 30 degrees, in this position the allowable load on one side will be SOOO/cosecant 30 deg. = SOOO/2 = 4000 lb. For the two-rope sling the total allowable load 2 times 4000 = SOOO lb. The table shows the load-bearing capacity of ropes and chains in different positions. Multiplying with the factors shown in the table the allowable load for a certain rope or chain, the product will indicate the allowable load in inclined position.
FACTORS TO CALCULATE SAFE LOADS FOR ROPES AND CHAINS
Angle of Inclination
900
60 0
45 0
300
100
On One End
1.00
0.S5
0.70
0.50
0.17
1.70
1.40
1.00
0.34
On Two Ends
122
OPENINGS SHAPE OF OPENINGS: Openings in pressure vessels shall preferably be circular, elliptical or obround. An obround opening is one which is formed by two parallel sides and semicircular ends. The opening made by a pipe or a circular nozzle, the axis of which is not perpendicular to the vessel wall or head, may be considered an elliptical opening for design purposes. Openings may be of shapes other than the above. Code UG-36(a)(2) SIZE OF OPENINGS: Openings are not limited as to size. The rules, construction details of this handbook conform to the Code UG-36 through UG-43 and apply to openings: • for maximum 60 in. inside-diameter-vessel one half ofthe vessel diameter, but maximum 20 in. • for over 60 in. inside-diameter-vessel one third of the vessel diameter, but maximum 40 in. For openings exceeding these limits, supplemental rules of Code Appendix 1-7 shall be satisfied Code UG-36(b)(1) For nozzle neck thickness see page 140. WHERE EXTERNAL PIPING IS CONNECTED TO THE VESSEL, THE SCOPE OF THE CODE INCLUDES: (a) the welding end connection fQr the first circumferential joint for welded connections, (b) the first threaded joint for screwed connections, (c) the face of the first flange for bolted, flanged connections, (d) the first sealing service for proprietary connections or fittings. Code U-I (e)(1)
123
INSPECTION OPENINGS All pressure vessels for use with compressed air and those subject to internal corrosion, erosion or mechanical abrasion, shall be provided with suitable manhole, handhole, or other inspection openings for examination and cleaning. The required inspection openings shown in the table below are selected from the alternatives allowed by the Code, UG-46, as they are considered to be the most economical. INSPECTION OPENINGS ARE NOT REQUIRED: INSIDE DIAMETER OF VESSEL
over 12 in. less than 18 in.
J.D.
INSPECTION OPENING REQUIRED
two - l~ in. pipe size threaded opening
18 in. to 36 in. inclusive 1.0.
min. 16. in. I.D. manhole or two - 2 in. pipe size threaded opening
over 36 in. 1.0.
min. 16 in. I.D. manhole or two - 6 in. pipe size nozzle
1. for vessels 12 in. or less inside diameter if there are at least two minimum in. pipe size removable connections. 2. for vessels over 12 in. but less than 16 in. inside diameter, that are to be installed so that they must be disconnected from an assembly to permit inspection, if there are at least two removable connections not less than 17l in. pipe size. UG-46(e). 3. for vessels over 12 in. inside diameter under air pressure which also contain other substances which will prevent corrosion, providing the vessel contains suitable openings through which inspection can be made conveniently, and providing such openings are equivalent in size and number to the requirement of the table. UG-46(c). 4. for vessels (not over 36 in. 1.0.) which are provided with teltale holes (one hole min. per 10 sq. f1.) complying with the provisions of the Code UG-25, which are subject only to corrosion and are not in compressed air service. UG-46(b).
*
The preferable location of small inspection openings is in each head or near each head. In place of two smaller openings a single opening may be -used, provided it is of such size and location as to afford at least an equal view of the interior. Compressed air as used here is not intended to include air which has had moisture removed to the degree that it has an atmospheric dew point of ·50 F or less. The manufacturer's Data Report shall include a statement "for non·corrosive service" and Code paragraph number when inspection openings are not provided. NOZZLE NECK THICKNESS The wall thickness of a nozzle neck or other connection used as access or inspection opening only shall not be less than the thickness computed for the applicable loadings plus corrosion allowance.
124
OPENINGS WITHOUT REINFORCING PAD
Below the most commonly used types of welded attachments are shown. For other types see Code, Fig. UW-16.1. OTATIONS:
a= The angle ofbeveling shall be such as to permit complete joint penetration and complete fusion. Depends on plate thickness, welding procedure. t = Thickness of vessel wall less corrosion allowance, in. til = Nominal thickness of nozzle wall less corron A sion allowance. in. NOTES: I. When complete joint penetration cannot be verified by visual inspection or other means permited by the Code, backing strips shall be For detan used with full penetration weld deposited from lee filurea only one side. ~j.(J~~~B 2. The purpose of weld b is to eliminate the irregularities ofthe groove weld at the root and secure full penetration. It is urually one pass only and NOZZLE NOZZLE WITH may be omitted if not needed for the above WITH SLIP ON WELDING NECK FLANGE FLANGE purpose. 3. The weld sizes defined here are the minimum requirements. For calculation of strength of B welds, see page 136. 4. Strength calculation of welds for pressure loading are not required for attachments shown in fig. B, C, E, F, G, and for openings: 3 in. pipe size attached to vessel walls of 3/8 R-"'.......• in. or less in thickness, 2 in. pipe size attached to vessel walls over BACKING STRIP 3/8 in. thickness. (Code UG -36 (c) (3» R = the lesser of \;4 t, or % in. ,= Min. weld size = tor t" or 0.375 in. whichever
is the smallest, in. J + a] = 1114 x the smallest of t, til or I in. J or a} = the smallest of t, til or 0.375 in. = No minimum size requirement
tbrll H.
c
F a a R
R = the lesser of \;4 t, or 3;4 in. D
R = the lesser of \;4 t, or % in.
G a b
E
H
R
125
OPENINGS WITH REINFORCING PAD Below the most commonly used types of welded attachments are shown. For other types see Code, Fig. UW-16.1.
NOZZLE WITH WELDING NECK FLANGE
J
NOTATION: Minimum weld sizes, inches. Use the smallest values. a = tn or te or 0.375 in. b = No minimum size requirement. c = 0.7t, or 0.7te, or 0.5 in. d= 0.7!, orO.7tn, orO.7te, orO.75 in. e = I, or tp , or 1 in. cx;= The angle of bevel shall be such as to permit complete joint penetration and complete fusion. Depends on plate thickness and welding techniques. t = Thickness of vessel wall less corrosion allowance, in. Ie = Thickness of reinforcing pad less corrosion allowance, in. t n = Nominal thickness of nozzle wall less corrosion allowance, in. tp = Thickness of pad type flange, in.
NOZZLE WITH SLIP ON FLANGE
t'r1i ~
~~
R ' - Backing strip R = the lesser of 1;4 t, or 3;4 in.
SEE NOTES ON FACING PAGE. N
K
R = the lesser of 1;4 I or 3;4 in. L
til
-;
1/8"
Ir'
o
d
j R R = the lesser of 1;4 t or % in.
M
p
126 THREADED AND WELDED FITTINGS
THE FIGURES BELOW SHOW THE MOST COMMONLY USEL tYPES OF WELDED CONNECTIONS. SEE CODE FIG. UW-16.1 FOR afHER TYPES
A
B
c
D
b
NarATION
a = t, t" or 0.375, whichever is the smallest, in. a J + a 2 = 1-1/4 times the smallest of t, t" or 1 in. a J or a 2 = the smallest of t, tn or 0.375 in. b = no minimum size requirement c = the smallest of t or 112 in. d = the thickness of Sch 160 pipe wall, in. e = the smallest of t or 3/4 in. t = thickness of vessel wall, less corrosion allowance, in. I" = nominal thickness of fitting wall less corrosion allowance, in.
The weld sizes defined here are the minimum requirements.
SEE NarES ON FACING PAGE
127
THREADED AND WELDED FITTINGS THE FIGURES BEWW SHOW THE MOST COMMONLY USED TYPES OF WELDED CONNECTIONS. SEE CODE FIG. UW-16.1 FOR OTHER TYPES
a SEE NOTATION ON FACING PAGE: G
---+c
~~~~~~~~~~
~~~~__~~~~-te
D max
=
outside diameter of pipe
+ 3/4
Max. pipe size: 3 in. in.
FITTINGS NOT EXCEEDING 3 IN. PIPE SIZE. In some cases the welds are exempt from size requirements, or fittings and bolting pads may be attached to the vessels by fillet weld deposited from the outside only with certain limitations (Code UW-16 (t) (2) and (3)) such as: 1.
The maximum vessel thickness: 3/8 in.
2.
The maximum size of the opening is limited to the outside diameter of the attached pipe plus % in.
3.
The weld throat shall be the greater ofthe minimum nozzle neck thickness required by the Code UG-45(a) or that necessary to satisfy the requirements ofUW 18 for the applicable loadings ofUG 22.
4.
The welding may effect the threads of couplings. It is advisable to keep the threads above welding with a minimum 1;4 in. or cut the threads after welding.
5.
Strength calculation of attachments is not required for attachments shown in Figs. A, C and E, and for openings: 3 in. pipe size fittings attached to vessel walls of3/8 in. or less in thickness, 2 in. pipe size fittings attached to vessel walls over 3/8 in. in thickness. (Code UG36(c)(3)).
128 SUGGESTED MINIMUM EXTENSION OF OPENINGS The tables give the approximate minimum outside projection of openings. When insulation or thick reinforcing pad are used it may be necessary to increase these dimensions. OUTSIDE PROJECTION, INCHES USING WELDING NECK FLANGE NOM. PRESSURE RATING OF FLANGE LB FIPE 900 150 300 600 1500 2500 SIZE
• g
\
I
! 1
Q)';::
"t:IV 'r;;.~
"0
~~;-t- . ~
SIS.
2 3 4 6 8 10
I
12 14 16 18 20 24
6 6 6 8 8 8 8 8 8
6 6 8 8 8 8 8 10
10 10
10 10 10
10
10
6 8 8 8 10
10 10 10 10
12 12 12
8 8 8
8 8 8
10 10
10
12 12 14 14 14 14 14
8 10
12 14 16 20 22
12 14 16 16 16 18 18 20
OUTSIDE PROJECTION, INCHES USING SLIP ON FLANGE NOM. PIPE SIZE
I
c
0
!
1
1»: "t:IV '-Q) "'..... "0 :S .. OQ,
~~:-r:~"~ -v
I
2 3 4 6 8 10
12 14 16 18 20 24
PRESSURE RATING OF FLANGE LB
150
300
600
900
1500
6 6 6 8 8 8 8 10
6 6 8 8 8 8
6 8 8 8
8 8 8
8 8 10 12 12 12 12
10
10 10 10
10 10 10
10 10 12
10
10 10 10
12 12 12 12
AAcA Flush Pipe cut to the curvature of vessel
Set flush not cut to the curvature
Minimum extension for welding
10 10
12 12 12 12 12 12 12
2500 8 10 10
12 12 14 16
d~ Extension for reinforcement or other purpose
129
REINFORCEMENTS OF OPENINGS DESIGN FOR INTERNAL PRESSURE Vessels shall be reinforced around the openings, except single, welded and flued openings not subject to rapid pressure fluctuations do not require reinforcement if not larger than: 3Y:z in. diameter in not over 3/8 in. thick vessel wall; 23/ 8 in. diameter in over 3/8 in. vessel wall. Threaded, studded or expanded connections for which the hole cut is not greater than 23/ 8 in. diameter. (Code UG-36(c)(3)(a) The design procedure described on the following pages conforms to Code UG-36 through UG-43. For openings exceeding these limits supplemental rules of Code 1-7 shall be applied in addition to UG-36 through UG-43. For reinforcement of openings in flat heads see Code UG-39. A brief outline of reinforcement design for better understanding of the procedure is described in the following pages. The basic requirement is that around the opening the vessel must be reinforced with an equal amount of metal which has been cut out for the opening. The reinforcement may be an integral part of the vessel and nozzle, or may be an additional reinforcement pad. (Fig. A) This simple rule, however, needs further refinements as follows: 1. It is not necessary to replace the actually removed amount of metal, but only the amount which is required to resist the internal pressure (A). This required thickness of the vessel at the openings is usually less than at other points of the shell or head. 2. The plate actually used and nozzle neck usually are thicker than would be required according to calculation. The excess in the vessel wall (AJ) and nozzle wall (A.z) serve as reinforcements. Likewise the inside extension of the opening (A 3) and the area of the weld metal (A-/) can also be taken into consideration as reinforcement. 3. The reinforcement must be within a certain limit. 4. The area of reinforcement must be proportionally increased if its stress value is lower than that of the vessel wall. 5. The area required for reinforcement must be satisfied for all planes through the center of opening and normal to vessel surface. The required cross sectional area of the reinforcement shall then be: The required area for the shell or head to resist the internal pressure (A). From this area subtract the excess areas within the limit (AjA2A3A-/). If the sum of the areas available for reinforcement (Aj+A 2+A 3+A-/) is equal or greater than the area to be replaced (A), the opening is adequately reinforced. Otherwise the difference must be supplied by reinforcing pad (A5). Some manufacturers follow a simple practice using reinforcing pads with a crosssectional area which is equal to the metal area actually removed for the opening. This practice results in oversized reinforcement, but with the elimination of calculations they find it more economical.
130
REINFORCEMENT FOR OPENINGS DESIGN FOR INTERNAL PRESSURE (continued)
1.
B
c
D
o
E
For vessels under internal pressure the total cross-sectional area required for reinforcement of openings shall not be less than: A = d Xl" where d = the inside diameter of opening in its corroded condition, inches. t, = the required thickness of shell or head computed by the applicable formulas using E = 1.0 when the opening is in solid plate or in a category B joint. When opening passes through any other welded joint, E = the efficiency of that joint. When the opening is in a vessel which is radiographically not examined, E = 0.85 for type No.1 joint and E = 0.80 for type No.2 joint. When the opening and its reinforcement are entirely within the spherical portion of a flanged and dished head, t, is the thickness required by the applicable formulas using M= 1. When the opening is in a cone, t, is the thickness required for a seamless cone of diameter, D measured where the nozzle axis intersects with the wall of the cone. When the opening and its reinforcement are in a 2: I ellipsoidal head and are located entirely within a circle the center of which coincides with the center of the head and the diameter of which is equal to 0.8 times the head diameter, t, is the thickness required for seamless sphere of radius 0.9 times the diameter of the head. If the stress value of the opening's material is less than that of the vessel material, the required area A shall be increased. (See next page for examples.) 2.
F
h
AREA OF REINFORCEMENT
A VAILABLE AREAS OF REINFORCEMENT
AJ= Area of excess thickness in the vessel wall (t-t,) d or (t-t,) (t" + t)2 use the larger value, square inches. If the stress value of the opening's material is less than that of the vessel material, area Al shall be decreased. (See next page for examples.) A 2= Area of excess thickness in the nozzle wall (t,,- trn) 5t or (t,,-t,,) 5t" use - the smaller value, square inches. A3= Area ofinside extension ofnozzle square inches (t,,-c)2h. A4= Area of welds, square inches. If the sum of A, A2 A3 andA-I is less than the area for reinforcement required, A the difference must be supplied by reinforcing pad.
131 REINFORCEMENT FOR OPENINGS DESIGN FOR INTERNAL PRESSURE (continued) G
3.
LIMITS OF REINFORCEMENT
The metal used as reinforcement must be located within the limits. The limit measured parallel to the vessel wall X = d or Rn + tn + t, use larger value. The limit measured parallel to the nozzle wall Y = 2.5 tor2.5t/1' use smaller value. When additional reinforcing pad is used, the limit, Y to be measured from the outside surface of the reinforcing pad.
- - - - - - - - - - 1 Rn= inside radius of nozzle in corroded condition, inches.
NOTATION: For other notations, see the preceding page. r = thickness of the vessel wall less cor- 4. STRENGTH OF REINFORCEMENT rosion allowance, I-------------------------l If the strength of materials in AI A2 A3 A./ and A5 or the inches. material of the reinforcing pad are lower than that of the Ir = see preceeding page vessel material, their area considered as reinforcement shall In= nominal thickness be proportionately decreased and the required area, A in of nozzle wall irrespective of product inverse proportion increased. The strength ofthe deposited form. less corrosion weld metal shall be considered as equivalent to the weaker material of the joint. allowance. inches. Irn=required thickness of seamless nozzle wall. inches. h = distance nozzle projects beyond the inner surface of the vessel wall less corrosion allowance. inches. c = corrosion allowance, inches. d = see preceding page.
It is advisable to use for reinforcing pad material identical with the vessel material.
No credit shall be takenJor additional strength of reinforcement having higher stress value than that of the vessel wall. EXAMPLES:
1.
a. The stress value of nozzle material: 17,100 psi. The stress value of shell material: 20,000 psi. Ratio 17,100/20,000=0.855 To the required area, A shall be added: +2t/1 tr(1-0.855) b. From the area AI shall be subtracted: -2t/1X (t-t r) (1-0.855)
2.
Using identical material for the vessel and reinforcing pad, the required area for reinforcement is 12 square inches. If the stress value of vessel material = 20,000 psi., the stress value of the nozzle material = 17,100 psi., ratio 20,000117, 100 = 1.17 In this proportion shall be increased the area ofreinforcing pad: 12 X 1.17 = 14.04 square inches.
132 REINFORCEMENT FOR OPENINGS DESIGN FOR INTERNAL PRESSURE ( continued) 100
5. REINFORCEMENT IN DIFFERENT PLANES FOR INTERNAL PRESSURE \
0.95
0.90
1
Since the circumferential stress in cylindrical shells and cones is two times greater than the longitudinal stress, at the opening the plane containing the axis of the shell is the plane of the greatest unit loading due to pressure. On the plane perpendicular to the vessel axis the unit loading is one half of this.
\
0.85
0.80 ~
...0
Chart shows the variation of the stresses on different planes. (Factor F)
0.75 ~
...
;:J
~
When the long dimension of an elliptical or obround opening exceeds twice the short dimensions, the reinforcement across the short dimensions shall be increased as necessary to provide against excessive distortion due to twisting moment. Code UG-36(a)(l).
0.70
0.65
0.60
0.551-+-+-++-+-~-+-++-+-+-I~~-+-~
1"'-.
Factor F shall not be less than 1.0, except for integrally reinforced openings in cylindrical shells and cones it may be less.
O. 50 L...L---L.....L......L.....I...-.L......I---L......J.......L...J..-..r........J'--I.--l.......L.....L--'= 0" 10" 20" 30" 40" 50" 60° 70° 80° 90'
Angle
e
of Plane with Longitudinal Axis Factor F - Fig. UG-37
4T ? PI..,45} -(f *-* PI,.,
F= 1.00" Longitudinal axis of shell
The total cross-sectional area of reinforcement in any planes shall be: A = dx trx F
F= 0.5
F= 0.75
Longitudinal axis of shell
(Notations on preceeding pages.)
DESIGN FOR EXTERNAL PRESSURE The reinforcement required for openings in a single-walled vessel subject to external pressure need be only 50 percent of that required for internal pressure where tr is the wall thickness required by the rules for vessels under external pressure. Code UG37(d)(l). A = dx trx F 2 (See Notations on preceeding pages.)
133
REINFORCEMENT OF OPENINGS EXAMPLES EXAMPLE 1. tn tm
Rn
I
~ ~ f-'"'-r--
I
tr
h
-,.
I I
I
t
I,"
~
3*
DESIGN DATA: Inside diameter of shell: 48 in. Design pressure: 250 psi at 200 0 F Shell material: SA-285-C S=15,700 psi t = 0.625 in. The vessel is spot radiographed. No allowance for corrosion. Nozzzle material: SA-53-B S = 17,100 psi, tn = 0.432 in. Nozzle nom. size: 6 in. Extension of nozzle inside the vessel: 1.5 in. h=2.5.tn=2.5 x 0.432=1.08 in. The nozzle does not pass through seams. Fillet weld size: 0.375 in.
Wall thickness required:
PR 250x24 for shell: tr = - - - - = - - - - - - - - = 0 . 3 8 6 i n . 8E-0.6 15,700x1.0-0.6x250 for nozzle: t
= m
PRn
8E-0.6P
250x2.88 --------=0.043in. 17,100x 1.0- 0.6x 250
AREA OF REINFORCEMENT REQUIRED A = dtr = 5.761 x 0.386 = AREA OF REINFORCEMENT AVAILABLE Al = (Excess in shell.) Larger of the following: (t-tr ) d = (0.625-0.386) x 5.761 = 1.377 sq. in. or (t-t r) (tn + t) 2 = (0.625 - 0.386) x (0.432 + 0.625) x 2 = 0.505 sq. in. A2 = (Excess in nozzle neck.) Smaller of the followmg: (tn-tm ) 5t = (0.432-0.043) x 5 x 0.625 = 1.216 sq. in. (tn-tm ) 51n = (0.432-0.043) x 5 x 0.432 = (No credit for additional strength of nozzle material having higher stress value that of the vessel wall.)
2.224 in.
1.377 sq. in.
0.843 sq. in.
A3 = (Inside projection.) tn x 2h = 0.432 x 2 x 1.08 =
0.933 sq. in.
A4 = (Area of fillet weld) 0.375 2 As = (Area of fillet weld inside) 0.375 2
0.140 sq. in. 0.140 sq. in.
TOTAL AREA AVAILABLE Since this area is greater than the area required for reinforcement, additional reinforcement is not needed.
3.433 sq. in.
134
REINFORCEMENT OF OPENINGS EXAMPLES
EXAMPLE 2.
In (I - Ir)
d
h
DESIGN DATA: Inside radius of shell: R = 24 in. Design pressure: P = 300 psi at 200 0 F. Shell material: t = 0.500 in. SA-516-70 plate, S = 20,000 psi The vessel is spot examined There is no allowance for corrosion Nozzle nominal size: 6 in. Nozzle material: SA-53 B S=17,100psi. t n =0.432 in. Extension of nozzle inside the vessel: 1.5 in. Fillet weld size inside: 0.500 in.; Fillet weld size outside: 0.625 in. Ratio of stress values: 17,100/20,000 = 0.855
Wall thickness required:
PR Shell, tr = -S-E---0-.6-P-
PR SE -0.6P
Nozzle, tm = - - - "n- -
300x24 20,000xl-0.6x300
0.364in.
300x2.88 17.1 00 x 1.0 - 0.6 x 300
0.05Iin.
Since the strength of the nozzle material is lower than that of the vessel material, the required area for reinforcement shall be proportionally increased and the areas available for reinforcement proportionally reduced. AREA OF REINFORCEMENT REQUIRED A = dtr 5.761 x 0.364 = 2.097 sq. in. Area increased: + 2tn x tr (1-17,100/20,000) = 2·x 0.432 x 0.364 x (1-0.855) = 0.046 sq. in. 2.143 sq. in. AREA OF REINFORCEMENT AVAILABLE AI = (Excess in shell.) Larger of the following: (t - t r ) d = (0.500 - 0.364) x 5.761 = 0.784 sq. in. or (t - tr) (tn + t) 2 = (0.500 - 0.364) x (0.432 + 0.500) x 2 = 0.254 sq. in. Area reduced: -2 x tn (t -tr ) (1 -- 0.855) = -2 x 0.432 x (0.500 - 0.364) (l - 0.855) = -0.017 sq. in. 0.767 sq. in. A2 = (Excess in nozzle neck.) Smaller of following: (tn - t rn ) 5t = (0.432 - 0.051) 5 x 0.500 = 0.953 (tn - trn) 5tn = (0.432 - 0.051) 5 x 0.432 = 0.823 Area reduced: 0.855 x 0.823 = 0.704 sq. in. Since the strength of the nozzle is lower than that of the shell, a decreased area shall be taken into consideration. 17,100/20,000 = 0.855, 0.855 x 0.823 = 0.704 sq. in. A3 = (Inside projection.) tn x 2h = 0.432 x 2 x 1.08 = 0.933 Area decreased 0.933 x 0.855 = 0.797 sq. in. A4 = (Area of fillet weld) 2 x 0.5 x 0.625 2 x 0.855 = 0.334 sq. in. As = (Area of fillet weld inside) 2 x 0.5 x 5002 x 0.855 = 0.214 sq. in. TOTAL AREA AVAILABLE 2.816 sq. in. Additional reinforcement not required.
135
REINFORCEMENT OF OPENINGS EXAMPLES
EXAMPLE 3. DESIGN DATA: Inside diameter of shell: 48 in. Design pressure: 300 psi at 200 F. Shell material: 0.500 in. SA-516-60 plate, The vessel fully radiographed, E = I There is no allowance for corrosion Nozzle nominal size: 8 in. Nozzle material: SA-53 B, 0.500 in. wall Extension of nozzle inside the vessel: 0.5 in. The nozzle does not pass through the main seams. Size of fillet welds 0.375 in. (Reinforcement pad to nozzle neck.)
::,1
I,
0
~I I -f--4F"1r-- I
~
Wall thickness required: Shell
tr =
Nozzle
PR
SE-0.6P
t ,
rn
=
300x24 17,100x1-0.6x300
PR n
SE-0.6P
=
0.426 in.
300x3.8125 17,100xl-0.6x300
AREA OF REINFORCEMENT REQUIRED A = d x tr = 7.625 x 0.426 =
0.068 in.
3.249 sq. in.
AREA OF REINFORCEMENT AVAILABLE Al = (Excess in shell.) Larger of the following: (t - tr) d = (0.500 - 0.426) 7.625 = 0.564 0.564 sq. in. or (t - tr ) (tn + t) 2 = (0.500 - 0.426) ( 0.500 + 0.500) 2 = 0.148 sq. in. A2 = (Excess in nozzle neck.) Smaller of following: (tn - trn) 5t = (0.500 - 0.068) 5 x 0.5 = 1.08 or 1.08 sq. in. (t n - trn) 5tn = (0.500 - 0.068)5 x 0.5 = 1.08 0.500 sq. in. A3 = (Inside projection.) tn x 2h = 0.500 x 2 x 0.5 = 2 0.141 sq. in. A4 = (Area of fillet weld) 0.375 . (The area of pad to shell weld disregarded) 2.285 sq. in. TOTAL AREA AVAILABLE This area is less than the required area, therefore the difference shall be provided by reinforcing element. It may be heavier nozzle neck, larger extension of the nozzle inside of the vessel or reinforcing pad. Using reinforcing pad, the required area of pad: 3.249 - 2.285 = 0.964 sq. in. Using 0.375 in. SA-516-60 plate for reinforcing pad the width of the pad 0.964/0.375 = 2.571 The outside diameter of reinforcing pad: Outside diameter of pipe: 8.625 width of reinforcing pad: 2.571 11.196 in.
136
STRENGTH OF ATTACHMENTS JOINING OPENINGS TO VESSEL A
At the attachments, joining openings to the vessel, failure may occur through the welds or nozzle neck in the combinations shown in figures A and B. The strength of the welds and the nozzle neck in those combinations shall be at least equal to the smaller of: I. The stength in tension of the cross-sectional area of the element of reinforcement being considered, or
Possible paths of failure: 1. Through
2. The strength in tension of area a (A = d x tr ) less the strength in tension of the excess in the vessel wall (A I).
B The allowable stress value of the welds is the stress value of the weaker material connected by the welds multiplied by the following factors: Groove-weld tension Groove-weld shear Fillet-weld shear
3 2 Possible paths of failure: 1. Through
0.74 0.60 0.49
The allowable stress value of nozzle neck in shear is 0.70 times the allowable stress value of nozzle material.
EXAMPLE 4. A = 2.397 sq. in. Al = 0.484 sq. in.
do = 6.625 in., outside diameter of nozzle dm = 6.193 in., mean diameter of nozzle S = 20,000 psi allowable stress value of vessel material Sn = 17, 100 psi allowable stress value of nozzle material tn = 0.432 in. wall thickness of nozzle. t = 0.500 in. wall thickness of vessel' 0.375 in. fillet weld leg. Check the strength of attachment of nozzle load to be carried by welds. Load to be carried by welds (A - A I) S = (2.397 - 0.484) x 20,000 = 38,260 lb. STRESS VALUE OF WELDS: Fillet-weld shear 0.49 x 20,000 = 9,800 psi. Groove-weld tension 0.74 x 20,00 = 14.800 psi. Stess value of nozzle wall shear 0.70 x 17,100 =11,970 psi. STRENGTH OF WELDS AND NOZZLE NECK: a. Fillet-weld shear ~L x weld leg x 9,800 = 10.4065 x 0.375 x 9,800 = 38.243 lb. 2 b. Nozzle-wall shear 1Cd., x tn x 11,970 = 9.72 x 0.432 x 11,970 = 50,262 lb. 2
c. Groove-weld tension 1Cdo x t x 14,800 = 10.4065 x 0.500 x 14,800 = 77 ,008 lb. 2 POSSIBLE PATH OF FAILURES: 1. Through a. and b. 38,243 + 50,262 = 88,505 lb. 2. Throgh a. and c. 38,243 + 77,008 = 115,251 lb. Both paths are stronger than the required strength 38,260 lb.
137
STRENGTH OF ATTACHMENTS JOINING OPENINGS TO VESSEL EXAMPLE 5. DESIGN DATA A = 3.172 sq. in., Al = 0.641 sq. in., A2 = 0.907 sq. in. dp = 12.845 in. outside diameter of reinforcing pad. do = 8.625 in. outside diameter of nozzle. dm = 8.125 in. mean diameter of nozzle. S = 20,000 psi allowable stress value of vessel material Sn = 17,100 psi allowable stress value of nozzle material t = 0.5000 in. thickness of vessel wall. 0.375 in. leg of fillet - eeld a 0.250 in. leg of fillet - weld d te = 0.250 in. thickness of reinforcing pad. Check the strength of attachment of nozzle. LOAD TO BE CARRRIED BY WELDS: (A - A I)S = (3.172 - 0.641) x 20,000 = 50,620 lb. LOAD TO BE CARRIED BY WLDS a, c, e: (A2 + 2 tnt)S = (0.907 + 2 x 0.500 x 0.500) x 17,100 lb. = 24,059 STRESS VALUE OF WELDS: Fillet - weld shear 0.49 x 20,000 = 9,800 psi Groove - weld tension 0.74 x 20,000 = 14,800 psi STRESS VALUE OF NOZZLE WALL SHEAR: 0.70 x 17,100 = 11,970 psi STRENGTH OF WELDS AND NOZZLE NECK:. a. Fillet weld shear
redo
x weld leg x 9,800
2
red
b. Nozzle wall shear ----I!!.x tn x 11,970 2
= 13.55
= 12.76 x
x 0.375 x 9,800
0.500 x 11,970
= 49,796 lb.
= 76,368
c. Groove weld tension ;rdo x weld leg x 14,800 = 13.55 x 0.500 x 14.800 2
lb.
= 100,270 lb.
;rd d. Filet weld shear _P_x weld leg x 9,800 = 20.18 x 0.25 x 9.800 = 49,433 lb.
2 e. Groove weld tension
redo weld leg x 14,800 = 13.55 x 0.25 x 14,800 = 50,128 lb. 2
POSSIBLE PATH OF FAILURE: 1. Through band d 76,368 + 49,433 = 125,801 lb. 2. Through C and d 100,270 + 49,433 = 149,703 lb. 3. Through a,c and e 49,796 + 100,270 + 50,128 = 200,194 lb. Paths 1. and 2. are stronger than the total strength of 50,620 lb. Path 3. is stronger than the strength of 24,059 lb. The outer fillet weld d strength 49,433 lb. is greater than the reinforcing pad strength of (dp - dcJt e x S = (12,845 - 8,625) x 0.25 x 20,000 = 21,100 lb.
138
LENGTH OF COUPLINGS AND PIPE FOR OPENINGS NOZZLE IN SPHERE OR CYLINDER C
=
R,-vR/ r2
EXAMPLE: Given: Ri = 15 in., r = 8 in. u
Find: C = 15--J15 2-8 2 =
15-"'225 - 4 = 15-12.6886
=
2.3114 in.
NOZZLE IN SPHERE OR CYLINDER X= G-Y Y= -JR/-(F + rj2 ~
EXAMPLE: Given: Ri = 15 in., G = 24 in., F = 6 in. r = 4.3125 in. Find: X Y = ...;rI5'-2--{-6-+-4-.3-12-5-Y = -J225-1 06 = W9 Y= 10.9 X= 24-10.9 = 13.1 in.
COUPLING IN SPHERE OR CYLINDER X= V-Y EXAMPLE: Given: Ri = 15 in., Ro = 16 in., F = 6 in., r = 1.25 in. V = "'16 2-{6-1.25)2 = -J256-22.56 = 15.30 in. Y= -J15 2-{6 + 1.25)2 = "'225-52.56 = 13.12 in. X = 15.30-13.12 = 2.18 in.
COUPLING IN SPHERE OR CYLINDER X= V-Y, Sin/3=AIRo , r=a+/3 F =Sin xRo
r
EXAMPLE: Given: Ro = 12 in., a= 15°, A = 6 in. Find: F Sin /3= 6/12 = 0.500 = 30° r= 30°+15° = 45° F= Sin 45° x 6 = 0.7071 x 6 = 4.243 in. When F is known, Find X as in Example C above.
NOZZLE IN 2: 1 ELLIPSOIDAL HEAD X=G-Y-SF Y= VR/-(F+r)2
2
~I
I
EXAMPLE: Given: Ri = 24 in., F= 12 in., r= 8 in., SF= 2 in. G=20 in. Find: X Y = Y~24-:2-=-(--:-:-12-:-+---:8-'-)2' = -J576-400 = 6.3 in.
2 X
=
20---6.63-2
2 =
11.37 in.
139 LENGTH OF COUPLING AND PIPE FOR OPENINGS
~
COUPLING IN 2: 1 ELLIPSOIDAL HEAD
I-f+~
L~~~+-.j~ SEAN
i
R;
~
-V
>C
:>
>-
~
R.
NOZZLE IN FLANGED & DISHED HEAD
Flrl T
V
I
I I.I~ !:!
l(
-"'"
.,r ~
~
10
b..
~ll~
tIN~/N:E!.h
.
~
~
-=--
+ r)2 X = V-V, V =VR;- (F_r)2, Y =V R?-(F I EXAMPLE Ri = 24 in., Ro = 25 in., F = 8 in., r = 1 in. Given: Find: X V =,.,/25 2- (8 _1)2 =V625 ·49 = 24 in.
~~
r;~
~~. ~-2 t~ ~:-
~~
SEAN'
~
V-
6
.J
X
,
J
I
'~-=:A, ~~
I
VESSEL
R{
Y =-V242- (8 + 1)2 ='V576-81 = 22.25 in. X=
y
f
:>
>.
~~
I
X=G-Y-SF, Y = ID-C, C = R i · Ri2 - (F + r) 2 EXAMPLE Given: Inside depth of dish, ID = 8 in. Ri = 48 in., Ro = 49 in., F = 24 in., r = 2 in., G = 18 in., SF = 2 in. Find: X C = 48-""; 48 2 - (24 + 2)2 = 7.70 in. X= 18-7.70-2 = 8.30 in.
COUPLING IN FLANGED & DISHED HEAD
,rr
L.IN
,j
R? _ (F + r) 2 R i-(F-r)2, = v- Y, v Y 2 2 EXAMPLE Given: Ri = 29 in .• Ro = 30 in., F = 18 in., r = 1 in. Find: X 2 -V30 -(18-1)2 =-'/900-289 = 12.36 in. V 2 2 -V29 2 - (18 + 1)2 ";841-361 = 10.95 in. Y 2 2 X= 12.36-10.95 = 1.41 in.
x
24-22.25 = 1.75 in.
NOZZLE IN CONE When ex is less than 45 0 X=G-Y, Y=Ri-[tanex x(F+r)] EXAMPLE Ri = 24 in., G = 30 in .• F = 12 in., r = 2 in., Given: 0: = 30 0 Find: X Y = 24- [tan 30 0 (12 + 2)] = 24-8.08 = 15.92 in. X = 30· 15.92 = 14.08 in.
I
d ~x
'~1hA
I
l
~~J).
[\
COUPLING IN CONE X=V+2Y, V=
: I ... ~ I ... ~~
Jy.~ V Y I
• ...i cos ex
Y = tan ex x r
EXAMPLE tc = 2 in., r = 1 in., a = 30 0 Given: Find: X 2 V = - - = 2.31 Y = 0.5774 x 1 = 0.5774 0.866 X = 2.31 + 2 x 0.5774 = 3.46 in.
140
NOZZLE NECK THICKNESS CodeUG-45 1.
for Access Openings, Openings for Inspection only the minimum wall thickness of necks shall not be less than the thickness computed from the applicable loadings in UG-22 such as internal or external pressure, stattic, cyclic, dynamic, seismic, impact reactions, etc.
2.
for Nozzles and other openings (except access and inspection openings) the minimum wall thickness of necks shall be the larger of he chickness computed from the applicable loadings in UG-22 or the smaller of wall thickness determined in 3, 4, 5, 6 below.
3.
In vessels under internal pressure thicknes of the shell or head required for internal pressure only, assuming £ = 1.0.
4.
In vessels under external pressure thickness of the shell or head for internal pressure using it as an equivalent value for external pressure, assuming £=1.0.
5.
In vessels under internal or external pressure the greater of the thickness determined in 3 and 4.
6.
The minimum wall thickness of standard wall pipe.
7.
The wall thickness of necks in no case shall be less than the minimum thickness specified in UG-16(b) for: Shells and heads: 0.0625 in. Unfired steam boilers: 0.2500 in. In compressed air service: 0.0918 in.
8.
Allowance for corrosion and threading - when required - shall be added to the thicknesses determined in 1. through 7. above. Using pipe listed in Table of Std. ANSI 836.10, the minimum wall thickness equals 0.875 times the nominal wall thickness. See Code UG-45 footnote No. 27 using pipe sizes 22, 26 and 30 inches. For selection of required pipe under internal pressure, see table "Maximum Allowable Internal Working Pressure for Pipes" on the following pages. EXAMPLES for using the table: Internal Design Pressure: Corrosion Allowance The Required Pipe for Manway: The Required Pipe for Nozzle:
18" 800 psig 0.125" Sch.60 Sch.60
0.750" Wall 0.750" Wall
2. Opening Diameter: Internal Design Pressure: Corrosion Allowance The Vessel Wall Thickness The Required Pipe for Manway: The Required Pipe for Nozzle:
18" 150 psig 0.125" 0.3125" Sch.l0 Std. Wt
0.250" Wall 0.375" Wall
1. Opening Diameter:
141
NOZZLE NECK THICKNESS CodeUG-45 (Continued)
3. Opening Diameter: 18" Internal Design Pressure: 140 psig Corrosion Allowance 0.125" The Vessel Wall Thickness 0.750" The Required Pipe for Manway: Sch. 10 The Required Pipe for Nozzle: Sch.40 Std. Wt. 0.328" + 0.125" Corr. Allow. 4. External Design Pressure: Material SA 516-60; Outside diameter of cylindrical shell: Shell thickness: The required thickness for 14 in. 0.0.,
0.250" Wall 0.453" Wall (min.)
P = 35 psi S= 17,100 D{) = 96 in. t = 1 in. 12 in. long nozzle neck:
1. To withstand 35 psi external pressure approximately 0.05 in. wall re-
quired, but the thickness shall not be less than the smaller of: 2. The thickness required for the shell under 35 psi internal pressure (as equivalent external pressure) PR 35 X 47 . t SE _ 0.6P 17,100 _ 32 = 0.097 In. 3. The minimum thickness of standard wall pipe: 0.328 in. (0.375 in. nom.) The smaller of2. and 3. 0.097 for wall thickness of nozzle neck is satisfactory. 5. External Design Pressure: P = 15 psi Material SA 516-60; S= 17,100 Outside diameter of cylindrical shell: D{) = 36 in. t=0.3125 in. Shell thickness: The required thickness for 14 in. 0.0.,-12 in. long nozzle neck: 1.
To withstand 15 psi external pressure approximately 0.02 in. wall required, but the thickness shall not be less than the smaller of the following:
2.
The th ickness required for the shell under 15 psi internal pressure t
3.
PR 15X17.6875 SE-0.6P 17,100-9
0016· . In.
The minimum thickness of standard wall pipe: 0.328 in. (0.375 in. nom.) The smaller of2. and 3. is 0.016 in., butthe thickness of the nozzle neck shall be in no case less than 0.0625 in. UG-45(a)(2).
142
MAXIMUM ALLOWABLE INTERNAL WORKING PRESSURE FOR PIPES The Calculations Based on the Formula:
p=
2 SEt
D+ 1.2t'
where
P = The max. allowable working pressure, psig. S = 17,100 psig. the stress value of the most commonly used materials for pipe (A53B, AI06B) at temperature - 20 to 650 OF. For higher temperature see notes at the end of the tables. E = 1.0 joint efficiency of seamless pipe D = Inside diameter of pipe, in. t = Minimum pipe wall thickness, in. (.875 times the nominal thickness). Nom. pIpe SIze
112
3/4
1
1-114
1-112
2
Designation STD. X-STG. SCH.160 XX-STG. STD. X-STG. SCH.160 XX-STG. STD. X-STG. SCH.160 XX-STG. STD. X-STG. SCH.160 XX-STG. STD. X-STG. SCH.160 XX-STG. STD. X-STG. SCH.160 XX-STG.
Pipe wall thickness .Min. Nom. 0.109 0.095 0.147 0.129 0.164 0.187 0.294 0.257 0.099 0.113 0.154 0.135 0.218 0.191 0.308 0.270 0.133 0.116 0.154 0.179 0.219 0.250 0.313 0.358 0.140 0.123 0.191 0.167 0.250 0.219 0.334 0.382 0.145 0.127 0.200 0.175 0.281 0.246 0.400 0.350 0.154 0.135 0.191 0.218 0.343 0.300 0.382 0.436
Corrosion allowance in. 0 1116 118 3/16 Max. Allow. Pressure psig. 4,252 1,365 5,987 2,888 163 7,912 4,575 1,649 13,854 9,719 6,146 3,030 3,487 1,222 4,900 2,498 328 7,280 4,638 2,263 114 11,071 8,026 5,308 2,867 3,245 1,437 4,513 2,607 848 6,570 4,498 2,592 834 10,054 8,462 5,519 3,532 2,692 1,283 3,741 2,266 882 5,043 3,487 2,028 658 8,201 6,435 4,788 3,246 2,414 1,192 35 3,399 2,124 918 4,939 3,578 2,294 1,079 7,388 5,886 4,473 3,139 2,036 1,069 143 2,938 1,933 971 50 4,805 3,716 2,676 1,683 6,312 5,155 4,050 2,997
114
287
661
1,703
1,803
1,878
731 1,988
143
MAXIMUM ALLOWABLE WORKING PRESSURE (cont) I
Nom. pIpe SIze 2~
3
31;2
4
5
6
8
Designation STD. X-STG. SCH-160 XX-STG. STD. X-STG. SCH.160 XX-STG. STD. X-STG. XX-STG. STD. X-STG. SCH.120 SCH.160 XX-STG. STD. X-STG. SCH.120 SCH.160 XX-STG. STD. X-STG. SCH.120 SCH.160 XX-STG. SCH.20 SCH.30 STD. SCH.60 X-STG. SCH.I00 SCH.120
Pipe wall thickness Nom. Min. 0.203 0.178 0.276 0.242 0.375 0.328 0.552 0.483 0.216 0.186 0.300 0.263 0.438 0.383 0.600 0.525 0.226 0.198 0.318 0.278 0.636 0.557 0.237 0.208 0.337 0.295 0.438 0.383 0.531 0.465 0.674 0.590 0.258 0.226 0.375 0.328 0.500 0.438 0.625 0.547 0.750 0.656 0.280 0.245 0.432 0.378 0.562 0.492 0.718 0.628 0.864 0.756 0.250 0.219 0277 0.242 0.322 0.282 0.406 0.355 0.500 0.438 0.593 0.519 0.718 0.628
Corrosion allowance in. 1/4 1/16 1/8 3/16 Max. Allow. Pressure Psig. 639 2,227 1,419 657 3,085 2,246 1,437 947 4,293 3,409 2,559 1,738 6,637 5,664 4,728 3,829 2,962 13 633 1,930 1,272 126 750 2,793 2,053 1,391 4,100 3,378 2,679 1,999 1,339 5,874 5,052 4,301 3,572 2,867 88 632 1,762 1,190 240 787 2,515 1,925 1,348 5,359 4,691 4,042 3,410 2,208 156 639 1,640 1,134 319 832 2,365 1,842 1,331 3,122 2,582 2,054 1,539 1,035 3,852 3,294 2,749 2,218 1,698 5,009 4,423 3,852 3,294 2,749 237 629 1,435 1,028 484 2,115- 1,696 1,284 881 2,872 2,439 2,014 1,597 1,187 3,649 3,201 2,761 2,330 1,907 4,452 3,988 3,534 3,088 2,650 628 298 963 1,303 670 2,044 1,692 1,346 1,005 2,699 2,338 1,981 1,631 1,285 3,507 3,132 2,764 2,400 2,044 4,294 3,906 3,526 3,150 2,781 128 375 629 885 468 216 722 981 126 631 377 888 1,147 419 931 673 1,454 1,191 758 1,809 1,542 1,277 1,016 2,161 1,890 1,621 1,355 1,093 2,643 2,365 2,091 1,820 1,552 0
144
MAXIMUM ALLOWABLE WORKING PRESSURE (cont) Nom. pIpe SIze 8
10
12
14
Designation SCH.140 SCH.160 XX-STG. SCH.20 SCH.30 STD. X-STG. SCH.80 SCH.I00 SCH.120 SCH.140 SCH.160 SCH.20 SCH.30 STD. SCHAO X-STG. SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH.160 SCH.I0 SCH.20 STD. SCHAO X-STG. SCH.60 SCH.80 SCH.I00 SCH.120 SCH.140
Pipe wall thickness Nom. Min. 0.812 0.711 0.906 0.793 0.875 0.766 0.250 0.219 0.307 0.269 0.365 0.319 0.500 OA38 0.593 0.519 0.718 0.628 0.843 0.738 1.000 0.875 1.125 0.984 0.250 0.219 0.330 0.289 0.375 0.328 OA06 0.355 0.500 OA38 0.562 OA92 0.687 0.601 0.843 0.738 1.000 0.875 1.125 0.984 1.312 1.148 0.250 0.219 0.312 0.273 0.375 0.328 OA38 0.383 0.500 OA38 0.593 0.519 0.750 0.656 0.937 0.820 1.093 0.956 1.250 1.094
0 3,017 3,393 3,269 707 873 1,038 1,439 1,716 2,095 2,484 2,976 3,377 595 788 897 973 1,207 1,361 1,674 2,074 2,482 2,812 3,317 541 677 816 956 1,096 1,306 1,664 2,101 2,469 2,850
Corrosion allowance in. 114 1/16 118 3/16 Max. Allow Pressure Psig. 2,736 2,456 2,180 1,909 3,106 2,822 2,543 2,266 2,983 2,701 2,423 2,148 102 300 502 462 259 57 666 220 421 831 625 606 1,228 1,019 811 873 1,502 1,290 1,080 1,877 1,662 1,447 1,236 2,261 2,248 1,825 1,610 2,750 2,526 2,264 2,085 3,146 2,918 2,692 2,469 86 253 422 103 273 615 443 209 379 550 723 282 453 625 799 681 554 856 1,030 658 832 1,183 1,006 962 1,494 1,315 1,137 1,891 1,710 1,528 1,349 2,295 2,110 1,926 1,744 2,623 2,435 2,248 2,063 3,123 2,932 2,740 2,552 78 385 230 209 55 363 519 190 345 657 501 482 327 639 796 463 620 774 937 825 666 1,144 983 1,500 1,337 1,175 1,014 1,933 1,767 1,602 1,438 2,299 2,130 1,963 1,796 2,676 2,505 2,334 2,166
I
145
MAXIMUM ALLOWABLE WORKING PRESSURE (cont) Nom. DesigpIpe nation SIze 14 SCH.160 SCH.10 SCH.20 SCH.30.STD. SCHAOX-STG. 16 SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH.160 SCH.lO SCH.20 STD. SCH.30 X-STG. 18 SCHAO SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH.160 SCH.10 SCH.20 STD. SCH.30 X-STG. SCHAO 20 SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH.160
Pipe wall thickness Nom. Min. 10406 1.230 0.250 0.219 0.312 0.273 0.375 0.328 0.500 00438 0.656 0.574 0.843 0.738 1.031 0.902 1.218 1.066 10438 1.258 1.593 1.394 0.250 0.219 0.312 0.273 0.375 0.328 00438 0.383 0.500 00438 0.562 00492 0.750 0.656 0.937 0.820 1.156 1.012 1.375 1.203 1.562 1.367 1.781 1.558 0.250 0.219 0.375 0.328 0.500 00438 0.593 0.519 0.812 0.711 1.031 0.902 1.281 1.121 1.500 1.313 1.750 1.531 1.968 1.722
Corrosion allowance in. 0 1116 1/8 3/16 114 Max. Allow Pressure Psig. 3,230 3,055 2,880 2,707 2,535 189 64 473 336 318 183 49 590 453 437 302 166 712 574 541 404 956 817 679 981 841 703 1,263 1,121 1,637 1,493 1,350 1,209 1,068 2,018 1,873 1,727 1,583 1,439 2,406 2,257 2,110 1,963 1,818 2,869 2,717 2,566 2,416 2,268 3,202 3,048 2,895 2,743 2,593 178 61 419 298 43 282 163 524 403 148 267 631 509 388 253 494 373 739 616 359 481 848 725 603 463 585 955 831 707 785 908 1,287 1,157 1,032 1,616 1,488 1,362 1,235 1,110 2,013 1,883 1,754 1,625 1,497 2,414 2,282 2,151 2,020 1,890 2,764 2,631 2,496 2,364 2,232 3,179 3,042 2,907 2,772 2,637 54 160 377 263 133 240 567 458 348 432 323 761 650 541 463 684 573 906 794 914 802 1,250 1,137 1,026 1,599 1,485 1,370 1,257 1,144 2,006 1,888 1,772 1,657 1,542 2,368 2,250 2,131 2,014 1,898 2,788 2,667 2,546 2,427 2,308 3,162 3,039 2,916 2,795 2,674
146
MAXIMUM ALLOWABLE WORKING PRESSURE (cont)
Nom. pIpe SIze
Designation
22
SCH.10 SCH.20 STD. X-STG. SCH.30 SCH.40 24 SCH.60 SCH.80 SCH.IOO SCH.120 SCH.140 SCH.160
26
30
Pipe wall thickness Nom. Min. 0.250 0.219 0.312 0.273 0.375 0.328 0.437 0.382 0.500 0.438 0.562 0.492 0.625 0.547 0.688 0.602 0.750 0.656 0.250 0.219 0.375 0.328 0.500 0.438 0.562 0.492 0.687 0.601 0.968 0.847 1.218 1.066 1.531 1.340 1.812 1.586 2.062 1.804 2.343 2.050 0.250 0.219 0.312 0.273 0.375 0.328 0.437 0.382 0.500 0.438 0.562 0.492 0.625 0.547 0.688 0.602 0.750 0.656 0.312 0.273 0.375 0.328 0.500 0.438
Corrosion allowance in. 1/4 0 1/16 3/16 1/8 Max. Allow. Pressure Psig. 50 343 243 145 132 35 230 428 329 218 120 316 515 416 155 402 304 601 501 294 491 392 690 591 477 378 677 577 776 565 466 665 867 766 554 753 653 956 855 639 739 1,044 942 841 45 133 313 223 200 290 110 471 380 269 359 632 541 450 346 437 528 712 620 505 597 688 873 780 861 959 1,241 1,146 1,053 1,574 1,478 1,383 1,289 1,194 1,998 1,900 1,803 1,707 1,610 2,386 2,286 2,187 2,089 1,991 2,734 2,634 2,534 2,433 2,334 3,135 3,032 2,930 2,829 2,728 42 123 289 206 29 111 194 361 278 102 184 267 435 351 173 256 339 508 424 248 331 414 583 499 320 403 487 656 572 393 477 562 730 646 467 551 636 805 721 624 540 794 709 880 26 96 168 313 240 88 160 232 376 304 214 287 359 505 432
147
NOTE: IF THE STRESS VALUE OF PIPE LESS THAN 17100 PSIG. DUE TO HIGHER TEMPERATURE, MULTIPLY THE MAX. ALLOWABLE PRESSURE GIVEN IN THE TABLES BY THE FACTORS IN THIS TABLE:
A53B AI06B
TEMPERATURE NOT EXCEEDING DEGREE OF 650 700 750 800 850 900 950 1 000 17,100 15,600 13,OOC 10,800 8,700 5,900 -
stress values pSlg 17,100 15,600 13,OOC 10,800 8,700 5,900 4,000 2,500
Factor
1.000
0.9123 0.7602 0.6316 0.4971 0.3450 0.2339 0.1462
Example: The Maximum Allowance Pressure for 6" x Stg. Pipe With a Corrosion Allowance of 118" From Table = 1,346 psi. - at Temperature 800 OF The Max. Allow. Press. 1,346 x 0.6316 = 850 psig. Example to find max. allow. pressure for any stress values: The Max. Allow. Press. 1,346 Psig. From Tables The Stress Value 13,000 psi. 13 000 For This Pipe The Max. Allow. Pressure ' x 1,346 = 1,023 psi. . 17,100
148
REQUIRED WALL THICKNESS FOR PIPES UNDER INTERNAL PRESSURE
The required wall thickness for pipes, tabulated on the following pages, has been computed with the following formula:
PR t= SE-O.6P
, where
t = the required minimum wall thickness of pipe, in. P = internal pressure, psig. S = 17,100 psig. the stress value of the most commonly used materials for pipe. A 53 B and A 106 B @ temp~rature -20 to 650°F. E = Joint efficiency of seamless pipe R = inside radius of the pipe, in. For the inside diameter of the pipe round figures are shown. With interpolation the required thickness can be determined with satisfactory accuracy. The thicknesses given in the tables do not include allowance for corrosion. For the determination of the required pipe wall thickness in piping systems the various piping codes shall be applied. Selecting pipe, the 12.5% tolerance in wall thickness shall be taken into consideration. The minimum thickness of the pipe wall equals the nominal thickness times .875.
149
REQUIRED PIPE WALL THICKNESS
FOR INTERNAL PRESSURE I.S. DIAM 1 2 3 4 5
50 0.002 0.003 0.005 0.006 0.008
100 0.003 0.006 0.009 0.012 0.015
150 0.005 0.009 0.014 0.018 0.022
PRESSURE PSIG. 250 300 200 350 0.009 0.006 0.008 0.011 0.012 0.015 0.018 0.021 0.018 0.022 0.027 0.031 0.024 0.030 0.036 0.042 0.030 0.037 0.045 0.052
6 7 8 9 10
0.009 0.011 0.012 0.013 0.015
0.018 0.021 0.024 0.027 0.030
0.027 0.031 0.036 0.040 0.044
0.036 0.042 0.047 0.053 0.059
0.045 0.052 0.059 0.065 0.074
0.054 0.062 0.071 0.080 0.089
11 12 13 14 15
0.016 0.018 0.019 0.021 0.022
0.033 0.036 0.038 0.041 0.044
0.049 0.053 0.058 0.062 0.066
0.065 0.071 0.077 0.083 0.089
0.081 0.089 0.096 0.104 0.111
16 17 18 19 20
0.024 0.025 0.027 0.028 0.030
0.047 0.050 0.053 0.056 0.059
0.071 0.075 0.080 0.084 0.089
0.095 0.100 0.106 0.112 0.118
21 22 23 24 25
0.031 0.033 0.034 0.035 0.037
0.062 0.065 0.068 0.071 0.074
0.093 0.097 0.102 0,106 0.111
26 27 28 29 30
0.038 0.040 0.041 0.043 0.044
0.077 0.080 0.083 0.085 0.088
0.115 0.119 0.124 0.128 0.133
400 0.012 0.024 0.037 0.048 0.060
450 0.014 0.027 0.040 0.054 0.067
500 0.015 0.030 0.045 0.060 0.075
0.063 0.073 0.083 0.094 0.104
0.072 0.083 0.095 0.107 0.112
0.081 0.094 0.107 0.121 0.134
0.090 0.105 0.119 0.134 0.149
0.098 0.107 0.116 0.124 0.133
0.114 0.125 0.135 0.145 0.156
0.131 0.143 0.155 0.166 0.178
0.147 0.161 0.174 0.188 0.201
0.164 0.179 0.194 0.209 0.224
0.118 0.126 0.133 0.140 0.148
0.142 0.151 0.160 0.169 0.178
0.166 0.176 0.187 0.197 0.208
0.190 0.202 0.214 0.226 0.238
0.214 0.228 0.241 0.254 0.268
0.238 0.253 0.268 0.283 0.298
0.124 0.130 0.136 0.142 0,148
0.155 0.163 0.170 0.177 0.185
0.187 0.195 0.204 0.213 0.222
0.218 0.228 0.239 0.249 0.259
0.249 0.261 0.273 0.285 0.297
0.281 0.294 0.308 0.321 0.335
0.313 0.328 0.343 0.357 0.372
0.153 0.159 0.165 0.171 0.177
0.192 0.199 0.207 0.214 0.222
0.231 0.240 0.249 0.257 0.266
0.270 0.280 0.290 0.301 0.311
0.309 0.321 0.332 0.344 0.356
0.348 0.361 0.375 0.388 0.401
0.387 0.402 0.417 0.432 0.447
150
REQUIRED PIPE WALL THICKNESS FOR INTERNAL PRESSURE (cont.) I.S. DIAM 1 2 3 4 5
550 0.017 0.033 0.050 0.066 0.082
600 0.018 0.036 0.054 0.072 0.090
650 0.020 0.039 0.059 0.078 0.098
PRESSURE PSIG. 700 800 750 850 0.021 0.023 0.024 0.026 0.042 0.045 0.048 0.052 0.063 0.068 0.073 0.077 0.084 0.090 0.097 0.103 0.105 0.113 0.121 0.128
900 0.028 0.055 0.082 0.109 0.136
950 0.029 0.058 0.087 0.115 0.144
1,000 0.031 0.061 0.091 0.122 0.152
6 7 8 9 10
0.099 0.115 0.132 0.148 0.164
0.108 0.126 0.144 0.162 0.180
0.117 0.136 0.156 0.175 0.195
0.126 0.147 0.168 0.189 0.210
0.135 0.158 0.181 0.203 0.226
0.l45 0.l69 0.193 0.217 0.241
0.154 0.180 0.205 0.231 0.257
0.l63 0.191 0.218 0.245 0.272
0.173 0.201 0.230 0.259 0.288
0.182 0.212 0.243 0.273 0.303
11
12 13 14 15
0.181 0.197 0.214 0.230 0.246
0.197 0.215 0.233 0.251 0.269
0.214 0.234 0.253 0.273 0.292
0.231 0.252 0.273 0.294 0.315
0.248 0.271 0.293 0.316 0.338
0.265 0.289 0.313 0.337 0.361
0.282 0.301 0.333 0.359 0.385
0.299 0.326 0.354 0.381 0.408
0.316 0.345 0.374 0.403 '0.431
0.334 0.364 0.394 0.425 0.455
16 17 18 19 20
0.263 0.279 0.296 0.312 0.328
0.287 0.305 0.323 0.341 0.359
0.312 0.331 0.350 0.370 0.389
0.336 0.357 0.378 0.399 0.420
0.361 0.383 0.406 0.428 0.451
0.385 0.409 0.434 0.458 0.482
0.401 0.436 0.461 0.487 0.513
0.435 0.462 0.489 0.517 0.544
0.460 0.489 0.518 0.546 0.575
0.485 0.516 0.546 0.576 0.606
21 22 23 24 25
0.345 0.361 0.378 0.394 0.410
0,377 0.395 0.413 0.430 0.448
0.409 0.428 0.448 0.467 0.487
0.441 0.462 0.483 0.504 0.525
0.473 0.496 0.518 0.541 0.564
0.506 0.530 0.554 0.578 0.602
0.538 0.564 0.590 0.615 0.641
0.571 0.598 0.625 0.653 0.680
0.604 0.633 0.661 0.690 0.719
0.637 0.667 0.697 0.728 0.758
26 27 28 29 30
0.427 0.443 0.460 0.476 0.492
0.460 0.484 0.502 0.520 0.538
0.506 0.525 0.545 0.564 0.584
0.546 0.567 0.588 0.609 0.630
0.586 0.608 0.631 0.654 0.676
0.626 0.650 0.674 0.698 0.722
0.666 0.692 0.718 0.743 0.769
0.707 0.734 0.761 0.788 0.816
0.747 0.776 0.805 0.834 0.862
0.788 0.819 0.849 0.879 0.909
151
REQUIRED PIPE WALL THICKNESS FOR INTERNAL PRESSURE (cont.) I.S. DIAM . 1 2 3 4 5
1,100 0.034 0.067 0.101 0.139 0.168
1,200 0.037 0.074 0.110 0.147 0.184
1,300 0.040 0.078 0.120 0.160 0.199
PRESSURE PSIG. 1,400 1,500 1,600 1,700 0.043 0.047 0.050 0.053 0.086 0.093 0.099 0.106 0.130 0.139 0.149 0.159 0.173 0.183 0.199 0.212 0.216 0.232 0.248 0.265
6 7 8 9 10
0.201 0.235 0.268 0.301 0.335
0.220 0.257 0.293 0.330 0.367
0.239 0.279 0.319 0.359 0.399
0.259 0.301 0.345 0.388 0.431
0.278 0.324 0.371 0.417 0.463
0.298 0.347 0.397 0.446 0.496
11 12 13 14 15
0.368 0.402 0.435 0.469 0.502
0.403 0.440 0.477 0.513 0.550
0.438 0.478 0.518 0.558 0.598
0.474 0.517 0.560 0.603 0.646
0.510 0.556 0.602 0.648 0.695
16 17 18 19 20
0.536 0.569 0.603 0.636 0.669
0.586 0.623 0.660 0.696 0.733
0.638 0.677 0.717 0.757 0.797
0.689 0.732 0.775 0.818 0.861
21 22 23 24 25
0.703 0.736 0.770 0.803 0.837
0.770 0.806 0.843 0.879 0.916
0.837 0.877 0.916 0.956 0.996
26 27 28 29 30
0.870 0.904 0.937 0.971 1.004
0.953 0.989 1.026 1.063 1.099
1.036 1.076 1.116 1.155 1.195
1,800 0.057 0.113 0.169 0.225 0.281
1,900 0.060 0.119 0.179 0.238 0.298
2,000 0.063 0.126 0.189 0.252 0.315
0.318 0.370 0.423 0.476 0.529
0.337 0.394 0.450 0.506 0.562
0.357 0.417 0.477 0.536 0.596
0.378 0.441 0.503 0.566 0.629
0.546 0.595 0.645 0.694 0.744
0.582 0.635 0.688 0.740 0.793
0.618 0.675 0.731 0.787 0.843
0.665 0.715 0.774 0.834 0.893
0.692 0.755 0.818 0.881 0.944
0.741 0.787 0.834 0.880 0.926
0.793 0.843 0.893 0.942 0.992
0.846 0.899 0.952 1.005 1.058
0.899 0.955 1.012 1.068 1.137
0.953 1.012 1.072 1.131 1.191
1.007 1.070 1.132 1.195 1.258
0.904 0.947 0.991 1.034 1.077
0.973 1.019 1.065 1.111 1.158
1.041 1.091 1.140 1.190 1.240
1.110 1.163 1.216 1.269 1.322
1.180 1.236 1.292 1.349 1.405
1.250 1.310 1.369 1.429 1.488
1.321 1.384 1.447 1.510 1.573
1.120 1.163 1.206 1.249 1.292
1.204 1.250 1.297 1.343 1.389
1.289 1.339 1.388 1.438 1.487
1.375 1.428 1.480 1.533 1.586
1.461 1.517 1.573 1.630 1.686
1.548 1.607 1.667 1.727 1.786
1.636 1.698 1.761 1.824 1.887
152
REQUIRED PIPE WALL THICKNESS FOR INTERNAL PRESSURE (cont.) LS.
PRESSURE PSIG.
DIAM 2,100 2,200 2,300 2,400 2,500 2,600 2,700 2,800 2,900 3,000 1 2 3 4 5
0.067 0.133 0.199 0.266 0.332
0.070 0.140 0.209 0.279 0.349
0.074 0.147 0.220 0.293 0.366
0.077 0.154 0.230 0.307 0.383
0.080 0.161 0.241 0.321 0.401
0.084 0.168 0.251 0.335 0.419
0.088 0.175 0.262 0.349 0.436
0.091 0.182 0.273 0.364 0.454
0.095 0.189 0.284 0.378 0.472
0.098 0.196 0.294 0.393 0.491
6 7 8 9 10
0.398 0.464 0.531 0.597 0.663
0.419 0.488 0.558 0.628 0.697
0.439 0.512 0.586 0.659 0.732
0.460 0.537 0.613 0.690 0.767
0.481 0.561 0.641 0.722 0.802
0.502 0.586 0.670 0.753 0.834
0.524 0.611 0.700 0.785 0.872
0.545 0.636 0.727 0.818 0.908
0.567 0.661 0.756 0.850 0.944
0.589 0.687 0.785 0.883 0.981
11 12 13 14 15
0.730 0.796 0.862 0.928 0.995
0.767 0.837 0.907 0.976 1.046
0.805 0.878 0.951 1.025 1.098
0.843 0.920 0.997 1.073 1.145
0.882 0.962 1.042 1.112 1.202
0.921 1.004 1.088 1.172 1.255
0.960 1.047 1.134 1.221 1.308
0.999 1.090 1.181 1.271 1.362
1.039 1.133 1.228 1.322 1.416
1.079 1.177 1.275 1.373 1.471
16 17 18 19 20
1.061 1.127 1.194 1.260 1.326
1.116 1.185 1.255 1.325 1.395
1.171 1.244 1.317 1.390 1.463
1.226 1.303 1.380 1.456 1.533
1.282 1.363 1.443 1.523 1.603
1.339 1.421 1.506 1.590 1.673
1.396 1.483 1.570 1.657 1.745
1.453 1.544 1.635 1.725 1.816
1.511 1.605 1.700 1.794 1.888
1.569 1.667 1.765 1.863 1.961
21 22 23 24 25
1.392 1.459 1.525 1.591 1.658
1.464 1.534 1.604 1.673 1.743
1.537 1.610 1.683 1.756 1.829
1.610 1.686 1.763 1.839 1.916
1.683 1.763 1.843 1.923 2.004
1.757 1.841 1.924 2.008 2.092
1.832 1.919 2.006 2.093 2.181
1.907 1.998 2.089 2.179 2.270
1.983 2.077 2.172 2.266 2.360
2.059 2.157 2.255 2.353 2.451
26 27 28 29 30
1.724 1.790 1.856 1.924 1.989
1.813 1.883 1.952 2.022 2.092
1.902 1.976 2.049 2.122 2.195
1.994 2.069 2.146 2.223 2.299
2.084 2.164 2.244 2.324 2.404
2.175 2.259 2.343 2.426 2.510
2.268 2.355 2.442 2.529 2.617
2.361 2.452 2.543 2.633 2.724
2.455 2.549 2.644 2.738 2.832
2.549 2.647 2.745 2.843 2.942
153
NOZZLE EXTERNAL FORCES AND MOMENTS IN CYLINDRICAL VESSELS Piping by the adjoining nozzles exert local stress in the vessel. The method, below, to determine the nozzle loads is based in part on the Bulletin 107 of Welding Research Council and represents a simplification of it. The vessels are not intended to serve as anchor points for the piping. To avoid excessive loading in the vessel, the piping shall be adequately supported.
External Forces & Moments
To calculate the maximum force and moment, first evaluate p and y. Then determine a, I, and L1 from Figures I, 2 and 3, for the specified p and y, substitute into the equations below, and calculate F RRF, MRCM and MRLM.
P =.875 (~:)
y= Rm T
Determine a, I and L1 from Figures I, 2 and 3. Calculate Pressure Stress (oj.
If O'is greater than So, then use So as the stress due to design pressure.
M
III.M =
FRF
~
O~
__________
R,/r,,(.S
--..1-
Plot the value of F RRFas F RF and the smaller of MRCM and MRLM as M RM. The allowable nozzle loads are bounded by the area of F RF, 0, M RM.
~~
MRJo/
EXAMPLE: Determine Resultant Force and Moment
Rm=37.5 ro=15"
p=
T=.75" P=150psi
.875E~:) = .875 b~~5)= .35
From Figure I, a. = 440
y- 0')
From Figure 2, I = 1,070
Sv=31,500psi@460° S,,=20,000psi
y=
(Ri~ = 3.~; = 50
From Figure J, ..1 = 340
154 NOZZLE EXTERNAL FORCES AND MOMENTS IN CYLINDRICAL VESSELS (continued) Calculate Pressure Stress
f2}L 2C.1 50) (37.5 ".,. = 2P(1)m--2 - .7 5)= 14850 , pSI. < Sa = 20,000 psi. r 75 ~ 2
r
u
Use a = 14,850 in the equations for calculating FRRF and Calculate Allowable Forces and Moments _ R/I? _ (3.75)2 " _ FRRF--a (5v-0-)- 440 (-,1,500-14,850)-53,214Ib.
MRLM
37.5 2 (I5) (31,500) 1,070 620,984 in.-Ib.
0& MRJ,(
= 620, 984 in-lb.
Plot for the value of FRRF' as FRF and the smaller of M RCM and MRLM as M RM• The allowable nozzle loads are bounded by the area of FRF , 0, M RM . Therefore, a nozzle reaction of F = 20,000 lbs. and M = 100,000 in. lbs. would be allowable (point A) but a nozzle reaction of F = 5,000 Ibs. and M = 620,000* in. Ibs. would not be allowable (point B). *Note: Use absolute values in the graph.
NOTATION:
P
=
ro
= Nozzle Outside Radius, inches
Rm T Sy
=
Mean Radius of Shell, inches
=
Shell Thickness, inches
=
Yield Strength of Material at Design Temperature, pounds per square inch
MRCAF Maximum Resultant Circumferential
0'
=
Stress Due to Design Pressure, pounds per square inch
MP.LJ..F Maximum Resultant Longitudinal Mo-
Sa
=
Stress Value of Shell Material, pounds per square inch.
fJ r a
Design Pressure, pounds per sq. in.
=
Dimensionless Numbers
=
Dimensionless Numbers
I
=
L.1
= Dimensionless Numbers
FRRF
= Maximum Resultant Radial Force,
Dimensionless Numbers
pounds· Momentm , inch-pounds* ment, inch-pounds· FRF
= Maximum Resultant Force, pounds·
FRM
=
Maximum Resultant Moment, inchpounds*
·Use absolute values.
= Dimensionless Numbers
REFERENCES: Local Stresses in Spherical and Cylindrical Shells due to External Loadings, K. R. Wichman, A. G. Hopper and 1. L. Mershon - Welding Research Council. Bulletin 107/August 1965 - Revised Printing - December 1968. Standards for Closed Feedwater Heaters, Heat Exchange Institute, Inc., 1969.
155
NOZZLE LOADS Fig.!
-
-
2
=l'Y=
I '''-,-,- 1-
"""-.,,, .~
k
,-~+
__ •
'0--'-
, I
2
- 'c'
·--t--H
f,+-
I-
.
:
".;:.'-'--'
N-
--:.: fT-T , c;~.
r---- f--' ' ,
10 0
.05
,I
.15
.2
.25
.3
.35
.4
.45
. 'Y I ' '
.5
, I
156
NOZZLE LOADS Fig 2
1
'1 • • • • • • • • • 2
4
2
!_-----
103
9
2
2
10
o
.05
.1
.15
.2
.25
.3
.35
.4
.45
.5
157
NOZZLE LOADS Fig. 3
3
2
104 9 8 7 6
S 4
3
2
10] 9
lllllllllllllllllllllllllllllllllllllllllllll~!!~lIliiilii 2
102 9 8 7 6
3 2
10
o
.OS
.1
.IS
.2
.25
.3
.35
.4
{3
.45
.S
158
NOTES
159
REINFORCEMENT AT THE JUNTION OF CONE TO CYLINDER UNDER INTERNAL PRESSURE At the junction of cone or conical section to cylinder (Fig. C and D) due to bending and shear, discontinuity stresses are induced which are with reinforcement to be compensated. DESIGN PROCEDURE (The half apex angle
a 5'30 deg.)
1. Determine PISsEI and read the value of L1 from tables A and B.
2. Determine factor y, For reinforcing ring on shell, y = SsEs For reinforcing ring on cone, y I Sc Ec TABLE A - VALVES OF d FOR JUNCTIONS AT THE LARGE END PISs, Ell 0.001 I 0.002 I 0.003 I 0.004 10.005 I 0.006 I 0.007 I 0.008 J 0.009* d, deg., 11 I 15 I 18 I 21 I 23 I 25 I 27 I 28.5 I 30 TABLE B - VALVES OF d FOR JUNCTIONS AT THE LARGE END PISs, EI / / 0.002 / 0.005 / 0.010 / 0.020 / 0.040 / 0.080 / 0.100 I 0.125* d, deg.J I 4 , 6 I 9 I 12.5 I 17.5 I 24 I 27 I 30
* /). = 30 deg. for greater value of PISs E/
When the value of Ll is less than a, reinforcement shall be provided. 3. Determine factor k = y I Sr Er (Use minimum 1.0 for k in formula). 4. Design size and location of reinforcing ring (see next page). NOTATION E = with subscripts s, c or r modulus of elasticity of she 11, cone or reinforcing ring material respectively, psi. See charts beginning on page 43 for modulus of elasticity. E= with subscripts lor 2 efficiency of welded joints in shell or cone respectively. For compression E=1.0 for butt welds. fi = axial load at large end due to wind, dead load, etc. excluding pressure, lb/in.
ji= axial load at small end due to wind, dead load, etc. excluding pressure, lb/in. P= Design pressure, psi QI=algebraic sum of PRL I2 andfi Ib/in. Qs= algebraic sum of PRs/2 andji lb/in.
RL ~inside radius of large cylinder at large end of cone, in. Rs=inside radius of small cylinder at small end of cone, in. S= with subscripts s, cor r allowable stress of shell, cone or reinforcing material, psi. t= minimum required thickness of cylinder at the junction, in. ts= actual thickness of cylinder at the junction, in. t7= minimum required thickness of cone at the junction, in. tc= actual thickness of cone at the junction, in. a,= half apex angle of cone or conical section, deg. d= angle from table A or B, deg. y = factor: Ss Es or Sc Ec
160
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER
r::-r
FORMULAS a Max.
l~ ..... ~;
30°
JUNCTION AT THE LARGE END Required area of reinforcement, A sq. in. when tension governs (see notes)
e~
A
~ FIG. C
-
AeL
·· , \ -L I')
y,
=
(Is-I)
&;;; + (te-Ir) VRLte /
cos a
The distance from the junction within which the additional reinforcement shall be situated, in.
~
a Max. 30°
FIG. 0
(l-~)tana
kQIfiL SsE]
Area of excess metal for reinforcement, sq. in.
~
·
rL -
The distance from the junction within which the centroid of the reinforcement shall be situated, in. 0.25 x .,JRLfs
JUNCTION AT THE SMALL END Required area of reinforcement A sq. in. when tension governs (see notes) Ars
=
~~~) SsE! 1 a" tan a
Area of excess metal available for reinforcement A e, sq. in. Aes = (t s / t) cos (a -~) (ts-t) VR:i: + (te / Ir) X cos (a-~) (tc-tr) VRslc / cos a The distance from the junction within which the centroid of the reinforcement shall be situated, in.
vR;i; The distance from the junction within which the centroid of the reinforcement shall be situated, in. 0.25 x vii;i; NOTES: When atthe junction compressive loadsj; orji exceed the tensional loads determined by PR/ 2 or PR)2 respectively, the design shall be in accordance with U2 (g): ("as safe as those provided by the rules of the Code, Section VIII, Division 1.") When the reducers made out of two or more conical sections of different apex angles without knuckle, and when the half apex angle, a is greater than 30 deg., the design may be based on special analysis. (Code 1-5 (f) & (g).
161
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER EXAMPLE DESIGN DATA: a = 30 deg. half apex angle of cone.
E.EeEr= 30 X 106, modulus of elasticity, psi. EJEl = 1.0, joint efficiency in shell and cone EJ = 0.55, joint efficiency in reinforcing ring jj = 800 lb/in, axial load at large end
h
P RL
R. S, Sc S, t, t"
te tsl
RI .
-:\
~
tS5
trs
"
trL
952 lb/in, axial load at small end 50 psi., internal design pressure = 100 in., inside radius of large cylinder = 84 in., inside radius of small cylinder = 15,700 psi., allowable stress of shell material = 15,700 psi., allowable stress of cone material = 17,100 psi., allowable stress of ring material = 0.429 in., required min. thickness for large cylinder = 0.360 in., required min. thickness for small cylinder = 0.500 in. actual thickness of cone. = 0.4375 in., actual thickness of large cylinder = 0.375 in., actual thickness of small cylinder = 0.41 in., required thickness of cone at small cylinder = 0.49 in., required thickness of cone at large cylinder
= =
Using the same material for shell and cone. 1. PISsE/ = 15,7t~ x 1 = 0.0032 from table A L1 = 18.6 Since L1 is less than a: reinforcements is required.
2. Using reinforcement ring on the shell y= SsEs= 15,700 x 30 x 106 3. Factork=yISrEr = 15,700x30x 106 / 17,100x30x 106 =0.92 Use k= 1 4. QL =PRL/2ji , lb/in. = SO x 100 + 800 = 3,300 lb/in. 2 5. The required cross-sectional area of compression ring: A = kQLRL ~ \tan a-I x 3,300 x 100 11}8.6)tan 300= 4.62 sq in. rL a] 15,700 x 1 ~ 30 The area of excess in shell available for reinforcement: AeL =(t,I.-tl.) fRlt'1- + ((-(,/) vkLtc Icos a = (0.4375 - 0.429) x ~100 x 0.4375 + (0.5 - 0.49) x ~100 x 0.5/cos 30° = 0.132 sq. in. ArL - AeL = 4.62 - 0.132 = 4.49 sq. in. the required cross sectional area of compression ring Using 1 in. thick bar, the width of ring: 4.55/1 = 4.55 in.
It _
sp;-. '\
Location of compression ring: Maximum distance from the junction = vRJ; = ~100 x 0.4375 = 6.60 in. Maximum distance of centroid from the junction = 0.25 vif;h = 0.25 ~1 00 x 0.4375 = 1.65 in.
162
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER EXAMPLE (continued) JUNCTION AT SMALL CYLINDER
1.
PISs E/ = 0.0032; from table B ..1= 4.8 0 Since .1 is less than a., reinforcement is required.
2.
Factor y = Ss Es = 15,700 x 30 x 106
3.
Factor k = 1
4.
Qs = PR,/2 +1; lb.lin 50 ~ 84 + 952 = 3,052 lb.lin.
5.
The required cross-sectional area of compression ring~ .1) t 1 X 3,052 x 84~J W 300 -792 . - kQ.Rs A r'-SsE, ana. 15,700 x I ~-30Jtan -. sq.m.
(1 -u-
The area of excess in shell available for reinforcement: Aes =(t,/t,) cos (a -.1)(1,.,.-(,) X
vn;;:+ (lei I,)
cos (a. -.1) (Ie - 1r.1) VR.lelcos
a
(0.375/0.36) x cos(3-4.8) x (0.375 - 0.36) x ~84 x .0375
+ (0.5/0.41) cos (30-4.8)x (0.5-0.41) x ..J84 x 0.5/cos 30°= 0.77 sq. in. A". - A.s =7.92-0.77 = 7.15 sq. in., the required cross sectional area of com pression ring. Using 1~ thick bar, the required width of the bar: 7.15/1.5 -= 4.8 in. Location of the compression ring: Maximum distance from the junction: vfii:.,= ..J84 x 0.375 = 5.6 in. Maximum distance of centroid from the junction: vR;t;,= ..J84 x 0.375 = 1.4 in.
0.25
Insulation ring may be utilized as compression ring provided it is continuous and the ends of it are joined together. Since the-moment of in tertia of the ring is not factor, the use of flat bar rolled easy-way is more economical than the use of structural shapes. To eliminate the necessity of additional reinforcement by using thicker plate for the cylinders at the junction in some cases may be more advantageous than the application of compression rings.
163
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER UNDER EXTERNAL PRESSURE Reinforcement shall be provided at the junction of cone to cylinder, or at the junction of the large end of conical section to cylinder when cone, or conical section doesn't have knuckles and the value of ~, obtained from table E, is less than a. TABLE E - VALUES OF A P/SE 0 0.002 0.005 0.010 0.02 0.04 0.08 7 ~, deg 0 15 21 5 10 29 P/SE 0.125 0.15 0.20 0.25 0.30 0.35 ~, deg 37 40 47 52 57 60 ex = 60 deg. for greater values of P/SE Note: Interpolation may be made for intennediate values.
0.10 33
The required moment of intertia and cross-sectional area of reinforcing (stiffening) ring - when the half apex angle a is equal to or less than 60 degrees - shall be determined by the following formulas and procedure. I. Determine P/Se, and read the value of t1 from table E. 2. Determine the equivalent area of cylinder, cone and stiffening ring, ATL , sq. in. (See page 48 for construction of stiffening ring.) Make subscripts more visible
- LLts Lctc A ATL --2-+-2-+ s
3[F~ D )
Calculate factor B. B = -
4
ATL
where
2
2
M = -RL tan a + LL + RL -R,I' 2 2 3RL tana
If FL is a negative number, the design shall be in accordance with U-2 (g). 3. From the applicable chart (pages 43 thru 47) read the value of A entering at the value of B. moving to the left to the material/temperature line and from the intersecting point moving vertically to the bottom of the chart. For values of B falling below the left end of the materialltemperature line for the design temperature, the value of A = 2BI£. If the value of B is falling above the materialltemperautre line for the design temperature: the cone or cylinder configuration shall be changed, and/or the stiffening ring relocated, the axial compression stress reduced. For values of B having multiple values of A, such as when 8 falls on a horizontal portion of the curve, the smallest value of A shall be used. 4. Compute the value of the required moment of inertia For the stiffening ring only: 2
I = ADL ATL s
14.0
For the ring-shelkone section: 2 = ADL Au
Is
10.9
5. Select the type of stiffening ring and determine the available moment of inertia (see page 95) of the ring only I. or the shell-cone or the ring-shell-cone section 1'.
164
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER (continued) If lor l' is less than Is , or l's respectively, select stiffening ring with larger moment of inertia. 6. Determine the required cross-sectional area of reinforcement, A rL , sq. in. (when compression governs): A
= kQLRL tana SE
rL
[1-
Y4(PR L - QL QL
Ja~]
Area of excess metal available for reinforcement: AeL sq. in.: AeL
= O.55~ DLts (ts + tc / cos a)
The distance from the junction within which the additional reinforcement shall be situated, in.
The distance from the junction within which the centroid of the reinforcement shall be situated, in.
-.--;:r-r
O.2SJRL t s R,
'""-1-
Reinforcing shall be provided at the junction of small end of conical section without flare to cylinder. The required moment of inertia and cross-sectional area of reinforcing (stiffening) ring shall be determined by the following formulas and procedure. 1. Determine the equivalent area of cylinder, cone and stiffening ring, A TS sq. in.
Lsts Lctc A ATS =--+--+ s 2 2 2. Calculate factor B
B r----
I /
t3J
VESSEL VESSEL WITHOUT WITH STIFFENING STIFFENING RING RING FIG. G
=~(FsDsJ 4 A TS
I
where F.~ = PN +~tan
N
a. 2
= Rs tana + Ls + LL -Rs 2
2
2
6Rs tan a
If Fs is a negative number, the design shall be in accordance with U-2 (g).
165
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER (continued) 3. From the applicable chart (pages 43 thru 47) read the value of A entering at the value of B, moving to the left to the material/temperature line and from the intersecting point moving vertically to the bottom of the chart. For values of B falling below the left end of the material/temperature line for the design temperature, the value of A = 2BIE. If the value of B is falling above the material/temperature line for the design temperature: the cone or cylinder configuration shall be changed, and/or the stiffening ring relocated, the axial compression stress reduced. For values of B having multiple values of A, such as wh n B falls on a horizontal portion of the curve, the smallest value of A shall be used. 4. Compute the value of the required moment of inertia: For the stiffening ring only:
For the ring-shell-cone section: 2
l'
s
= ADs
= ADs
I
Ars 10.9
s
2
Ars 14.0
5. Select the type of stiffening ring and determine the available moment of inertia (see page 95) of the ring only, I and of the ring-shell-cone section, /'. If lor /' is less than ~\. or ~\. respectively, select stiffening ring with larger moment of inertia. 6. Determine the required cross-sectional area of reinforcement. Ars ' sq. in:
= kQsRs tan a
A
SE
rs
Area of excess metal available for reinforcement, A e , sq. in.
Aes =
O.55~Dsts ~ts -t)+(tc -tr)/cosa]
The distance from the junction within which the additional reinforcement shall be situated, in.
~Rsts The distance from the junction within which the centroid of the reinforcement shall be situated, in.
0.25~Rsts NOTE: When the reducers made out of two or more conical sections of different apex angles without knuckle, and when the half apex angle is greater than 60 degrees, the design may be based on special analysis. (Code 1-8 (d) and (e).) NOTATION A = area of excess metal available for e
reinforcement, sq. in. ArL = required area of reinforcement when QL is in compression, sq. in. A = required area of reinforcement TS when QL is in compression, sq. in.
As = cross-sectional area of the stiffening ring, sq. in. AT = equivalent area of cylinder, cone and stiffening ring, sq. in. B = factor D L = outside diameter or cone or large end of conical section, in.
166
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER (continued) Do Ds
E
outside diameter ofcylindrical shell, in. outside diameter at small end of conical section, in. lowest efficiency of the longitudinaljoint in the shell, head or cone; E = I for butt welds in compression.
E
with subscripts c, r or S modulus of elasticity of cone, reinforcement or shell material respectively, psi.
k
S~E./SRER
fi
h I I'
I, I's
L
Le
LL
but not less than 1.0. axial load at large end due to wind etc., lb./in. The value offi shal1 be taken as positive in all calculations. axial load at small end due to wind, etc. lb./in. The value ofh shall be taken as positive in all calculations. available moment of inertia of the stiffening ring, in4 available moment ofinertia ofcornbined ring-shell cross-section, in4. The width ofthe shell which is taken as contributing to the moment ~f inertia ofthe combined section: I.IO--JD"t required moment of inertia of the stiffening ring, in4.
required moment of inertia of the combined ring-shel1-cone crosssection, in4. axial length of cone, in. length ofcone along surface ofcone, or distance between stiffening rings of cone, in. design length of a vessel section, in/or stiffened vessel section: the distance between the cone-to-Iarge shell junction and an adjacent stiffening ring on the large shell. for unstiffened vessel section: the distance between the cone-to-Iarge-
Ls
P
QL
RL Rs
S SR
S,
te tr
ts
a ~
shelljunction and one-third the depth ofhead on the other end ofthe large shell. design length ofa vessel section, in. for stiffonedvessel section: distance between the cone-to-small-shell junction and an adjacent stiffening ring on the small shell. for unstiffoned vessel section: distance between the cone-to-smallshelljunctionandonethirdthedepth ofhead on the other end ofthe small shell. external design pressure, psi. PRL PRs
2+fi Q'=-2-+ h
axial compressive force due to pressure and axial load. outside radius oflarge cylinder, in. outside radius of small cylinder, in. allowable working stress, psi. of cone material. allowable stress of reinforcing material, psi. allowable stress of shell material, psi. minimum required thickness ofcylinder without allowance for corosion, in. actual thickness of cone without corrosion allowance, in. minimum required thickness ofcone without corrosion allowance, in. actual thickness of shell without allowance for corrosion., in. half apex angle, deg. value to indicate need for reinforcement, from table E, deg.
167
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER EXAMPLE DESIGN DATA
11"
t.
,II .
Design temperature = 500°F
SR trL trs
tc t, ts
DL = 96 in., outside diameter oflarge cylinder Ds = 48 in., outside diameter of small cylinder E = 0.7, efficiency oflongitudal weldedjoints of shell and cone Es' Ec' Er=30 X 106 ,modulus ofelasticity of shell, cone, and ring material, psi. fi = 100 Ib.in., axial load due to wind .12 = 30 Ib./in., axial load due to wind LL = 120 in., design length of large vessel section Ls = 244 in., design length of small vessel section Lc = 48 in. a = 30 deg., half apex angle of cone P = 15 psi, external design pressure RL = 48.00 in. outside radius oflarge cylinder Rs = 24.00 in. outside radius of small cylinder Ss = 17,100 psi. maximum allowable working stress of shell and cone material.
15700 psi. maximum allowable working stress of reinforcement material. 0.25 in. minimum required thicknes of large cylinder. = 0.1875 in. minimum required thickness of small cylinder. 0.25 in. actual thickness of cone. = 0.25 in. minimum required thickness of cone. 0.25 in. actual thickness of cylinder.
JUNCTION AT THE LARGE END 1. P/SE = 15/17100 = 0.00088; from table E ~ = 2.2 since ~ is less than a., reinforcement is required. 2. Assuming As= 0, An = LLt/2+L ctcl2+As = = 120xO.125+48xO.125+0=21 in 2. 48 2- 242 M= RL tan a +!!:... + RL2 - R/ _ 48 x 0.5774+ 120 T+ 3 x 48 x 0.5774=66.9 2 2 3RL tan a 2
FL = PM + ji tan a. = 15 x 66.9 + 100 x 0.5774 = 1061
168
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER EXAMPLE (continued) B=
J FD 4(:r) = 0.75
X
1061 x 96/21 = 3636
TL
3.
A = 0.0003 from chart on page 42.
4.
Required moment of inertia of the combined ring-shell-cone cross section: ADIAn 0.0003 x 96 2 x 21 _ . 4 I'.~= 10.9 = 10.9 - 5.32 Ifl.
5. Using two 2Y2 x Ih flat bars as shown, and the effective width of the shell: 1.10 x ..JDLI = 1.1 ..J96 x .025 = 5.389 in., The available moment of inertia: 5.365 in.4 (see page 95)
It is larger than the required moment of inertia. The stiffening is satisfactory. 6.
The required cross-sectional area of reinforcing: 6
k = S,rEr = 17100 x 30 x 10 = 1 09 S~R 15700 x 30 x 106 . PR 15 x 48 QL= 2 I +/1 2 + 100=460 ArL
_ kQLRL tan a [,1 II (PRL - QL\ ~] SE l.! -/4 Q J 0L
s
= 1.09 x 460 x 48 x 0.5774 r. _ 0 25 (15 x 48 - 460)2.2]= . 2 17100 x 0.7 l1! . 460 30 1.15 Ifl. The cross-sectional area of the stiffening -ring is 2.5 in 2. It is larger than the area required. The reinforcing shall be situated within a distance from the junction:
..JRLts = ~48 x 0.25 = 3.46 in. The centroid of the ring shall be within a distance from the junction:
0.25 ..JRLts = 0.25"48 x 0.25 = 0.86 in. JUNCTION AT THE SMALL END 1.
The conical section having no flare, reinforcement shall be provided.
2.
Asuming A.I
= 0,
Ars = Lstsl2 + Lctcl2 + As =
244 X 0.25/2 + 48 XO.25/2 + 0 = 36.5 inf N
Rs tan a LJ RL2 - R.~ 2 +2 + 6Rs tan a
24 x 0.5774
2
244
48 2 - 242
+ 2+ 6 x 24 x .5774
= 149.7 in.
169
REINFORCEMENT AT THE JUNCTION OF CONE TO CYLINDER EXAMPLE (continued) F~=PN+ /2
tan a
= 15 x 149.7+30xO.5774=2263
B = 3 FsDs = 3/4(2263 x 48) = 2232 "4 ~ 36.5 3. Since value of B falls below the left end of material/temperature line: A= 2 BIE = 2 x 2232/30 X 106 = 0.00014 Required moment of inertia of the combined ring-shell-cone cross section: l' = ADi Ars = 0.00014 x 48 2 x 36.5 = 1 08' 4 s 10.9 10.9 . m. 5. Using 2Y2 x Y2 flat bar, and the effective shell width:
4.
1.1 "48 x 0.25 = 3.81 in. The available moment of inertia 1.67 in.4 (see page 95)
It is larger than the required moment of inertia; the stiffening is satisfactory.
6. The required area of reinforcing:
k
= 1.09
QI'=
A . = kQ,R" tan S~E
T.I
a
P:~
+/2= 15
~ 24
+ 30 = 210 lb.lin.
= 1.09 x 210 x 24 x 0.5774 = 0.265 in. 2 17100 x 0.7
Area of excess metal available for reinforcement: Ae =
=~
R,dc (tc - t r) + "R,d.I· (1.1' - trs ) cos a
~2~~8~~5
(0.25 - 0.25) + "24 x 0.25 (0.25 - 0.1875) = 0.153 in. 2
A T.I· - Ae = 0.265 - 0.153 = 0.112 in. 2
The area of ring used for stiffening 1.25 in. 2 • It is larger than the required area for reinforcement. The reinforcing shall be situated within a distance from the junction:
-JR:i\= "24 x 0.25 = 2.44 in. and the centroid ofthe ring shall be within a distance from the junction: 0.25 "R,II.I = 0.25 "24 x 0.25 = 0.61 in.
170
WELDING OF PRESSURE VESSELS There are several methods to make welded joints. In a particular case the choice of a type from the numerous alternatives depend on: 1. The circumstances of welding 2. The requirements of the Code 3. The aspect of economy
1. THE CIRCUMSTANCES OF WELDING. In many cases the accessibility of the joint determines the type of welding. In a small diameter vessel (under 18 - 24 inches) from the inside, no manual welding can be applied. Using backing strip it must remain in place. In larger diameter vessels if a man way is not used, the last (closing) joint can be welded from outside only. The type of welding may be determined also by the equipment of the manufacturer. 2. CODE REQUIREMENTS. Regarding the type of joint the Code establishes requirements based on service, material and location of the welding. The welding processes that may be used in the construction of vessels are also restricted by the Code as described in paragraph UW-27. The Code-regulations are tabulated on the following pages under the titles:
a. Types of Welded Joints (Joints permitted by the Code, their efficiency and limitations of their applications.) Table UW-12
b. Design of Welded Joints (Types of Joints to be used for vessels in various services and under certain design conditions.) UW-2, UW-3 c. Examination of Welded Joints The efficiency of joints depends only on the type of joint and on the degree of examination and does not depend on the degree of examination of any other joint. (Except as required by UW-ll(a)(5) This rule of the 1989 edition of the Code eliminates the concept of collective qualification of butt joints, the requirement of stress reduction. 3. THE ECONOMY OF WELDING. If the two preceding factors allow free choice, then the aspect of economy must be the deciding factor. Some considerations concerning the economy of weldings: V-edge preparation, which can be made by torch cutting, is always more economical than the use of J or U preparation.
171 Double V preparation requires only half the deposited weld metal required for single V preparation. Increasing the size of a fillet weld, its strength increases in direct proportion, while the deposited weld metal increases with the square of its size. Lower quality welding makes necessary the use of thicker plate for the vessel. Whether using stronger welding and thinner plate or the opposite is more economical, depends on the size of vessel, welding equipment, etc. This must be decided in each particular case.
172
TYPES OF WELDED JOINTS JOINT EFFICIENCY, E TYPES CODE VW-12
1
~ IIZZZI
2
tfI2J ~//~
For circumferential ~ joint only
When the Joint: a. Fully Radiographed
b.
c.
Spot
Not
Examined
Examined
Butt joints as attained by double-welding or by other means which will obtain the same quality of deposited weld metal on the inside and outside weld surface. Backing strip if used shall be removed after completion of weld.
1.00
0.85
0.70
Single-welded butt jomt with backing stri p which remains in place after welding
0.90
0.80
0.65
Single-welded butt joint without use of backing strip
-
-
0.60
-
-
0.55
-
-
0.50
-
-
0.45
3
~ 4
i\ ,~\\~
?/~
Double-full fillet lap joint
5
~~!
Single-full fillet lap joint with plug welds
tm~
Single full fillet lap joint without plug welds
6
173
TYPES OF WELDED JOINTS LIMITAnONS IN APPLYING VARIOUS WELD TYPES
NOTES
FOR TYPE 1: NONE Joint Category: A, B, C, 0 FOR TYPE 2: NONE Joint Category: A, B, C, 0 Except butt weld with one plate off-set - for circumferential joints only. FOR TYPE 3: Joint Category: A, B, C Circumferential joints only, not over 5/8 in. thick and not over 24 in. outside diameter. FOR TYPE 4: (a) Longitudinal joints not over 3/8 in. thick. Joint Category: A (b) Circumferential joints not over 5/8 in. thick. Joint Category B,C For C joints these limitations not applicable for bolted flange connections.
FOR TYPE 5: (a) Circumferential joints for attachment of heads not over 24 in. outside diameter to shells not over ~ in. thick. Joints attaching hemispherical heads to shells are excluded. Joint Category B: (b) Circumferential joints for the attachment to shells of jackets not over 5/8 in. in nominal thickness where the distance from the center of the plug weld to the edge of the plate is not less than 1~ times the diameter of the hole for the plug. Joint Category: C FOR TYPE 6: (a) For the attachment of heads convex to pressure to shells not over 5/8 in. required thickness, only with use of fillet weld on inside of shell: Joint Category: A, B (b) For attachment of heads having pressure on either side, to shells not over 24 in. inside diameter and not over 'l4 required thickness with fillet weld on outside of flange only. Joint Category: A, B
1. In this table are shown the types of welded joints which are permitted by the Code in arc and gas welding processes. 2. The shape of the edges to be joined by butt-weld shall be such as to permit complete fusion and penetration.
3. Butt joints shall be free from undercuts, overlaps and abrupt ridges and valleys. To assure that the weld-grooves are completely filled, weld metal may be built up as reinforcement. The thickness of the reinforcement shall not exceed the following thicknesses. Plate thickness in. Maximum reinf. in. up to III incl. 3/32 over- Y2 to I incl. 1/8 over 1 3/16 4. Before welding the second side of a double welded butt joint, the impurities of the first side welding shall be removed by chipping, grinding or melting out to secure sound metal for complete penetration and fusion. For submerged arc welding, chipping out a groove in the crater is recommended. 5. The maximum allowable joint efficiencies given in this table are to be used in formulas, when the joints made by arc or gas welding processes.
6. Joint efficiency. E = I for butt joints in compression.
174
DESIGN OF WELDED JOINTS
formed head other than hemispherical
WELDED JOINT LOCATIONS To the joints under certain condition special requirements apply, which are the same for joints designated by identical letters. These special requirements, which are based on service, material, thickness and other design conditions, are tabulated below.
DESIGN CONDITION
JOINT TYPE AND CATEGORY
I. The design is based on joint efficiency I. 0 or 0.9 (See design conditions listed below when full radiography is mandatory. ) UW-II UW-12(d)
All category A and D butt welds in vessel sections and heads All category B or C butt welds (but not including those in nozzles or communicating chambers) which intersects the category A welds in vessel sections or heads or connect seamless vessel sections or heads Category A and B butt welds in vessel sections and heads shall be of Type (I) or Type (2)
2. Full radiographic examination is not mandatory UW-Il(b)
Type (I) or Type (2) butt welded joints
RADIOGRAPHIC EXAMINATION
JOINT EFFICIENCY
POST WELD HEAT TREATMENT
Full
Spot
Type (I) Type (2) 1.0 0.9
Per Code UCS·56
None
0.85 Joints Band C bUll welds in nozzles and communicating chambers that neither exceed 10 in. nom pipe size nor I 1/8 in wall thickness do not require
Spot
0.80 any radiographic examination except as required for ferritic steel wit h tensile properties enhanced by heat treatment UHT-57
Type (I) Type (2) 0.85 0.80
Per Code UCS-56
175
DESIGN OF WELDED JOINTS (CONT.) DESIGN CONDITION
JOINT TYPE AND CATEGORY
Any type of welded 3. Full radiographic joints. examination is not manditory. The vessel is designed for external pressure only. UW-II(c) Joints A shall be Type No. (I) UW-2(a)(I)(a) 4. Vessels containing lethal substances. UW-2(a) Joints Band C butt welds in nozzles and communicating chambers that neither exceed lain. in nom. pipe size or 1'1, in wall thickness do not require any radiographic examination except as required for ferritic steel with tensile properties enhanced by heat treatment UHT-57.
JOINT RADIOGRAPHIC EXAMINATION EFFICIENCY None
Joints of category C for the fabricated lap joint stub ends UW2(a)(I)(c).
5. Vessels Joints A shall be Type operated below -20°F No. (I) (except for austenitic chromium or impact nickel stainless steel). test is required for the material Joints B shall be Type No. (1) or No. (2). or weld metal UW- UW-2(b)(1) and (2). 2(b) Joints C full penetation welds extending through the entire section of the joint UW-2(b)(3).
(I) (2) (3) (4) (5) (6)
Full
Joints Band C shall be Type No. (I) or Type No. (2) UW-2(a)(1)(b) Joints D shall be full penetration welds extending through the entire thickness of the vessel or nozzle wall UW-2(a)(1)(d).
Type Type Type Type Type Type
0.70 0.65 0.60 0.55 0.50 0.45
1.0
1.0 Type (I) 0.9 Type (2)
All butt welded joints in shell and heads shall be fully radiographed except exchanger tubes and exchangers UW-2(a)(2) and (3) and per UW-II (a)(4)
Full Spot No
Type (I) 1.0 0.85 0.70
Type (2) 0.90 0.80 0.65
POST WELD HEAT TREATMENT Per Code USC-56
Vessels fabricated of carbon or low allow steel shall be post weld heat treated UW-2(a)
Per Code UCS-56
Joints D full penetration welds extending through the entire section at the joint UW-2(b)(4). 6. Unfired steam boilers with design pressure exceeding 50 psi See note above in this column at design condition 4:
Joints A shall be Type No. (I). Joints B shall be Type No. (1) or No. (2) UW-2(c)
All butt welded joints in shell heads shall be fully radiographed except under the provisions of UW-II(a)(4) TTW_?((")
1.0
1.0 Type (I) 0.9 Type (2)
Vessels fabricated of carbon or low alloy steel shall be post weld heat treated UW-2(c)
176
DESIGN OF WELDED JOINTS (CONT.) DESIGN CONDITION
JOINT TYPE AND CATEGORY
JOINT EFFICIENCY
POST WELD HEAT TREATMENT
Full Spot No
Type (I) Type (2) 1.0 0.90 0.85 0.80 0.70 0.65
When the thickness at welded joints of carbon steels (P-No. 1) exceeds 5/8 in. and all thicknesses for low alloy steels (other than PNo. I) post weld heat treatment is mandatory
Full
1.0 Type (I) 0.9 Type (2)
Per Code UCS-56
1.0 Type (I) 0.9 Type (2)
Per Code UCS-56
RADIOGRAPHIC EXAMINATION
Joints A shall be type No. (I)
7. Pressure vessels subject to direct firing
Joints B shall be type No. (I) or No. (2) when the thickness exceeds 5/8 in. No welded joints of type (3) are permitted for either A or B joints in any thickness UW-2(d) All but welds UW-II(a) (6)
8. Electroslag welding
Full 9. Final closure of vessels
10. Seamless vessel sections or heads UW-II(a) (5) (b) UW-12(d)
II.
Joints completed by pressure UW-12(f)
Ultrasonic examination when the construction does not permit radiographs
Any welds UW-Il(a) (7)
Joints connecting vessel sections and heads
Spot
1.0*
None or when A or B welds are type 3, 4, 5, 6
0.85*
Per Code UCS-56
Not greater than .80
Any Welds
EFFICIENCY (E) TO BE USED IN CALCULATIONS OF SEAMLESS HEAD THICKNESS ASME Code UW-l2(d) TYPE OF HEAD
TYPE OF JOINT
DEGREE OF EXAMINATION OF HEAD TO SHELL JOINT FULL
SPOT
NO
Hemi spherical
NOl
1.00
0.85
0.70
N02
0.90
0.80
0.65
Others
ANY
*For calculation involving circumferential stress or for thickness of seamless head
1.00
0.85
177
EXAMINATION OF WELDED JOINTS RADIOGRAPHIC EXAMINATION Full radiography is mandatory of joints: (Code UW-11) 1. All butt welds in shells, heads, nozzles, communicating chambers of unfired steam boilers having design pressures exceeding 50 psi and vessels containing
lethal substances. 2. All butt welds in vessels in which the least nominal thickness at the welded joint exceeds: 1 1/4 in. of carbon steel and 1 1/2 in. of SA-240 stainless steel Exemption: Categories Band C butt welds in nozzles and communicating chambers that neither exceed 10 in pipe size nor 1 1/8 in. wall thickness do not require radiographic examination in any of the above cases. 3. All category A and D butt welds in vessel sections and heads where the design of the joint or part is based on joint efficiency: 1.0, or 0.9. (see preceding pages: Design of Welding Joints). 4. All butt welds joined by electroslag welding and all electrogas welding with any single pass greater than 1 1/2 in.
Spot radiography, as a minimum, is mandatory of 1. Category B or C welds which intersect the Category A butt welds in vessel sections (including nozzles and communicating chambers above 10 in. pipe size and 1 in. wall thickness) or connect seamless vessel sections or heads when the design of Category A and D butt welds in vessel sections and heads based on a joint efficiency of 1.0 or 0.9. 2. Spot radiography is optional of butt welded joints (Type 1 or 2) which are not required to be fully radiographed. If spot radiography specified for the entire vessel, radiographic examination is not required of Category B and C butt welds in nozzles and communicating chambers. No Radiography. No radiographic examination of welded jOints is required when the vessel or vessel part is designed for external pressure only, or when the design of joints based on no radiographic examination.
ULTRASONIC EXAMINATION 1. In ferritic materials electroslag welds and electrogas welds with any single pass greater than 1 1/2 in. shall be ultrasonically examined throughout their entire length. 2. In addition to the requirements of radiographic examination, all welds made by the electron beam process or by the inertia and continuous drive friction welding process shall be ultrasonically examined for their entire length. 3. Ultrasonic examination may be substituted for radiography for the final closure seam if the construction of the vessel does not permit interpretable radiograph.
178
BUTT WELDED JOINTS OF PLATES OF UNEQ UAL THICKNESSES JOINING PLATES OF UNEQUAL THICKNESSES WITH BUTT WELD, THE THICKER PLATE SHALL BE TAPERED IF THE DIFFERENCE IN THICKNESS IS MORE THAN 1/8 IN. OR ONE-FOURTH OF THE THINNER PLATE. CODE UW-9(c), UW-13. THE LENGTH OF THE TAPERED TRANSITION SHALL BE MINIMUM 3 TIMES THE OFFSET BETWEEN THE ADJACENT SURFACES. THE WELD MAY BE PARTLY OR ENTIRELY IN THE TAPERED SECTION OR ADJACENT TO IT.
r~
l +-: 7----+ y
I
I
t ~ 3y Taper either inside or outside of vessel
t -, 1. -I
Tangent Line Y
t.f]f'£~ Tangent Line
~
HEADS TO SHELLS ATTACHMENT
,l ~ 3y Z z 1/2(ts-tW The shell plate centerline may be on either side of the head plate centerline.
HEADS TO SHELLS ATTACHMENT
J,
il:
3y
Z=..I/2 (th-ts)
When th exceeds ts" the minimum length of straight flange is 3th. but need not exceed 1-112 in. except when necessary to provide required length of taper. When th is equal to or less than 1.25Is• the length of straight flange shall be sufficient for any required taper. The shell plate centerline may be on either side of the head plate centerline.
179
APPLICATION OF WELDING SYMBOLS
WELD
MEANING OF SYMBO L
SYMBOL
/Y
dO
f I !
60°
~ l I J
'C7
i ~ ~ 60°
t 2 t
r±!
f ¥ } t~
r:±;
D
60°
cff
&
rrJ
, , OJ]
~ ~
"g" a .....
Yl"
I
~ '\"
j
>
1 I
S
~Yl
~
v( ,Y.
SYMBOL INDICATES SQUARE GROOYE WELD ON ARROW SIDE. ROOT GAP 1/8 IN.
SYMBOL INDICATES y. GROOYE WELD WITH AN ANGLE OF 60 DEGREES ON ARROW SIDE
SYMBOL INDICATES Y·GROOYE WELD WITH AN ANGLE OF 60 DEGREES ON ARROW SIDE AND BEAD·TYPE BACK WELD ON THE OTHER SIDE
SYMBOL INDICATES 1/2 IN. Y·GROOYE WELD
SYMBOL INDICATES y. GROOYE WELD ON ARROW SIDE AND ON OTHER SIDE WITH AN ANGLE OF 60 DEGREES
SYMBOL INDICATES y. GROOYE WELD ON ARROW SIDE AND ON OTHER SIDE WITH A ROOT OPENING OF 1/8 IN.
SYMBOL INDICATES PLUG WELD OF 1/21N. DIAMETER AND WITH AN ANGLE OF 60 DEGREES
SYMBOL INDICATES 1/4 IN. FILLET WELD
180
APPLICATION OF WELDING SYMBOLS
WELD
MEANING OF SYMBOL
SYMBOL
~
b
~
[b
SYMBOL INDICATES 3/8 IN. FILLET WELD ON ARROW SIDE AND 1/4 IN. FILLET WELD ON THE OTHER SIDE
SYMBOL INDICATES BEVEL GROOVE WITH AN ANGLE OF 45 DEGREES, 3/8 FILLET WELD ON ARROW SIDE AND BEAD TYPE BACK WELD ON OTHER SIDE
G
~
[b
Y4~
[b J1
D=f~
~
~22r ~
f,
-
/7
~v.
-1
~Y:~
I W
'7"
I
La---1 t
~ I11III
~
t
~t>
I
1/ S
SYMBOL INDICATES 1/4 IN. FILLET WELD ON ARROW SIDE AND BEVEL GROOVE WELD ON OTHER SIDE GRIND FLUSH ON OTHER SIDE
SYMBOL INDICATES BEVEL GROOVE WELD AND 3/8 FILLET WELD ON ARROW SIDE, BEVEL GROOVE AND 1/4 FILLET WELD ON OTHER SIDE
SYMBOL INDICATES WELD ALL AROUND 1/4 IN. FILLET WELD
SYMBOL INDICATES 1/4 IN. INTERMITTENT FILLET WELDS EACH 31N. LONG AND SPACED ON 6 IN. CENTERS. FIELD WELDED
SYMBOL INDICATES 1/4 IN. INTERMITTENT FILLET WELD. EACH 2 IN. LONG AND SPACED ON '8 IN. CENTERS. THE WELDS ARE STAGGERED.
SYMBOL INDICATES 1/4 IN. FILLET WELD ON ARRDW SIDE AND 3/8 FILLET WELD ON OTHER SIDE
181
CODE RULES RELATED TO VARIOUS SERVICES Service Air
Brief extracts of Code requirements
Code Paragraph
All pressure vessels for use with compressed air, except as permitted otherwise in this paragraph shall be provided with suitable inspection opening.
UG-46(a)
Min. thickness
UG-16(b)(4)
3/32
in.
Flammable and or noxIOUS gases and liquids
Expanded connections shall not be used.
UG-43 (b)(f)
Lethal substances
Butt welded joints in vessels to contain lethal substances shall be fully radiographed.
UW-2(a)
When fabricated of carbon or low allow steel shall be post weld heat treated.
UW-2(a)
The joints of various categories shall conform to paragraph UW-2. Steel plates conforming to sppecifications SA-36, SA-283 shall not be used.
USC-6(b)( 1)
Steam
Min. thickness
UG-16(b)(4)
Unfired steam boilers (1)
With design pressures exceeding 50 psi., the joints of various categories shall conform to paragraph UW-2.
Water (2)
3/32
in. shells and heads
Steel plates conforming to specifications SA-36, and SA-283 shall not be used.
USC-6(b)(2)
Min. thickness 1f4 in. shells and heads.
UG-16(b)(3)
Minimum thickness
3/32
in. shells and heads.
UG-16(b)(4)
NOTES:
I
1.
Unfired steam boilers may also be constructed in accordance with the rules of Code Section I. (Code V-leg)
2.
Vessels in water service excluded from the jurisdiction of the Code are listed in U-l(c)(6) and (7).
182
CODE RULES RELATED TO VARIOUS WALL THICKNESSES OF VESSEL Wall Thickness, in.
~ 2,4, IS
~
~6
2,4,5,6, 8,9, II, 12, 14
4,6,8,9 11,12,14 15
~
1;{6
7, 10, 13, 16,20
7, 10, 13, 16,20
7, 10, 13, 16,20
1 ;{6
l~
7, 13, 16, 17,20
7, 13, 16, 17, 20, 19, 22
%'2
;{6
2,4,15 2,3,4,5, 5,6,8,9, 6,8,9, II II, 12, 14 12, 14, 15
Applicable Notes
5,6,8,9, 11,12,14
Wall thickness, in.
Us
Applicable Notes
7, 10, II, 12, 14, IS
7, 10, II, 12,14, IS
Wall Thickness, in.
1 !{6
lYs
Applicable Notes
7, 13, 16, 17,20
7, 13, 16, 17,20
%
l~
~6
%
Y2
4,6,8,9 , 7,8,9, II, 7,8,9, II, 11,12, .14 12, 14, IS 12, 14, IS 15
1~6
I
7, 10, 13, 16,20
7, 10, 13, 16,20
7, 10, 13, 16,20
1 ~6
1%
I%;
1~ & over
7, 13, 16, 17, 18,21 19, 20, 22
7, 13, 16, 17, 18,21 19,20,22
7, 13, 16, 17, 18,21 19,20,22
7, 13, 16, 17, 18, 19, 20,21
Ys
.
_.
Notes (Brief Extracts of Code Requirements) 1. The minimum thickness of plate for welded construction shall be not UG-16 (b) less than 1116. The minimum thickness of shells and heads used in compressed air UG-16 (b) (4) service, steam service and water service shall be 3/32 in. 2. Manufacturers' marking shall be other than deep die stamping.
UG-77 (b)
3. In compressed air, steam and water service corrosion allowance not less than 116 of the calculated plat-e thickness shall be provided.
UCS-2S
4. Single, welded openings up to 3 in. pipe size do not require reinforcement.
UG-36 (c) (3)
S. The minimum thickness of shells and heads of unfired steam boilers
UG-16 (b) (S)
shall not be less than Y
6. Double full fillet lap joint for longitudinal welded joints is acceptable.
Table UW-12
7. Single, welded openings up to 2 in. pipe size do not require reinforceforcement.
UG-36 (c) (3)
8. Single full fillet lap joint with plug weld for attachment of heads not over 24 in. outside diameter to shells, acceptable.
Table UW-12
9. Maximum thickness of reinforcement for butt weld 3/32 in.
UW-3S (a)
10. Maximum thickness of reinforcement for butt weld 118 in. 11. Single full fillet lap joint with plug welds for circumferential joint
acceptable.
UW-3S (a) Table UW-12
183 CODE RULES RELATED TO VARIOUS WALL THICKNESSES OF VESSEL (Continued) Notes (Brief Extracts of Code Requirements) 12. Single full fillet lap joints without plug welds acceptable for attachment of heads convex to pressure to shells.
Table UW-12
13. Welded joints of pres sure vessels subject to direct firing in category B shall be type (1) or (2). Post weld heat treatment required.
UW-2 (d) (I) (2)
14. Single welded butt joint without use of backing strip acceptable for circumferential joints not over 24 in. outside diameter.
Table UW-12
15. Double full fillet lap joints for circumferential joint acceptable.
Table UW-12
16. Steel plates conforming to SA-36 and SA-283 shall not be used.
ueS-6 (b)(4)
17. The maximum thickness of reinforcement for but weld 31J 6 in.
UW-35 (a)
18. Butt welded joints in materials classified P-I shall be fully radiographed.
ueS-57
19. Post weld heat treatment ofP-1 materials is mandatory for all welded connections and attachments.
Table ueS-56
20. Double welded butt joint or single welded butt joint with backing strip shall be used for circumferential or longitudinal joints.
Table UW-12
21. Full radiographic examination of butt welded joints ofP-1 Grade 1,2, and 3 materials is mandatory.
UW-II(a)(2)
22. Post weld heat treatment ofP-1 materials is not mandatory provided that the material is pre-heated.
Table ueS-56 Note (2)(a)(b)
The governing thickness of pressure vessels and parts joined by welding shall be determined by: UW-JJ, UCS-57 for radiographing, UCS-66 for impact testing UW-lO, UW40(f), UCS-56, UHA-32 for post weld heat treatment.
See page 185 for low temperature operation.
184
TANKS AND VESSELS CONT AINING FLAMMABLE AND COMBUSTIBLE LIQUIDS Excerpt from the Department of Labor Occupational Safety and Health Standards (OSHA), Chapter XVII, Part 1910.106, (Federal Register, July 1, 1985) REGULATION
CLASSIFICATION ATMOSPHERIC TANKS Storage tank which has been designed to operate at pressures from atmospheric through 0.5 psig.
Atmospheric tanks shall be built in accordance with acceptable good standards of design. Atmospheric tanks may be built in accordance with: 1. Underwriters' Laboratories, Inc. Standards 2. American Petroleum Institute Standards No. 12A, No. 650, No. 12B, No. 120, & No. 12F.
LOW PRESSURE TANKS
Low-Pressure tanks shall be built in accordance with acceptable standards of design.
Storage tank which has been designed to operate
Low-Pressure tanks may be built in accordance with
at pressures above 0.5 psig.
1. American Petroleum Institute Standard No. 620.
but not more than 15 psig.
2. ASME Code for Pressure Vessels, Section VIII. (These tanks are not within the jurisdiction of the ASME Code Section VIII (U-ld) but may be stamped with the Code U Symbol U-lg) PRESSURE VESSEL Storage tank or vessel which nas been designed to operate at pressures above 15 psig.
Pressure Vessels shall be built in accordance with the ASME Code for Pressure Vessels, Section VIII.
In addition to the regulations of the above mentioned standards and code, the occupational safety and health standards contain rules concerning tanks and vessels as follows: 1. 2. 3. 4. 5. 6. 7.
Definition of combustible and flammable liquids Material of storage tanks Location of tanks Venting for tanks Emergency relief venting Drainage Installation of tanks
185
LOW TEMPERATURE OPERATION If a minimum design metal temperatureand thickness-combination of carbon and low alloy steels is below the curves in FIG UCS-66, impact testing is required.
~
140 120
0..
100 80
~
If the thickness at any welded joint exceeds 4 in. and the minimum design metal temperature is colder than 120°F. impact tested material shall be used.UCS-66(b).
I
g..
~
J
.VL-nr-
II
E-'
I, I
:
~ :~ Cl
§ :E ~ ~
/
='
AH carbon and aHoy steels listed in the following pages and not shown below. &
&
~~
/t"
1/~
-20 -40 -55_°60
f-~t\~COde.
_r-r-r-I\ \SA-5I5 Gr 60, SA-285 Gr A B _ f-i\.\SA-516 Gr 65 70 if not normalized
VI""'"'
2~ JlL
1 _ _
c-
..L
b---"III /V C
~
NOTE: In the Handbook the most commonly used materials are listed. For others see ASME
A
:E
~
For stationary vessels, when the coincident ratio in Fig. UCS-66.1 is less than one, this Figure provides basis to use material without impact testing. UG-66(b)
SA-516 Gr 55 & 60 ifnot normalized.
V
L
SA-516 all grades if normalized.
-
-I- -t- -j- t::'t=-If--+i+-Im"' l ""-pa""tc_t ....,~r-es_ti1""n.... g ..,.R_~-tu_i..,rer-d-t-......, -80 I 0.394
:E
I
2
I
4
Nominal Thickness, in.
NO IMPACT TEST IS REQUIRED: For bolts:
FIG. UCS-66 IMPACT TEST CURVES
For nuts:
~ r----
~
\
----
-_.
l"-t
~ I
~
r-- - -
REDUCTION OF MINIMUM METAL TEMPERATURE .
I
r---- r--
-~
--
---
SA-193 B7 to -55°F SA-307 B to -20°F SA-194 2H to -55°F
For I Y2 thick, SA-515 Gr 60 plate the minimum design temperature is from Fig. USC66 - 50°F.
1"-- ,.....
Rll":;~" ";lnOI "q~i;'~i; ~
/: ~ -50 to-ISO· F, at ratio
// ~:>V~~;f;~f;;i-~ /-~/)-//10:::/t;~d/'~~
EXAMPLE:
r~ 1;;-
If the actual stress in tension from internal pressure and other loads is 12,000 PSI, and the maximum allowable stress of the material is 17,100 psi, the ratio: 12,000/17,100=0.7
Temperature, FO
and from FIG. USC 66.1 the reduction is 30°F. The minimum design temperature is: 50-30 = 200F.
FIG. UCS-66.1 REDUCTION OF MINIMlJM MET AL TEMPERATURE
(Applicable joint efficiencies shall be included in the calculation of stresses.)
Impact test is not mandatory for materials which satisfy all of the following: I. the thickness of material listed in curve A does not exceed Y2 in. 2. the thickness of material listed in curves B. C and D does not exceed I in.
3. The vessel is hydrostatically tested. 4. the design temperature is not lower than -20°F and not higher than 650°F. 5. thermal, mechanical shock loading or cylindrical loading is not controlling design requirement.
20
40
60
80100120140
186
PROPERTIES OF MATERIALS CARBON & ALLOW STEEL *
Form
Specifications Nominal Number Number Composition SA-283 C C
APPLICATION Structural quality. For pressure vessel may be used with limitations see note: 1
C
SA-285
C
Boilers for stationary service and other pressure vessels.
C-Si
SA-515
(j)
For intermediate and higher temperature
C-Si
SA-515
65
For intermediate and higher temperature
C-Si
SA-515
70
For intermediate and higher temperature
C-Si
SA-516
55
For moderatee and lower temperature service
C-Si
SA-516
(j)
For moderate and lower temperature service
C-Mn-Si
SA-516
65
For moderate and lower temperature service
C-Mn-Si
SA-516
70
For ~oderate and lower temperature serVIce
C-Si
SA-234
WPB
'€
C-Mn-Si
SA-105
-
For ambient and higher temperature
ad
C-Si
SA-I8I
-
For general service
C-Mn-Si
SA-350
LFI
For low temperature service
C-Mn
SA-350
LF2
For low temperature service
C-Mn
SA-53
B
For general service
C-Mn
SA-106
B
For high temperature service
ICr-1I5 Mo SA-I93
B7
For high temperature service Bolt 21;2 in. diam or less
C
SA-194
2H
For high temperature service nut
C
SA-307
B
C
SA-36
-
For general structural purposes
C
SA-36
-
For general structural pU!]Joses
II)
~
0::
OJ)
c:
w:
For moderate and elevated temperature
II)
OJ)
c: ro
't:i: II)
0..
0:
OJ)
..§ '0 co .... ro co
Machine bolt for general use
*Data of the most frequently used materials from ASME Code Section II and VIII.
187
PROPERTIES OF MATERIALS CARBON & ALLOW STEEL * (continued) Form
Specification
Tensile Strength 1,000 psi
Grade
p Number
SA-283
C
1
55.0
30.0
2
SA-285
C
1
55.0
30.0
1,4
SA-515
(j)
1
60.0
32.0
1,4
SA-515
65
1
65.0
35.0
1,4
SA-515
70
1
70.0
38.0
1,4
SA-516
55
1
55.0
30.0
1,4
SA-516
(j)
1
60.0
32.0
1,4
SA-516
65
1
65.0
35.0
1,4
SA-516
70
1
70.0
38.0
1,4
SA-234
WPB
1
60.0
35.0
1,3
1
70.0
36.0
1,4
Number
Yield Point 1,000 psi
See Notes
~
0::
O/J
c::
'13
SA-105
~
SA-I8I
I
1
60.0
30.0
1,4
SA-350
LFI
1
60.0
30.0
1,4
SA-350
LF2
1
70.0
36.0
1,3
SA-53
B
1
60.0
35.0
1,3
SA-106
B
1
60.0
35.0
1,3
SA-193
B7
-
125.0_
105.0
SA-194
2H
-
SA-307
B
-
~
O/J
c::
G:'" Seamless Pipe O/J
.§ "0
co
.....
co'"
Diam.':;::2Yz in.
5
55.0
-
-
60.0
-
-
SA-36
1
58.0
1
SA-36
1
36.0
1,3
188
PROPERTIES OF MATERIALS CARBON & LOW ALLOY STEEL (continued)
NOTES 1.
Upon prolonged exposure to temperatures above 800 0 F, the carbide phase of carbon steel may be converted to graphite.
2.
SA-36 and SA-283 ABeD plate may be used for pressure parts in pressure vessels provided all of the following requirements are met: UCS-6 (b) (l) The vessels are not used to contain lethal substances, either liquid or gaseous; (2) The material is not used in the construction of unfired steam boilers (sec Code U-l (g); (3) With the exception of flanges, flat bolted covers, and stiffening rings the thicckness of plates on which strength welding is applies does not exceed 5/8 in.
3.
Allowable stresses for temperatures of 700 0 F and above are values obtained from time-dependent properties.
4.
Allowable stresses for temperatures of 750 0 F and above are values obtained from time-dependent properties.
5.
Stress values in bearing shall be 1.60 times the values in tables.
MODULI OF ELASTICITY FOR FERROUS MATERIALS Materials -100 Carbon steels with C < 0.30% Carbon steels with C> 0.30%
70 29.5
200 28.8
30.2 29.3 30.0
28.6
Million psi, for Temperature of. of: 400 500 600 700 800 27.3 25.5 27.7 24.2 26.7 28.1 27.1 25.3 27.5 26.5 24.0 300 28.3
900 22.4
1000 20.4
22.3 20.2
The values in the External Pressure Charts are intended for external pressure calculations only.
189
PROPERTIES OF lVIATERIALS CARBON & LOW ALLOY STEEL Maximum Allowable Stress Values in Tension 1000 psi." Specitication Numbcr Grade
-20 400
500
For l'.letal Temperature Not Exceedin~ De~. F. 650 750 850 600 700 800
950 900
SA-283
C
15.7
15.7
15.3
14.8
-
-
-
-
-
SA-285
C
15.7
15.7
15.3
14.8
14.3
13.0
10.8
8.7
5.9
SA-SIS
60
17.1
17.1
16.4
15.8
15.3
13.0
10.8
8.7
SA-SIS
65
18.6
18.6
17.9
17.3
16.7
13.9
11.4
SA-SIS
70
20.0
20.0
19.4
18.8
18.1
14.8
SA-516
55
15.7
15.7
15.3
14.8
14.3
SA-516
60
17.1
17.1
16.4
15.8
SA-516
65
18.6
IR.6
17.9
5A-516
70
20.0
20.0
SA-234
WPB
17.1
SA-lOS
-
SA-181
I
SA-350
1000
-
-
5.9
4.0
2.S
8.7
5.9
4.0
2.5
12.0
9.3
6.7
4.0
2.5
13.0
10.8
8.7
5.9
4.0
2.5
15.3
13.0
10.8
8.7
5.9
4.0
2.5
17.3
16.7
13.9
11.4
8.7
5.9
4.0
2.5
19.4
18.8
18.1
14.8
12.0
9.3
6.7
4.0
2.5
17.1
. 17.1
17.1
15.6
13.0
10.8
8.7
5.9
4.0. 2.5
20.0
19.6
18.4
17.8
17.2
14.8
12.0
9.3
6.7
4.0
2.5
17.1
16.3
15.3
14.8
14.3
13.0
10.8
8.7
5.9
4.0
2.5
LFI
17.1 .
16.3
15.3
14.8
14.3
13.0
10.8
8.7
5.9
4.0
2.5
SA-350
LF2
20.0
19.6
18.4
17.8
17.2
14.8
12.0
9.3
6.7
4.0
2.5
SA-53
B
17.1
17.1
17.1
17.1
15.6
13.0
10.8
8.7
5.9
-
-
SA-lOG
B
17.1
17.1
17.1
17.1
15.6
13.0
10.8
8.7
5.9
4.0
2.5
SA-193
B7:S;2W'
25.0
25.0
25.0
25.0 -
25.0
23.6
21.0
17.0 12.5
8.5
4.5
SA-194
2H
SA-307
B
SA-36
-
15.2
15.2
15.2
15.2
-
-
-
-
-
-
-
SI\-36
-
16.6
16.6
16.6
16.6
15.6
130
10.8
8.7
5.9
-
-
I ---.--+--~-1·-·---- -_._- ..
1"--
--. ----.--- f-.--_.........--....·.-...·· .. r- '" The
Stre~s
.!
: - - - - f-.
-_.
Values in this table may be intcrpolated to detennin'e values for intennediate temperatures._ The value~ shown in bold obtained from time-dependentpl'Ope/'/ies. J ! l L_~..J..-· _L~..,.. r L ..__+-...-.J.~,,,~
The stress values shown in this table are used throughout tIllS book. Pressure Vessel Handbook - 12th Edition
190
PROPERTIES OF MATERIALS STAINLESS STEEL P-No. 8 Group No. 1 TABLE 1 Product o~
~~
Z 00
r;) 0
~
til
Smls. Pp.
SA·312
TP304H
-
;:....~
Smls. Pp.
SA·376
TP304
2
U
TP304H F304
-
Forg.
SA·376 SA·182
'D
Forg. Bar
SA·182 SA-479
F304H
-
304
23
~
SA·240 SA·213
316 TP316
23 2
Smls. Th.
SA·213
TP316H
-
SA·312 SA·312
TP316
2
til
Smls. Pp. Smls. Pp.
TP316H
-
;:....~
Smls. Pp.
SA·376
TP316
2
Smls. Pp. Forg.
SA·376 SA·182
TP316H
-
~ I
-Z
2
F316
2
Forg.
SA·182 SA-479
F316H 316
-
23
Spec. No.
Grade
Notes
SA·240 SA-213
316L TP316L TP316L
-
o~
]~
2
0...
Notes
Z
-
Smls. Pp.
Grade
~~
TP304
1=1
Spec. No.
I
N
TP304H
d ~~
E=
Product
0
SA·213
.5
0
23 2
SA·312
.2:!
Z
Notes
304 TP304
Smls. Pp.
. U "oc;::
-
Grade
SA·240 SA·213
Smls. Th.
til
~..I
00
Spec. No.
Plate Smls. Th.
~
.-
I
TABLE 3
. "oc;:: ~
-
.2:!
1=1
.5
d ~~
0
E=
r;) 0
0
Plate Smls. Th.
Bar
0...
U
~
TABLE 2
.....:I
Z
Product
~
Spec. No.
Grade
Notes
""'0 Nt-"0 til
Z
"01=1
">=~
SA·240 SA-213
Smls. Pp.
SA·312
304L TP304H TP304L
Bar
SA·479
304L
Plate Smls. Th.
25
-
-
~ 0
Z
-
Product
.....:I
00
0
TABLE 4
0
u 00
""'0 Nt-"0 til "01=1
">=~
Plate Smls. Th. Smls. Pp. Bar
SA·312 SA-479
-
316L
-
MAXIMUM ALLOWABLE STRESS VALUES, 1,000 psi. FOR METAL TEMPERATURES NOT EXCEEDING DEG. OF.
MATERIALS IN TABLE 1 2 3 4
-20-100 200 20.0 20.0 20.0 16.7 16.7 16.7 16.7 14.3 20.0 20.0 20.0 17.3 16.7 16.7 16.7 14.2
MATERIALS IN TABLE
I
3
950
1000
14.3 10.6 15.4 11.4
14.0 lOA 15.3 11.3
300 18.9 IS.0 16.7 12.8 20.0 15.6 16.7 12.7
400
800
18.3
15.2 11.2
500 600 650 700 750 IS.8 15.5 17.5 16.6 16.2 11.7 12.9 12.3 12.0 11.5 13.8 14.7 14.0 13.7 13.5 13.3 15.8 10.2 10.9 10.4 10.0 9.8 11.7 17.0 16.3 18.0 16.6 16.1 19.3 12.6 12.1 11.9 14.3 13.3 12.3 14.8 14.0 13.5 13.2 15.1 13.7 10.9 10.2 10.0 9.8 11.7 10.4 FOR METAL TEMPERATURES NOT EXCEEDING 1300 1350 1050 1100 11 SO 1200 12S0
12.4 10.1 15.1 11.2
9.8 9.8 12.4 11.1
7.7 7.7 9.8 9.8
6.1 6.1 7.4 7.4
4.7 4.7 5.5 5.5
3.7 3.7 4.1 4.1
2.9 2.9 3.1 3.1
850 14.9
900 14.6
11.0
10.8
13.0
-
-
9.7 15.9 11.8
-
-
12.9 9.6
Note! I I
15.7 11.6
IS.6 11.5
I
12.7
-
1
9.4
DEG. OF. 1400
14S0
1500
2.3 2.3 2.3 2.3
1.8 1.8 1.7 1.7
1.4 1.4 1.3 1.3
I I
NOTES: 1. These higher stress values exceed 2/3 but do not exceed 90% of the yield strength at temperature. Use 0
these stress values may result in dimensional changes due to permanent strain. These stress values are not recommended for flanges or gasketed joints or other applications where slight amounts of distortion can cause leakage or malfunction. 2. At temperatures above 1,000° F, these stress values apply only when the carbon is 0.04% or higher. 3. For temperatures above 1,000° F, these stress values may be used only if the material is heat treated by heating it to a minimum temperature of 1,900° F and quenching in water or rapidly cooling by other means.
191
THERMAL EXPANSION Linear Thermal Expansion between 70F and Im:licated Temperature, Inches/IOO Feet THE DATA OF THIS TABLE ARE TAKEN FROM THE AMERICAN STANDARD CODE FOR PRESSURE PIPING. IT IS NOT TO BE IMPLIED THAT MATERIALS ARE SUITABLE FOR ALL THE TEMPERATURES SHOWN IN THE TABLE. MATERIAL Carbon Steel Austenitic remp. Carbon·Moly 5CrMo Stainl_ thru IegF Low·Chrome St..ls Ithru 3 Cr Mol 9 CrMo 18 Cr 8 Ni -325 -2.37 -2.22 -3.85 -300 -2.24 -2.10 -3.63 -275 -2.11 -1.98 -3.41 -250 -1.98 -1.86 -3.19 -225 -1:85 -1.74 -2.96 -200 -1.71 -1.62 -2.73 -175 -1.58 -1.50 -2.50 -150 -1.45 -1.37 -2.27 -125 -1.30 -1.23 -2.01 -LIS -100 -1.08 -1.75 -t.OO -0.94 -1.50 - 75 -0.84 -0.79 -1.24 - 50 -0.98 -0.68 -0.63 - 25 -0.49 -0.46 -0.72 0 -0.32 -0.46 25 -0.30 -0.14 -0.13 50 -0.21 70 0 0 0 0.22 100 0.23 0.34 125 0.42 0.40 0.62 0.61 0.58 150 0.90 175 1.18 0.76 0.80 1.46 0.99 0.94 200 1.75 1.21 1.13 225 1.40 250 1.33 2.03 275 1.61 2.32 1.52 2.61 300 1.82 1.71 325 2.04 2.90 1.90 350 2.26 2.10 3.20 375 2.48 2.30 3.50 400 2.70 2.50 3.80 4.10 425 2.93 2.72 2.93 4.41 450 3.16 4.71 3.14 475 3.39 3.62 3.35 5.01 500 3.86 3.58 5.31 525 550 4.11 3.80 5.62 4.35 4.02 5.93 575 4.60 4.24 6.24 600 4.86 4.47 6.55 625 4.69 6.87 5.11 650 4.92 7.18 675 5.37 7.50 5.63 S.14 700 5.38 7.82 725 5.90 8.15 750 6.16 5.62 775 6.43 5.86 8.47 8.80 6.70 6.10 800 9.13 6.34 6.97 825 6.59 9.46 7.25 850 6.83 875 9.79 7.53 7.07 10.n 900 7.81 7.31 10.46 925 8.08 7.56 10.80 8.35 950 7.81 11.14 975 8.62 8.06 11.48 1000 8.89 11.82 9.17 8.30 1025 n.16 1050 9.46 8.55 12.50 9.75 8.80 1075 12.84 10.04 9.05 1100 13.18 9.28 10.31 1125 13.52 9.52 10.57 I ISO 9.76 13.86 10.83 1175 14.20 11.10 10.00 1200 14.54 10.26 1225 11.38 10.53 14.88 11.66 1250 15.22 11.94 10.79 1275 11.06 15.56 17.22 1300 15.90 12.50 11.30 1325 16.24 n.78 11.55 1350 11.80 16.58 13.06 1375 n.05 16.92 13.34 1400 17.30 1425 17.69 1450 18.08 1475 18.47 1500
12Cr nCr 27Cr -2.04 -1.92 -1.80 -1.68 -1.57 -1.46 -1.35 -1.24 -1.11 -0.98 -0.85 -0.72 -0.57 -0.42 -0.27 -0.12 0 0.20 0.36 0.53 0.69 0.86 1.03 1.21 1.38 1.56 1.74 1.93 2.11 2.30 2.50 2.69 2.89 3.08 3.28 3.49 3.69 3.90 4.10 4.31 4.52 4.73 4.94 5.16 5.38 5.60 5.82 6.05 6.27 6.49 6.71 6.94 7.17 7.40 7.62 7.95 8.18 8.31 8.53 8.76 8.98 9.20 9.42 9.65 9.88. 10.11 10.33 10.56 10.78 11.01
25 Cr 20Ni
0 0.32 0.58 0.84 1.10 1.37 1.64 1.91 2.18 2.45 2.72 2.99 3.26 3.53 3.80 4.07 4.34 4.61 4.88 5.15 5.42 5.69 5.96 6.23 6.50 6.77 7.04 7.31 7.58 7.85 8.15 8.45 8.75 9.05 9.35 9.65 9.95 10.25 10.55 10.85 11.15 11.45 11.78 n.ll 12.44 12.77 13 ..10 13.43 13.76 14.09 14.39 14.69 14.99 15.29
Monel 67 Ni 30Cu -2.62 -2.50 -2.38 -2.26 -2.14 2.02 -1.90 -1.79 -1.59 -1.38 -1.18 -0.98 -0.77 -0.57 -0.37 -0.20 0 0.28 0.52 0.75 0.99 1.22 1.46 1.71 1.96 2.21 2.44 2.68 2.91 3.25 3.52 3.79 4.06 4.33 4.61 4.90 5.18 5.46 5.75 6.05 6.34 6.64 6.94 7.25 7.55 7.85 8.16 8.48 8.80 9.n 9.44 9.77 10.09 10.42 10.75 11.09 11.43 11.77 12.11 n.47 12.81 13.15 13.50 13.86 14.22 14.58 14.94 15.30 15.66 16.02
3~
Nickel Aluminum
-2.25 -2.17 -2.07 -1.96 -1.86 -1.76 -1.62 -1.48 -1.33 -1.17 -1.01 -0.84 -0.67 -0.50 -0.32 -0.15 0 0.23 0.42 0.61 0.81 1.01 1.21 1.42 1.63 1.84 2.05 2.26 2.47 2.69 2.91 3.13 3.35 3.58 3.81 4.04 4.27 4.50 4.74 4.98 5.22 5.46 5.70 5.94 6.18 6.43 6.68 6.93 7.18 7.43 7.68 7.93 8.17 8.41
-4.68 -4.46 -4.21 -3.97 -3.71 -3.44 -3.16 -2.88 -2.57 -2.27 -1.97 -1.67 -1.32 -0.97 -0.63 -0.28 0 0.46 0.85 1.23 1.62 2.00 2.41 2.83 3.24 3.67 4.09 4.52 4.95 5.39 5.83 6.28 6.72 7.17 7.63 8.10 8.56 9.03
Gray Bronze ClISt Iron
0 0.21 0.38 0.5~
0.73 6.90 1.08 1.27 1.45 1.64 1.83 2.01 2.2 2.4 2.62 2.83 3.03 3.24 3.46 3.67 3.89 4.11 4.34 4.57 4.80 5.03 5.26 5.50 5.74 5.98 6.22 6.47 6.72 6.97 7.23 7.50 7.76 8.02
-3.98 -3.74 -3.50 -3.26 -3.02 -2.78 -2.54 -2.31 -2.06 -1.81 -1.56 -1.32 -1.25 -0.77 -0.49 -0.22 0 0.36 0.66 0.96 1.26 1.56 1.86 2.17 2.48 2.79 3.11 3.42 3.74 4.05 4.37 4.69 5.01 5.33 5.65 5.98 6.31 6.64 6.96 7.29 7.62 7.95 8.28 8.62 8.96 9.30 9.64 9.99 10.33 10.68 11.02 11.37 11.71 12.05 12.40 12.76 13.11 13.47
192 DESCRIPTION OF MATERIALS When describing various vessel components and parts on drawings and in bill of materials, it is advisable that a standard method be followed. For this purpose it is recommended the use of the widely accepted abbreviations in the sequences exemplified below. For ordering material the requirements of manufacturers should be observed. PART
DESCRIPTION
MATERIAL SPECIFICATION
~
BAR
Bar 2 x 1/4 x 3' - 6 Bar 3/4 ¢ x 2 '- 0 Bar 1 cp x 3'- 0
[J::a
BOLT
3/4 ¢ x 2-1/2 H. Hd. M. B. w/ (1) sq. nut SA-193 B7 bolt 1 f/J x 5-1/2 stud w/ (2) h. nuts SA-194 2H nut
0
CAP
8" Std. Cap
ICJ
Screwed COUPLING
I" - 6000 # 2" - 3000 # 1" - 6000 # 1" - 6000 #
~
Welding ELBOW
6" - Std. 90 0 L. R. Ell. 4" - X Stg. 45 0 S. R. Ell. 6" x 4" Std. L. R. Red. Eli
SA-234 WPB
FLANGE
4" - 300# RF. So. Fig. 6" - 150# RF. Wn. Fig. Std. Bore 6" - 600# RTJ. Wn. FIg. X Stg. Bore 3" - 150# FF. So. FIg. 8" - 150# R.F. Bid. FIg.
SA-181 1
Screwed Socket Welding FORGED FITTING
1" - 6000 # 90 0 Scr'd. Ell. 1" - 3000 # 90 0 Scr'd. Street Ell. 2" - 3000 # S.W. Cplg. 1" - 3000# Sq. Hd. Plug 2" - 6000 # Scr'd. Tee 2" - 3000 # 45 0 S. W. Ell.
SA-lOS
GASKET
18 - 150 # 1/16" Servo Sht. Gasket 18 - 300 # Spiral Wound ASB. Filled
ASB.
HEAD
48" ID x 0.375 min. 2: 1 eHip. head 2" S.F. 48" OD x 0.500" min. ASME F & D Head 2 S.F. L =48" r = 3" 54" ID x 0.375" min. Hemis. Head
@ • • ~ (JJ
~
© 8
Cplg. Cplg. Half Cplg. 4-1/2 Lg. Cplg.
SA-7
SA-lOS
SA-285 C SA-515-70 SA-516-70
193 DESCRIPTION OF MATERIALS (cont.) Long [p Welding Neck
18" - 300
RF. LWN
SA-181 1
PIPE
6" - Std. Pipe x 2'-1 8" -X Stg. Pipe x l' - 6-1/2 4" - S. 160 Pipe x 2'-4 24" - 0.438" Wall Pipe xl' - 0
SA-53 B
cJ
PLATE
It 96" x 3/8 x 12' - 6 It24"ODx 1/2x 18"ID 1l18" OD x 1-1/2
SA-285 C
[::J
Welding REDUCER
6" x 4" Std. Conc. Reducer 8" x 6" X Stg. Ecc. Reducer
SA-234 WPB
~
Welding RETURN
6" - Std. 1800 L. R. Return 4" - X Stg. 1800 S. R. Return
SA-234 WPB
0
Welding TEE
4" - Std. Tee 6" x 6" x 4" X Stg. Red. Tee
SA-234 WPB
~
\0 +;:..
EQUIVALENT & COMPARABLE MATERIALS OF FOREIGN COUNTRIES European Standard
U.S.A.
Germany
United Kingdom
Japan
SA285 Gr. B
P235 GH
HI
161 Gr400
SB410
SA 515 Gr60 SA 515 Gr70 SA 299 SA204Gr A SA 387 Gr 12 Class 2 SA 387 Gr 22 Class 2 SA 516 Gr60 SA516Gr70 SA 572 Gr65
P265 GH P295 GH P355 GH 16 Mo3 13 CrMo4-5 10 Cr Mo 9-10 P275NH P355NH P460NH
HII 17 Mn4
161 Gr430 224 Gr340 225 Gr490
SB480 SPY 315 SPV356 SB480M SCMV2Div.2 SCMV4Div.4
SA 240 - 410 S
X6Cr 13 X6 Cr Al13 X5 CrNi 18-10 X2 Cr N i 19-11 X5CrNiMo 17-12-2 X2CrNiMo 17-12-2 X2 CrNi Mo 18-15-4
SA 240 - 405 SA 240 - 304 SA240- 304 L SA 240 - 316 SA 240 - 316 L SA 240 - 317 L
19Mn6 15 Mo3 13 CrMo 44 10 CrMo 910 WStE285 ,WStE 355 WStE460
-
630 Gr27 620 Gr 31 164 Gr 400, Lt 20 225 Gr 490, Lt. 20
SGV450 -
-
-
1.4000 1.4002 1.4301 1.4306 1.4401
403 S 17 405 S 17 304 S 31 304 S 11 316S31
410 S 405 304 304L 316
1.4404 1.4438
316S11
316L 317 L
-
CODES, STANDARDS, SPECIFICATIONS EN 10028-2,
AS ME Code II. -_.
_ _ .-
_1 0028=-~,1 0088
DIN 17 102, 17155,17440
BS 1501,4360, 970, 1442
JIS G 3103,3115,4109, 3118,4304 sus
I
195
SPECIFICATION FOR THE DESIGN AND FABRICATION OF PRESSURE VESSELS NOTES: Pressure vessel users and manufacturers have developed certain standard practices which have proven advantageous in the design and construction of pressure vessels. This specification includes those practices which have become the most widely accepted and followed. These standards are partly references to the selected alternatives permitted by the ASME Code, and partly described design and construction methods not covered by the Code. The regulations of the Code are not quoted in this Specification. AGENERAL
1. This Specification, together with the purchase order and drawings, covers the requirements for the design and fabrication of pressure vessels. 2. In case of conflicts, the purchase order and drawings take precedence over this Specification. 3. Pressure vessels shall be designed, fabricated, inspected and stamped in accordance with the latest edition ofthe ASME Boiler and Pressure Vessel Code, Section VIII, Division 1, and its subsequent addenda. 4. Vessels and vessel appurtenances shall comply with the regulations of the Occupational Safety and Health Act (OSHA). 5. Vessel Manufacturers are invited to quote prices on alternate materials and construction methods if economics or other aspects make it reasonable to do so. 6. All deviations from this Specification, the purchase order, or the drawings shall have the written approval of the purchaser. 7. Vessel fabricator, after receipt of purchase order, shall furnish to purchaser checked shop drawings for approval. B. DESIGN
1. Pressure Vessels shall be designed to withstand the loadings exerted by internal or external pressure, weight of the vessel, wind, earthquake, reaction of supports, impact, and temperature. 2. The maximum allowable working pressure shall be limited by the shell or head, not by minor parts. 3. Wind load and earthquake. All vessels shall be designed to be free-standing. To determine the magnitude of wind pressure, the probability of earthquakes and seismic coefficients in various areas of the United States, Standard ANSIIASCE 7-95 (Minimum Design Loads in Buildings and Other Structures) shall be applied. It is assumed that wind and earthquake loads do not occur simultaneously, thus the
vessel should be designed for either wind or earthquake loading, whichever is greater. 4. Horizontal vessels supported by saddles shall be designed according to the method of L. P. Zick (Stresses in Large Horizontal Pressure Vessels on Two Saddle Supports). 5. The deflection of vertical vessels under normal operating conditions shall not exceed 6 inches per 100 feet oflength.
196 Specification for the Design and Fabrication of Pressure Vessels (continued) 6. Stresses in skirts, saddles, or other supports and their attachment welds may exceed the maximum allowable stress values of materials given in Part UCS of the ASME Code by 33-1/3 percent. 7. Vessel manufacturers shall submit designs for approval when purchaser does not furnish a design or does not specify the required plate thickness.
c. FABRICATIUN 1. Materials shall be specified by purchaser and their designation indicated on the shop drawings. Materials shall not be substituted for those specified without prior written approval of purchaser. 2. The thickness of plate used for shell and heads shall be 1/4-inch minimum. 3. Manufacturer's welding procedure and qualification records shall be submitted for approval upon receipt of purchase order. Welding shall not be performed prior to purchaser's approval of welding procedure and qualification. All welding shall be done by the metallic shielded arc or the submerged arc welding process. Permanently installed backing strips shall not be used without written approval of purchaser. When used, backing strips shall be the same composition steel as that which they are attached to. 4. Longitudinal seams in cylindrical or conical shells, all seams in spherical shells and built-up heads shall be located to clear openings, their reinforcing pads, and saddlewear plates. Circumferential seams of shell shall be located to clear openings, their reinforcing pads, tray and insulation support rings, and saddle wear plates. When the covering of circumferential seam by reinforcing pad is unavoidable, the seam shall be ground flush and examined prior to welding the reinforcing pad in place. No longitudinal joints shall be allowed within the downcomer area or at any other place where proper visual inspection of the weld is impossible. The minimum size of fillet weld serving as strength weld for internals shall be 1/4 inch. 5. Skirt. Vertical vessels shall be provided with a skirt which shall have an outside diameter equal to the outside diameter of the supported vessel .. The minimum thickness for a skirt shall be 1/4 inch. Skirts shall be provided with a minimum of two 2-inch vent holes located as high as possible 180 degrees apart. Skirts 4 feet in diameter and less shall have one access opening; larger than 4-foot diameter skirts shall have two I8-inch 0.0. access openings reinforced with sleeves. 6. Base rings shall be designed for an allowable bearing pressure on concrete of 625 psi. 7. Anchor bolt chairs or lug rings shall be used where required and in all cases where vessel height exceeds 60 feet. The number of anchor bolts shall be in multiples of 4; a minimum of 8 is preferred. 8. Saddle. Horizontal vessels shall be supported by saddles, preferably by only two whenever possible. Saddles shall be welded to the vessel, except when specifically ordered to be shipped loose. Saddles to be shipped loose shall be fitted to the vessel and matchmarked for field installation. The shop drawing shall bear detailed instruction concerning this.
197 Specification for the Design and Fabrication of Pressure Vessels (continued) When temperature expansion will cause more thao 3/8 inch change in the distance between the saddles, a slide bearing plate shall be used. Where the vessel is supported by concrete saddles 1/4 inch thick, corrosion plate 2 inches wider than the concrete saddle shall be welded to the shell with a continuous weld. The corrosion plate shall be provided with a 1/4 inch vent hole plugged with plastic sealant after the vessel has been pressure tested. 9. Openings of 2 inches and smaller shall be 6000 lb forged steel full or half coupling. Openings 2-1/2 inches and larger shall be flanged. Flanges shall conform to Standard ANSI BI6.5-1973. Flange faces shall be as follows: Raised face.
below rating 600 lb ANSI
Raised face.
rating 600 lb ANSI, pipe size 3 inches and smaller
Ring type joint.
rating 600 lb ANSI, pipe size 4 inches and larger
Ring type joint.
above rating 600 lb ANSI.
Flange-bolt-holes shall straddle the principal centerlines of the vessel. Openings shall be flush with inside of vessel when used as drains or when located so that there would be interference with vessel internals. Internal edges of openings shall be rounded to a minimum radius of 1/8 inch or to a radius equal to one-half of the pipe wall thickness when it is less than 1/4 inch. When the inside diameter of the nozzle neck and the welding neck flange or welding fitting differ by 1/16 inch or more, the part of smaller diameter shall be tapered at a ratio 1:4. Openings shall be reinforced for new and cold, as well as for corroded condition. The plate used for reinforcing pad shall be the same composition steel as that used for the shell or head to which it is connected. Reinforcing pads shall be provided with a" 1/4 inch tapped tell-tale hole located at 90° off the longitudinal axis of vessel. The minimum outside diameter of the reinforcing pad shall be 4 inches plus the outside diameter of the opening's neck. When covers are to be provided for openings according to the purchaser's requisition, manufacturer shall furnish the required gaskets and studs; these shall not be used for testing the vessel. Manway covers shall be provided with davits. Coupling threads must be clean and free from defects after installation. 10. Internals. Trays shall be furnished by tray fabricator and installed by vessel manufacturer. Tray support rings and downcomer bolting bars shall be furnished and installed by vessel manufacturer. The tray fabricator shall submit complete shop details, including installation instructions and packing list, to purchaser for approval and transmittal to vessel fabricator. Trays shall be designed for a uniform live load ·of 10 psf or the weight of water setting, whibhever is greater, and for a concentrated live load of 250 lb. At the design loading the maximum deflection of trays shall not exceed up to 10-foot diameter - 1/8 inch larger than 10-foot diameter - 3/16 inch
198 Specification for the Design and Fabrication of Pressure Vessels (continued) The minimum thickness of internal plateworks and support rings shall not be less than 1/4 inch. Internal carbon steel piping shall be standard weight. Internal flanges shall be ANSI 150-lb slip-on type or fabricated from plate. Carbon steel internal flanges shall be fastened with carbon steel square-head machine bolts and square nuts tack-welded to the flanges to avoid loosening. Removable internals shall be made in sections which can be removed through the manways. Removable internals shall not be provided with corrosion allowance. For openings connected to pump suction, a vortex breaker shall be provided. 11. Appurtenances. Vessels provided with manways, liquid level controls or relief valves 12 feet above grade, shall be equipped with caged ladders and platforms. Ladder and platform lugs shall be shop-welded to the vessel. Where vertical vessels require insulation, fabricator shall furnish and install support rings. Reinforcing rings may also be utilized in supporting insulation. Insulation support rings shall be 1/2 inch less in width than the thickness of insulation and spaced 12 foot-I/2 inch clear starting at the top tangent line. The top ring shall be continuously welded to the head; all other rings may be attached by a I-inch long fillet weld on 12-inch centers. The bottom head of insulated vertical vessel shall be equipped with I/2-inch square nuts welded with their edges to the outside of the head on approximately 12-inch square centers. 12. Fabrication tolerances shall not exceed the limits indicated in the table beginning on page 200.
D. INSPECTION 1. Purchaser reserves the right to inspect the vessel at any time during fabrication to assure that the vessel materials and the workmanship are in accordance with this specification. .
2. The approval of any work by the purchaser's representative and his release of a vessel shall not relieve the manufacturer of any responsibility for carrying out the provisions of this specification. E. MISCELLANEOUS 1. Radiographic examination shall be performed when required by the ASME Code or when determined by the economics of design. 2. The completed vessel shall be provided with a name plate securely attached to the vessel by welding. 3. If the vessel is post-weld heat-treated, no welding is permitted after stress relieving. 4. Removable internals shall be installed after stress relieving. 5. The location of all vessel components openings, seams, internals, etc., of the vessel shall be indicated on the shop drawings by the distance to a common reference line. The reference line shall be permanently marked on the shell. 6. The hydrostatic test pressure shall be maintained for an adequate time to permit a thorough inspection, in any case not less than 30 minutes. 7. Vessels shall not be painted unless specifically stated on order.
199 Specification for the Design and Fabrication of Pressure Vessels (continued) F. PREPARATION FOR SHIPMENT
1. After final hydrostatic test, vessel shall be dried and cleaned thoroughly inside and outside to remove grease, loose scale, rust and dirt. 2. All finished surfaces which are not protected by blind flanges shall be coated with rust preventative. 3. All flanged openings which are not provided with covers shall be protected by suitable steel plates. 4. Threaded openings shall be plugged. 5. For internal parts, suitable supports shall be provided to avoid damage during shipment. 6. Bolts and nuts shall be coated with waterproof lubricant. 7. Vessels shall be clearly identified by painting the order and item n urn ber in a conspicuous location on the vessel. 8. Small parts which are to be shipped loose shall be bagged or boxed and marked with the order and item number of the vessel. 9. Vessel fabricator shall take all necessary precautions in loading by blocking and bracing the vessel and furnishing all necessary material to prevent damages. G. FINAL REPORTS
1. Before the vessel is ready for shipment the manufacturer shall furnish purchaser copies or reproducible transparency each of the following reports: a. Manufacturer's data report. b. Shop dra wings showing the vessel and dimensions "as built". c. Photostatic copies of recording charts showing pressure during hydrostatic test. d. Photostatic copies of recording charts showing temperature during post-weld heat treatment. e. Rubbing of name plate. H. GUARANTEE
Manufacturer guarantees that the vessel fulfills all conditions as stated in this Specification and that it is free from fault in design, workmanship and materiaL Should any defect develop during the first year of operation, the manufacturer agrees to make all necessary alterations, repairs and replacements free of charge.
200
VESSEL FABRICATION TOLERANCES The dimensional tolerances in this table - unless otherwise noted - are based on practice widely followed by users and manufacturers of pressure vessels. All tolerances are inches, unless otherwise indicated. Tolerances not listed in this table shall be held within a practical limit.
Base Ring a. Flatness b. Out of level
+ 1/16 + 1/8
Clips, Brackets c. Distance to the reference line
+
1/4
d. Deviation circumferentially measured + 1/4 at the joint of structure + Distance between two adjacent clips. 1/16 Manway e. Distance from the face of flange or centerline of man way to reference line, vessel support lug, bottom of saddle, centerline of vessel, whichever is + 1/2 applicable f. Deviation circumferentially measured + 1/2 on the outer surface of vessel g. Projection; shortest distance from outside surface of vessel to the face of manway
+ 1/2
h. Deviation from horizontal, vertical or the intended position in any direction.
+ 10
i. Deviation of bolt holes in any direction. Nozzle, Coupling which are not to be connected to piping. ....
_...'
+ 1/4
The tolerances for manways shall be applied. Nozzle, Coupling which are to be connected to piping. Distance from the face of flange or centerline of opening to reference line, vessel support lug, bottom of saddle, centerline of vessel, whichever is + 1/4 applicable. f. Deviation circumferentially measured + 1/4 on the outer surface of vessel
g. Projection; shortest distance from outside surface of vessel to the face of opening.
+ 1/4
201 VESSEL FABRICATION TOLERANCES (continued) Nozzles, (continued)
~ ill:=:::l ~11Fl h
h. Deviation from horizontal, vertical or the intended position in any direction. . . . . . . . . . . . + 1/2 0 i. Deviation of bolt holes in any direction. . . . . . . . . . . .
+ 1/8
Nozzles, Couplings used for level gage, level control, etc. Distance between centerline of openings . . . . . . . . . . . .
+ 1/16
Saddle k. Distance centerline of boltholes to reference line . . .'. . . . . . . . k. Distance centerline of boltholes to centerline of shell . . . . . . . . .
+ 1/8 ::t 1/8
l. Distance between bolt holes in base plate or between boltholes or slots of ::t 1/8 two saddles. . . . . . . . .
m. Transverse tilt of base plate . .
::t 1/32
n. Longitudinal tilt of base plate.
::t 1/8
per Ft. Shell O.
Deviation from verticallity for vessels of up to 30 ft overaU length . . . . . ::t 1/2 for vessels of over 30 ft overall length
±
1/8 per 10ft. max. 1-1/2 p. Vessels for internal pressure. The difference between the maximum and minimum inside diameters at any cross section shall not exceed one percent of the nominal diameter at the cross section. . . . . . . . . . . . . ± 1%
Omax -
0min = p
Deviation from nominal inside diameter as determined by strapping . . ::t 1/32 per Ft. Out of roundness Code UG-80 External pressure. See Code UG-80 Formed Heads, Code UG-81 Tray Installation r. Out of level in any direction.
::t 1/32 per Ft.
Tray Support r. Out of level in any direction.
::t 1/32 per Ft.
202 VESSEL FABRICATION TOLERANCES ( continued) Tray Support (continued)
'L~ wH x
1F4
-+4-
s. Distance between adjacent tray supports . . . . . . . . .
v. Distance to downcomer support.
+ + + +
w. Tilt for any width of support ring.
+ 1/16
t. Distance to reference line . . . s. Distance to seal pan . . . . . .
1/8 1/4 1/8 1/8
Weir Plate y. Height . . .
+ 1/16 + 1/8
z. Distance to inside of vessel wall
:t 1/4
x. Out of level
203 API Specification for
SHOP WELDED TANKS Summary of Major Requirements of API. Standard 12F, Eleventh Edition 1994
SCOPE - This Specification covers material, design, fabrication and testing requirements for vertical, cylindrical, above-ground, shop fabricated, welded, steel storage tanks for oilfield service in standard sizes as tabulated below.
A
MATERIAL Plates shall conform to the following ASTM Standards: A26, A283, C or D, and A285 C. MINIMUM PLATE TIllCKNESS Shell and deck: 3/16 in., Bottom: l;4 in., Sump: 15-6 diam Deck: l;4 in.
n B
c
3fs in.
CONSTRUCTION The bottom of the tank shall be flat or conical; the latter may be skirted or unskirted. Fig. A, B, C. The deck shall be conical. The slope of the bottom and deck cone = 1: 12. WELDING Bottom shell and deck plate joints shall be double-welded butt joints with complete penetration. Fig. D. The bottom and the deck shall be attached to the shell by doublewelded butt joint or 3/16 in filet welds, both inside and outside. Fig. E through K. OPENINGS Tanks shall be furnished with 24 in. x 36 in. extended neck cleanout. API Std. 12F Fig. 4.
D
TESTING The tank will be tested with air 1Yz times the maximum design pressure. PAINTING One coat Primer. TANK DIMENSIONS Nominal Capacity bbl.
90 100 IS 0 200 210 250 300 400 500 500 750 Tolerance
Working Capacity bbl. 72
79 129 166 200 224 266 366 466 479 746 -
Outside Diameter ft. in.
Height ft.
7-11 9- 6 9- 6 12- 0 10- 0 11- 0 12- 0 12- 0 12- 0 15- 6 15- 6
10 12 10 15 15 15 20 25 16 24
±l/g in.
±3/8 in.
8
204
WELDED STEEL TANKS FOR OIL STORAGE API. Standard 650, Ninth Edition, 1993
APPENDIX A - OPTIONAL DESIGN BASIS FOR SMALL TANKS (Summary of major requirements) SCOPE This appendix provides rules for relatively small capacity, field-erected tanks in which the stressed components are limited to a maximum of~ inch nominal thickness, including any corrosion allowance specified by the purchaser.
MATERIALS The most commonly used plate materials of those permitted by this standard: A 283 C, A 285 C, A 36, A 516-55, A 516-60
The plate materials shall be limited to
~
thickness.
WELDED JOINTS The type of joints at various locations shall be: Vertical Joints in Shell Butt joints with complete penetration and complete fusion as attained by double welding or by other means, which will obtain the same quality of joint. Horizontal Joints in Shell Complete penetration and complete fusion butt weld. Bottom Plates Single-welded, full-fillet lap joint, or single-welded butt joint with backing strip.
Roof Plates Single-welded, full-fillet lap joint. Roofplates shall be welded to the top angle of the tank with continuous fillet weld on the top side only. Shell to Bottom Plate Joint Continuous fillet weld laid on each side of the shell plate. The size of each weld shall be the thickness of the thinner plate.
The bottom plates shall project at least 1 inch width beyond the outside edge of the weld attaching the bottom to shell plate. INSPECTION Butt Welds Inspection for quality of welds shall be made by the radiographic method. By agreement between purchaser and manufacturer, the spot radiography may be deleted. Fillet Welds Inspection of fillet welds shall be made by visual inspection.
205
WELDED STEEL TANKS FOR OIL STORAGE API. Standard 650, Ninth Edition, 1993
TESTING Bottom Welds
1.
Air pressure or vacuum shall be applied using soapsuds, linseed oil, or other suitable material for detection of leaks, or
2.
After attachment of at least the lowest shell course, water shall be pumped underneath the bottom and a head of 6 inches shall be maintained inside a temporary dam.
Tank Shell
1.
The tank shall be filled with water, or
2.
Painting all joints on the inside with highly penetrating oil, and examining outside for leakage.
3.
Applying vacuum.
Appendix A -
Optional Design Basis for Small Tanks
Appendix B -
Recommendations for Design and Construction of Foundations for Above Ground Oil Storage Tanks
Appendix C -
External Floating Roofs
Appendix D -
Technical Inquiries
Appendix E -
Seismic Design of Storage Tanks
Appendix F -
Design of Tanks for Small Internal Pressures
Appendix G -
Structurally Supported Aluminum Dome Roofs
Appendix H -
Internal Floating Roofs
Appendix I -
Undertank Leak Detection and Subgrade Protection
Appendix J -
Shop-Assembled Storage Tanks
Appendix K -
Sample Application of the Variable-Design-Point Method to Determine Shell-Plate Thickness
Appendix L -
API Standard 650 Storage Tank Data Sheets
Apprndix M -
Requirements for Tanks Operating at Elevated Temperatures
Appendix N -
Use of New Materials That Are Not Identified
Appendix 0 -
Recommendations for Under-Bottom Connections
Appendix P -
Allowable External Loads on Tank Shell Openings
Appendix S -
Austenitic Stainless Steel Storage Tanks
206
WELDED STEEL TANKS API. Standard 650-APPENDIX A FORMULAS NOTATION CA. = corrosion allowance, in. D = nominal diameter of tank, ft. E = joint efficiency, 0.85 when spot radiographed 0.70 when not radiographed 0 = specific gravity of liquid to be stored, but in no case less than 1.0
H = design liquid level, ft. t = minimum required plate thickness, in. R = radius of curvature of roof, ft. = angle of cone elements with horizontal, deg.
e
(2.6) (D) (H-O (0) + C.A. (E) (21,000) but in no case less than the following: t
D
...
SHELL
Plate Mean diameter of tank thickness feet inches Smaller than 50 ......................................... ..... 3h 6 50 to 120, excl. ................................................ 14 120 to 200, incl. .............................................. 5/16 Over 200 ......................................................... 3/g t=
SELF-SUPPORTING CONE ROOF
=
400
SIll
e
but not less than 3/16 in.
Maximum t = Yz in. 9: 12 slope Maximum e = 37 deg. Minimum e = 9 deg. 28 min. 2: 12 slope t = RI
SELF-SUPPORTING DOME AND UMBRELLA ROOF
n.
200 but not less than 3/16 in.
Maximum t = Yz in. R = radius of curvature of roof, in feet Maximum R = 0.8 D (unless otherwise specified by the purchaser. Maximum R = l.2D The cross-sectional area of the top angle plus the participating area ofthe shell and roof plate shall be equal or exceed the following: For Self-Supporting Cone Roofs:
For Self-Supporting Dome and Umbrella Roofs:
D2 DR 3,000 sin e 1,500 The participating area shall be determined using Figure F -1 of this Standard. BOTTOM
All bottom plates shall have a minimum nominal thickness of 14 in.
207
WELDED STEEL TANKS FOR OIL STORAGE API. Standard 650, Ninth Edition 1993
APPENDIX J - SHOP-ASSEMBLED STORAGE TANKS (Summary of major requirements) SCOPE This appendix provides design and fabrication requirements for vertical storage tanks in sizes that permit complete shop assembly and delivery to the installation site in one piece. Storage tanks designed on this basis are not to exceed 20 feet in diameter. MATERIALS The most commonly used plate materials of those permitted by this standard: A 36, A 283 C, A 285 C, A 516-55, A 516-60 WELDED JOINTS As described in Appendix A (see preceeding page) with the following modifications: Lap-welded joints in bottoms are not permissible. All shell joints shall be full penetration, butt-welded without the use of backup bars. Top angles shall not be required for flanged roof tanks. Joints in bottom plates shall be full penetrations butt-welded. Flat bottoms shall be attached to the shell by continuous fillet weld laid on each side of the shell plate. BOTTOM DESIGN All bottom plate shall have a minimum thickness of '14 inch. Bottoms may be flat or flat-flanged. Flat bottoms shall project at least 1 inch beyond the outside diameter of weld attaching the bottom shell. SHELL DESIGN Shell plate thickness shall be designed with the formula: (for notations see Appendix A on the preceeding page.) t
= (2.6) (D) (H-l) (G) + C A (E) (21,000)
. .
but in no case shall the nominal thickness be less than: Nominal Tank Nominal Plate Diameter (feet) Thickness (inches) Up to 10.5, incl .................................... 3~6 Over 10.5.............................................. '14 ROOF DESIGN Roofs shall be self supporting cone or dome and umbrella roofs. See Appendix A for design formulas. TESTING Apply 2 to 3 pounds per square inch internal pressure. For tanks with a diameter of 12 feet or less, a maximum pressure of 5 psig shall be used.
208
Summary of Major Requirements of
PIPING CODES PIPE WALL THICKNESS AND ALLOWABLE PRESSURE
CODE & SCOPE
FORMULAS Straight Pipe Under Internal Pressure
ANSI B31.1 -1998 POWER PIPING This Code describes minimum requirements for the design. materials, fabrication, erection, test. and inspection of power and auxiliary service piping systems for electric generation atations, industrial and institutional plants. central and district heating systems. except as limited by Para. 100.1.3. These systems are not limited by plant or other property lines unless they are specifically limited in Para. 100.1.
t
=
t
=
P =
PD() 2(SE + Py)
+A
Pd + 2SEA + 2J:!.PA 2(SE + Py P) 2SE(tm -A) D() - 2y(tm - A)
2SE(tm -A) P = d - 2y(t - A) + 2tl/1 m V ALUES OF S, 1000 psi. For materials ASTM A53B and AI06B For metal temperatures not exceeding Deg. F. -20 to 650 700 750 800 15.0 14.4 13.0 10.8 External Pressure For determining wall thickness and stiffening requirements, the procedures outlined in Paras. UG-28, 29 and 30, Section VIII, Division 2 of the ASME Boiler and Pressure Vessel Code shall be followed.
USAS B31.2-1968 FUEL GAS PIPING This Code covers the design, fabrication, installation and testing of piping systems for fuel gases such as natural gas, manufactured gas, liquefied petroleum gas (LPG) - air mixtures above the upper combustible limit, liquetied petroleum gas (LPG) in the gaseous phase, or mixtures of these gases.
ANSI B31.3-1999 CHENnCALPLANTAND PETROLEUM REFINERY PIPING (a) This Code prescribes requirements for the materials, design. fabrication. assembly, erection, examination. inspection, and testing of piping systems subject to pressure or vacuum. (b) This Code applies to piping systems handling all tluids, including fluidized solids, and to all types of service . including raw, intermediate and finished chemicals, oil and other petroleum products, gas, steam, air. water, and refrigerants. except as provided in 300.1.2 or 300.1.3. Only Category D and M fluid services as defined in 300.2 are segregated for special consideration.
Internal Pressure tl/1
=t+A
P = 2SEt D
t =
PD 2SE
(see notes 1, 3, 4, 5, 6 & 8) VALVES OF S, 1000 psi. For materials ASTM A53B and AI06B For metal temperatures not exceeding Deg. F. -20 to 100 200 300 400 450 20.00 19.10 18.15 17.25 16.80 Internal Pressure 1m
=t+c
t
= 2[SE
Pd P (I
Y) J
PD t = 2(SE + PY) (see notes 1, 7 & 8) V ALVES OF S, 1000 psi. For materials ASTM A53B and AI06B For metal temperatures not exceeding Deg. F. -20 to 100 200 300 400 500 1.gtg 20.00 20.0 20.0 20.0 18.9 External Pressure For determining wall thickness and stiffening requirements the procedures outlined in Paras. UG-28, 29 and 30, Section VIII, Div. I of the ASME Boiler and Pressure Vessel Code shall be followed.
209 Summary of Major Requirements of
PIPING CODES (Continued from facing page) NOTATION
NOTES
A = an additional thickness in inches to compensate for material removed in threading, grooving, etc., and to provide for mechanical strength, corrosion and erosion. Centrifugally cast 0.14 in. Statically cast 0.18 in. the sum in inches of the mechanical allowances (thread or groove depth) plus corrosion and erosion allowance.
c
=
d
= inside diameter of the pipe in corroded conditions, inches.
D& Do= outside diameter of the pipe, inches E
=
efficiency factor of welded joint in pipe (see applicable code) For seamless pipe E = 2.0.
F = for cast iron pipe casting quality factor F shall be used in place of E. P = internal design pressure, or maximum
1. The minimum thickness for the pipe selected, considering manufacturer's minus tolerance, shall not be less than tm . The minus tolerance for seamless steel pipe is 12.5% of the nominal pipe wall thickness. 2. Where steel pipe is threaded and used for steam service at pressure above 250 psi, or for water service above 100 psi with water temperature above 200 oF, the pipe shall be seamless, having the minimum ultimate tensile strength of 48,000 psi and weight at least equal to sch. 80 of ANSI B36.20. (Code ANSI B31.1, Para. 104.1.2C.l) 3. Piping systems installed in open easements which are accessible to the general public or to individuals other than the owner of the piping system or his employee or agent, shall be designed in accordance with ANSI B31.8. (Code ANSI B31.02, Para. 201.1)
allowable working pressure, psig.
S
=
maximum allowable stress in material due to internal pressure and the design temperature, psig.
t
=
thickness of pipe required for pressure, inches
tm
=
minimum thickness of pipe in inches required for pressure and to compensate for material removed for threading, grooving, etc., and to provide for mechanical strength, corrosion and erosion.
y&Y
=
coefficients as tabulated below VALUES OF y & y
900 1 Temperature and F below 950 1000 1050 FerriticSteels 0.40.50.7 0.7 Austenitic Steels 0.4 0.4 0.4 0.4
1250 and llOO above 0.7 0.7 0.5 0.7
Note:For intermediate temperatures the values may be interpolated. For nonferrous materials and cast iron, y equals 0.4. IFor pipe with a D,/tm ratio less than 6, the value of y for ferritic and austenitic steels designed for temperatures of 900 0 F and below shall be taken
as: y= _d_ d + Do
4. When not specifically required by a gas using process or equipment, the maximum working pressure for piping systems installed in buildings intended for human use and occupancy shall not exceed 20 psig. {Code ANSI B31.2, Para. 201.2.1) 5. Every piping system, regardless of anticipated service conditions, shall have a design pressure of at least 10 psig between the temperatures of minus 20 0 F and 250 oF. (Code ANSI B31.2, Para. 201.2.2,b) 6. Where the minimum wall thickness is in excess of 0.10 of the nominal diameter, the piping system shall meet the requirements of ANSI B31.3. (Code ANSI B31.2, Para. 203) 7. Pipe with t equal to or greater than D/6, or P/SE greater than 0.385, requires special consideration, taking into account design and material factors such as theory of failure, fatigue and thermal stresses. 8. Pipe bends shall meet the flattening limitations of the applicable Code.
210 Summary of Major Requirements of
PIPING CODES PIPE WALL THICKNESS AND ALLOW ABLE PRESSURE CODE & SCOPE
FORMULAS Straight Pipe Under Internal Pressure
ANSI B3I.4-1998 LIQUID TRANSPORTATION SYSTEMS
=t+A PiD t = 2S ' where
til
This Code prescribes requirements for the design, materials, construction, assembly, inspection. and testing of piping transporting liquids such as crude oil. condensate, natural S = allowable stress value, psi. For pipe gasoline, natural gas liquids, liquidied petromaterials ASTM A 53 B and A 106 leum gas, liquid alcohol, liquid anhydrous B, S = 25,200 psi. at -20 o F to 250°F. ammonia, and liquid petroleum products between producers' lease facilities, tank farms, t = pressure design wall thickness inches (See notes 1, 2). naatural gas processing plants, refineries, stations, terminals, and other delivery and receiving points.
ANSI B31.5-2000 REFRIGERATION PIPING
Internal Pressure t/ll
This Code provides minimum requirements for the materials, design, fabrication, assembly, erection, test, and inspection of refrigerant and secondary coolant piping for temperatures as low as 320°F (whether erected on the premises or factory assembled) except as specifically excluded in the following paragraphs. Users are advised that other piping Code Sections may provide requirements for refrigeration piping in their respectivejurisdictions. This Code shall not apply to:
1
(b) water pi ping;
S
=
2St
Do - 2yt
or
1
=
Pd 2 (S + Py - P)
-=-:-:--..::.......:,~-,...,
, where
maximum allowable stress, psi. For pipe materials ASTM A 53 B and A 106 B, S = 15,000 psi, at 1OOoF to 400 oF.
t = pressure design wall thickness, inches. (See notes 1, 2).
External Pressure The pressure design thickness, t, shall be determined in accordance with Code, Para. 504.1.3.
ANSI B3I.8-1999 GAS TRANSMISSION AND DISTRIBUTING PIPING SYSTEMS This Code covers the design, fabrication, installation, inspection, testing, and the safety aspects of operation and maintenance of gas transmission and distribution systems, including gas pipelines, gas compressor stations, gas metering and regulating stations, gas mains, and service lines up to the outlet of customer's meter set assembly. Included within the scope of this Code are gas storage equipment of the closed type, fabricated or forged from pipe or fabricated from pipe and fittings and gas storage lines.
PD,)
= 2 (S + Py)
P =
(a) any self-contained or unit systems subject to the requirements of Underwriters' Laboratories or other nationally recognized testing laboratory; (c) piping designed for external or internal gage pressure not exceeding 15 psi (103 kPa) regardless of size.
=t+c
Steel Pipe Design Formula Internal Pressure
P =2S1 x Fx Ex T where D ' S = specified minimum yield strength, psi. For pipe materials ASTM A 53 Band A 106 B, S - 35,000 psi. t
= nominal wall thickness, inches (See notes 1,2,3,4 & 5).
211
Summary of Major Requirements of
PIPING CODES (Continued from facing page) NOTATION: A = Sum of allowance, inches for threading and grooving as required under Code, Para. 402.4.2, corrosion as required under Code, Para 402.4.2, and increase in wall thickness if used as protective measure under Code Para. 402.1.
c
For internal pressure, the sum of allowances in inches thread and groove depth, manufacturers' minus tolerance, plus corrosion and erosion allowance. For external pressure, the sum in inches of corrosion and erosion allowances, plus manufacturers' minus tolerance.
T = Temperature Derating Factor for Steel Pipe. Temperature Degrees Fahrenheit 250 F or less 300 F 350 F 400 F 450 F
Factor T 1.000 0.967 0.933 0.900 0.867
Note: Interpolate for intermediate values. y = Coefficient for materials indicated:
For nonferrous materials, ferritic steels and austenitic steels y = 0.4.
Dr in range of 4-6, use
If
_
d
d = Inside diameter of pipe, inches.
y - d+ Do
D&
for ductile materials.
Do = Outside diameter of pipe, inches.
For brittle materials use y = 0.0.
E = Longitudinal joint factor obtained from
Code, table 841.12. For seamless pipe, E= 1.0. F = Values of Design Factor F
Construction Type Design Factor F (See Code 841.114A) Type Type Type Type
-
A B C D
0.72 0.60 0.50 0.40
P&
Pi = Internal design pressure, psig.
S
As described at the formulas, and in applicable Code, psi.
tt
As described at the formulas, inches.
tn
Nominal wall thickness of straight part of steel pipe satisfying requirements for pressure and allowances.
tmj=
Minimum required thickness, inches, satisfying requirements for design pressure and mechanical, corrosion and erosion allowances.
NOTES: 1. In selection of pipe the manufacturers' minus tolerance shall be taken into consideration. The minus tolerance for seamless steel pipes is 12.5% of the nominal wall thickness. This tolerance may be used also when specification is not available. 2. Pipe bends shall meet the flattening limitations of the applicable Code. 3. Classification of Locations. In Code B31.8, Para. 840.2, four classes are described as a basis for prescribing the types of construction. 4. Limitation by Pipe Design Factors, Code B3 1. 8, Para. 841. 111-114. 5. Least Nominal Wall Thickness, Code B31.8, Table 841.141. The formulas and regulations are extracted from the American National Standard Code for Pressure Piping with the permission of the publisher, The American Society of Mechanical Engineers.
212 NOTES
213
RECTANGULAR
TANKS
UNDER HYDROSTATIC PRESSURE
:;'lat-walled tanks due to their mechanically disadvantageous shape are used for low lydrostatic pressure only. The quantity of material required for rectangular tanks is righer than for cylindrical vessels of the same capacity. However, sometimes the applicaion of rectangular tanks is preferable because of their easy fabrication and the good ltilization of space. MAXIMUM SIZE
Unstiffened tanks may be not larger than 30 cu. ft. and tanks with stiffenings, 140 cubic feet capacity. ::;or larger tanks, the use of stay rods is advisable for economic reasons. ~ATIO OF SIDES [f all sides are equal, the length of one side: B = where V Preferable ratio: Longer side: 1.5 B; Shorter side: 0.667 B
W;
= volume
cu. ft.
DESIGN
rhe formulas on the following pages are based on maximum allowable deflection: .1, = ti2, where ta denotes the thickness of side-plate.
Values of a and {J R aho,"[ . H ofl H 0.25 Constant, {J 0.024 Constant, a 0.00027
0.286 0.031 0.00046
R allo,"[ . H of7 H Constant, {J Constant, a
1.5 0.26 0.043
H
=
1.0 0.16 0.022
height of tank
L
=
0.333 0.041 0.00083 2.0 0.34 0.060
length of tank
0.4 0.056 0.0016 2.5 0.38 0.070
3.0 0.43 0.078
0.5 0.080 0.0035 3.5 0.47 0.086
0.667 0.116 0.0083 4.0 0.49 0.091
maximum distance between supports
WELDING OF PLATE EDGES Some preferable welded joints of plate edges:
LL~ [he stiffenings may be attached to the tank wall either by intermittent or continuous welding and may be placed inside or outside. ~IBLIOGRAPHY
)ther design methods are offered in the following papers: lojtaszak, I. A.: Stress and Deflection of Rectangular Plates, ASME Paper A-71, Journal Appl. lIecl•. , Vol. 3 No.2, 1936. rimoshenko, S. and S. Woinowsky-Krieger: {ill Book Company, 1959.
"Theory of Plates and Shells", 2nd edition, McGraw-
:anti K. Mahajan: "Design of Procas Equipment.", Pressure Vessel Handbook Publishing. Inc. 1990.
214 RECTANGULAR TANKS UNDER HYDROSTATIC PRESSURE WITH TOP-EDGE STIFFENING NOTATION a
E G
= factor depending on ratio of length and height of tank, H/L (See Table) = modulus of elasticity, psi.; 30,000,000 for carbon steel = specific gravity of liquid
H = height of tank, in I = moment of inertia, in.4 I = maximum distance between supports, inches L = length of tank, nches R = reaction with subscripts indicating the location, lb./in. S = stress value of plate, psi. as tabulated in Code, Tables ues - 23 t = required plate thickness, inches ta = actual plate thickness, inches tb = required plate thickness for bottom, inches t8 = actual thickness of bottom, inches w = load perunit of length lb./in. y = deflection of plate, inches
REQUIRED PLATE THICKNESS
L
t = B
'\ IPHO.036G V S
Thickness, t may be used also for the bottom plate if its entire surface is supported. Thickness, t shall be increased in corrosive service. Maximum deflection of plate: _ aO.036GHL4
L
Ed
max -
I - - - - . -..----~-~-----------
STIFFENING FRAME
w=
R1 = O.3w
0.036 GH2
R2
O.7w Minimum required moment of inertia for top-edge stiffening:
2
=
lmin=
BOTTOM PLATE WHEN SUPPORTED BY BEAMS t b
w
1:
:r
18
!. S 1.254 yO.036 G H ..
Maximum spacing of supports for a given thickness of bottom:
215 RECTANGULAR TANKS EXAMPL.ES
DESIGN DATA
Capacity of the tank: 600 gallon = 80 Content: water; G = 1 The side of a cube-shaped tank for the Preferred proportion of sides: L = 4.31 x 1.5 = 6.47 ft. = H = 4.31 x .667 = 2.87 ft. = Width of the tank 4.31 ft. = S = 15,700, using SA 285 C material Corrosion allowance: 1/16 in. H/L = 34178 = 0.43; fJ = 0.063
cu. ft. approximately 3
designed capacity:
V80 = 4.31 ft.
78 inches 34 inches 52 inches
REQUIRED PLATE THICKNESS
'\ / 0.063
t = 78
V
X
·34 '>( 10.036 15,700
+ 0.0625
X
1 = 0 1729 . . m.
corr. allow = 1/4 in.
STIFFENING FRAME
0.036
1
X
X
342 =
20.808 lbiin
W
2 I
_ = mm
R 1 - = 0.3 R2 = 0.6
X X
20.808 = 6.24 lb/in 20.808 = 14.57 lh/in
6.24 X 784 = 0.214 in4 192 x 30.000,000 x 0.1875
1-3/4 x 1-3/4 x 3/16 (.18 in4) satisfactory for stiffening at the top of the tank
BOTTOM PLATE WHEN SUPPORTED BY BEAMS if number of beams = 3; 1 = 39 inches Ib
39 = ----"-~~~= = 0.275 /15,700 1.254
in.,
0.036x 1x34
Or using the plate thicknessO.1875 as calculated above, the maximum spacing for supports: I = 1.254
Using 4 beams, .1
x
0.1875
-= 26 in.
Jo0.036 15,700 x 1 x 34
= 26.63 in.
216
RECTANGULAR TANKS WITH VERTICAL STIFFENINGS NOTATION
p = E ]{
I G
I L S w
Z
= = = = = = = = = =
Factor depending on ratio of length and height, 1111 (See Table on page 213) modulus of elasticity, ~i. height of tank inches moment ofinenia, in4 specific gravity of liquid the maximum distance between stiffenings on the longer or shorter side of the tank, inches. length of tank, inches stress value of plate, psi. required plate thickness, inches I(J = actual plate thickness, inches 10ad,lbs. section modulus, in 3
I---L-J
I.
L
REQUIRED PLATE THICKNESS
t = I
V
PH 0.036 G S
LOADS, lb/in
- O.036GH2 W2
STIFFENING FRAME
Required section modulus of vertical stiffening 3
0.0642. 0.036 GH 1 z=------S
Minimum required moment of inertia for top-edge stiffening:
RJ L" I min = 192 E I(J
217
RECTANGULAR TANKS WITH VERTICAL STIFFENINGS EXAMPLES DESIGN DATA E = 30,000,00 psi
L
=
H= B= S = I =
78 in. 34 in. 52 in. J 5,700 psi 26 in.
Content: Water G= 1 34 HII= 26= 1.31:jJ=0.22
REQUIRED PLATE THICKNESS
t
=26 X /.22 X34 XO.036 XI =01077' 15700 . tn. ,
+ corr. allow
0.0625 in. 0.1702 in.
+ use 3116 in. plate STIFFENING FRAME
X 1 X 34 3 X 26 = 0 1504' 3 Zmm. = 0.0642 X 0.036 15700 . m. , 2 X 2 X 31J 6 (.19 in. 3) satisfactory for vertical stiffening
w=
0.036 X 1 X 342 2
'min
_ 6.24 X 78 in.4 _ 0 "'2' 4 -192 X 30,000,000 X 0.125 - .J m.
20.81b.lin.
Rl = 0.3 X 20.8 - 6.24Ib.lin.
218
RECfANGULAR TANKS Under Hydrostatic Pressure WITH HORIZONTAL STIFFENINGS NOTATION E G H I
L p R S
t ta w
= modulus of elasticity, psi.; 30,000,000 for carbon steel = specific gravity of liquid = height of tank, in = moment of inertia, in.4 = length of tank,inches = pressure of liquid, psi. = reaction with subscripts indicating the location, lb./in. = stress value of plate, psi. = required plate thickness, inches = actual plate thickness, inches = load per unit of length lb./in. H
I. SPACING OF STIFFENINGS
L
.1 HI = 0.6H
REQUIRED PLATE THICKNESS
n
H2 = O.4H
..
0.036 GH S
/
= 0. 311 V
t
w = 0.036 GH 2 LOAD Ib./in.
2
RJ
= 0.06
W
R2
= 0.3 w
R2
= 0.64 w
Minimum required moment of inertia for top-edge stiffening MINIMUM MOMENT OF INERTIA FOR STIFFENING
I I
-
RI L
4
192 E ta
Minimum required moment of inertia for intermediate stiffening
=
I 2
R2
L4 192 E ta I
219
RECTANGULAR TANKS WITH INTERMEDIATE HORIZONTAL STIFFENINGS EXAMPLES DESIGN DATA: Designed capacity = 1,000 gallon = 134 cu. ft. (approx.) Content: water s= 15,700 psi, using SA 285 Cmaterial Corrosion allowance = lit 6 in. The side of a cube-shaped tank for the designed capacity: Preferred proportion of sides: width = 0.667 X 5.12 = 3.41 ft; approx. 42 inches length = 1.500 X 5.12 = 7.68 ft; approx. 92 inches height = 5.12 ft; approx. 60 inches
3
134 = 5.12 ft.
For height 60 inches, intermediate stiffening is required.
SPACING OF STIFFENINGS: HI = 0.6
H= 36 in.
H2 = O.4H= 24 in.
REQUIRED PLATE TIDCKNESS: =01X60jO.036XI560 =02111' 15,700 . m.
t.J
+ corr. allow 0.0625 in. 0.2736 in.
LOADS: 2
/. w = 0.036 X 21 X 60 = 64 .81b .m. R2 =0.3w= 19.441b'/in.
RI =0.06w=3.891b'/in.
MINIMUM MOMENT OF INERTIA FORSTIFFENINGS: 4
3.89 X 92 -04690' 4 II - 192 X 30,000,000 X 0.25 - . m. _
19.44 X 92 4
_
12 - 192 X 30,000,000 X 0.25 - 0.
96 . 4 7 m.
220 TIE
ROD
S U p.p 0 R T
FOR RECTANGULAR TANKS Under Hydrostatic Pressure To avoid the use of heavy stiffenings, the sides of large tanks may be supported most economically by tie rods. NOTATIONS A Req uired cross sectional area of a ~ tie rod, sq. in. a horizontal pitch, in. b vertical pitch, in. 'hI 2 ~ G = specific gravity of liquid f P pressure of liquid, lb. Ib ~ S = stress value of rod material, psi. t = required plate thickness, in. Sp = stress value of plate material, psi
..
-+
+-
REQUIRED PLATE THICKNESS
when a:!!b
LOAD ON TIE ROD
EXAMPLE DESIGN DATA Length=30 ft., width=12 ft., height=15 ft.
a
hJ = 60 in
G = I S = 20,000 psi. S = 20,000 psi. Sp = 20,000 psi
h2 = 120 in
= 0.7
t
x 60
V
0.036 x 1 x 120 20,000
A = 15,552 = 0.778 sq. in. 2 20,000 PI
1
= It/> rods
=abO.036Gh l =6Ox60x0.036x60 = 7,776 lb.
A =
7,776 - 0.389 sq. in. = 3/4 ¢> rods
20,000
V
P=ab 0.036 Gh
REQUIRED CROSS SECTIONAL AREA OF TIE ROD
= 60 in. b = 60 in.
t = 0.7b
• ...
0.036 G h Sp
221
CORROSION Vessels or parts of vessels subject to thinning by corrosion, erosion or mechanical abrasion shall have provision made for the desired life of the vessel by suitable increase in the thickness of the material over that determined by the design formulas, or by using some other suitable method for protection (Code UG-25b). The Code does not prescribe the magnitude of corrosion allowance except for vessels with a required minimum thickness of less than 0.25 in. that are to be used in steam, water or compressed air service, shall be provided with corrosion allowance of not less than one-sixth of the required minimum thickness. The sum of the required minimum thickness and corrosion allowance need not exceed 1/4 in. This requirement does not apply to vessel parts designed with no x-ray examination or seamless vessel parts designed with 0.85 joint efficiency. (Code UCS-25). For other vessels when the rate of corrosion is predictable, the desired life of the vessel will determine the corrosion allowance and if the effect of the corrosion is indeterminated, the judgment of the designer. A corrosion rate of 5 mils per year (lI16 in. = 12 years) is usually satisfactory for vessels and piping. The desired life time of a vessel is an economical question. Major vessels are usually designed for longer (15-20 years) operating life time, while minor vesse1s for shorter time (8-10 years). The corrosion allowance need not be the same thickness for all parts of the vessel if different rates of attack are expected for the various parts (Code UG-25 c). There are several different methods for measuring corrosion. The simplest way is the use ofteltale holes (Code UG-25 e) or corrosion gauges. Vessels subject to corrosion shall be supplied with drain-opening (Code UG-25 0. All pressure vessels subject to iinternal corrosion, erosion, or mechanical abrasion shall be provided with inspection opening (Code UG-46). To eliminate corrosion, corrosion resistant materials are used as lining only, or for the entire thickness of the vessel wall. The rules of lining are outlined in the Code in Part UCL, Apendix F and Par. UG-26. The vessel can be protected against mechanical abrasion by plate pads which are welded or fastened by other means to the exposed area of the vessel. In vessels where corrosion occurs, all gaps and narrow pockets shall be avoided by joining parts to the vessel wall with continuous weld. Internal heads may be subject to corrosion, erosion or abrasion on both sides.
222 SELECTION OF CORROSION RESISTANT MATERIALS
The tabular information on the following pages is an attempt to present a summarized analysis of existing test data. It is necessarily brief and, while the utmost precautions have been taken in its preparation, it should not be considered as infallible or applicable under all conditions. Rather, it should be looked upon as a convenient tool for use in determining the degree of safety which various materials are capable of providing and in narrowing down the field of investigation required for final selection. This particularly applies where failure due to corrosion may produce a hazardous situation or result in expensive down-time. Footnotes have been generously used to explain and further clarify information contained in this table. It is most important that these notes be carefully read when using the table. In rating materials, the letter "A" has been used to indicate materials which are generally recognized as satisfactory for use under the conditions given. The letter "F" signifies materials which are somewhat less desirable but which may be used where a low rate of corrosion is permiSSible or where cost considerations justify the use of a less resistant material. Materials rated under the letter "c" may be satisfactory under certain conditions. Caution should be exercised in the use of materials in this classification unless specific information is available on the corroding medium and previous experience justifies their use for the service intended. The letter "X" has been used to indicate materials generally recognized as not acceptable for the service. Information on metals has been obtained from the International Nickel Company, the Dow Chemical Company, the Crane Company, the Haynes-Stellite Company, "Corrosion Resistance of Metals and Alloys" by McKay & Worthington, "Metals and Alloys Data Book" by Samuel L. White, "Chemical and Metallurgical Engineering" and "The Chemical Engineers' Handbook," Third Edition by McGraw-Hill. NOTES - GASKET MATERIALS I.
The generally accepted temperature limit for a good grade compressed asbestos sheet, also called asbestos composition sheet, is 7500F. However, some grades are successfully used at considerable higher temperatures. This type of sheet is used for smooth flanges. For rough flanges, gaskets cut from asbestos-metallic sheet or formed by folding asbestos-metallic cloth are preferred. The latter ,and gaskets cut from felted asbestos sheet, are indicated for flanges when bolt pressures are necessarily limited because of the type of flange meterial.
II. Data from the Pfaulder Company are given from the special point of view of the suitability of the gasket material for use with glass-lined steel equipment. III. Data in this column apply specifically to Silastic 181, a special silicone rubber for use in gasketing produced by Dow-Corning Corporation. IV. Fiberglas fabric filled with Silastic silicone rubber (polysiloxane elastomer) has a usable compressibility of about 20 per cent and shows the chemical resistance cited here over the temperature range from -85 to 3920F. For Fiberglas fabric filled with chemically resistant synthetic rubber, the temperature range is approximately -40 to 2570F. Both the silicone rubber and the ordinary synthetic rubber are available as gasket materials in which the reinforcing fabric is a metal cloth (brass, aluminum, iron, stainless steel). The chemical properties of these constructions are the same as those given here for the Fiberglas-reinforced material, with the properties of the metal in the cloth imposed upon them. The metal-cloth construction for increased mechanical strength and electrical conductivity.
223 V. Teflon is the DuPont trade-name for polymerized tetrafluorethylene. It is completely inert in the presence of all known chemicals. It is not affected by any known solvent or combination of solvents. It is chemically stable up to 6170F but, being a plastic, it is not recommended for gasket applications above 3920F or for high pressures unless confined in a tongue-and-groove or similar joint. Sources of Data: A - Armstrong Cork Co.; C - Connecticut Hard Rubber Co.; D - Dow-Corning Corp.; E - E. I. DuPont de Nemours & Co.; J - Johns-Manville Corp.; P - The Pfaudler Co.; S - Stanco Distributors, Inc.; U - United States Rubber Co. Information on gasket materials compiled by McGraw-Hili, "Chemical Engineers Handbook," Third Edition.
224 CHEMICAL RESISTANCE OF METALS Resistance Ratings: A = Good; F = Fair; C = Caution- depends on conditions; X = Not recommended.
Caution: Do not use table without reading footnotes and text.
u
rJ:i rJ:i
N
. -; '" 'u.. '".." e c: 0
Ch~mical
U
rii" ~
c:
"c:0
~
.. ·s
Q,o
~
~ Q,o
e0
" u
;: Z ..5
0
F F F F
A A C
....J
acid. crude................................. C Pure ...................................................... X Vapors................................................. X 150 Ib/sq.in. @ 4(X)·F..........._.......... X Acetic anhydride.................................. C Acetone....................... _.......................... A Acetylene ................................................ A Aluminum chloride .............................. X Aluminum sulfate....................... _....... X Alun1s ....................................................... X Ammonia gas. dry ............................... F ~Ioist .................................................... F Ammonium chloride............................ F Ammonium hydroxide ................ _...... A Ammonium nitrate .............................. F Ammonium phosphate ....................... C Ammonium sulfate.............................. F Aniline. aniline oiL ............................. A Aniline dyes........................................... Barium chloride .................................... Barium hydroxide....................... _....... Hariul11 sulfide ...................................... Beer .......................................................... C Beet sugar liquors ................................ C Benzene. benzoL ................................. A Benzine. petroleum ether. naphtha A Black sulfate liquor............................. A Boric acid ............................................... X Bromine .................................................. X
C C C
F F F
C C C
F A
C X
AI F A A Xe A Xs C X C F A C F A F A A A X A X X A X X A X X X X C A C C A C X X -
-
-
X
C F F A X X
X X
C
-
A A
-
A C
F A
-
A
-
A A F A C
Notes continued on opposite page 1. In absence of oxygen. 0 2. 125 maximum. 3. All percents; 70°. 4. To boiling. 5. 5% room temperature. 6. To 122°. 7. Iron and steel may rust considerably
U
X
In
presence of water and air. 8. HifLh copper al/oys prohibited by Codes; ye low brass acceptable. 9. Haslel/oy "c" recommended to 105°.
-
-
-
-
X
X
A
X
-
A A A A X C C
-
A A F C
-
"ij
"ii
:...>
X
"ij
c:
Q,
:I::
-
c:
Q,o
~
0
Q,o
Q,
~
..= Ac~tic
'3
e::l ::l
C
A A A C C F A C C A A C As
X
-
X
-
A C A A
-
A
X
..lII U
C
F
C
-A A A C C C
8 C A C C A A
C C
c:
~
C A C C A A A C F C
rJ:i rJ:i
rJ:i rJ:i
rJ:i rJ:i
~..
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225 CHEMICAL RESISTANCE OF GASKETS (SEE CHEMICALS ON OPPOSITE PAGE)
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226 CHEMICAL RESISTANCE OF METALS
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227
CHEMICAL RESISTANCE OF GASKETS (SEE CHEMICALS ON OPPOSITE PAGE)
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30. 31. 32. 33. 34.
228
CHEMICAL RESISTANCE OF METALS Resistance Ratings: A = Good; F = Fair; C = Caution - depends on conditions; X = Not recommended.
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229
CHEMICAL RESISTANCE OF GASKETS (SEE CHEMICALS ON OPPOSITE PAGE)
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permissible. 10% - room temperature. HOI. U'lSalisfactory for hot gases. Hastelloy "c" to 158°· Room temperature to 158°. Corrosion increases with increase in concentration as well as temperature. 35. Dilute at room temperature. 36. Attack increases when only partially submerged; fumes very rorrosive. 37. Hastelloy "C" to 212°. 30. 31. 32. 33. 34.
230
CHEMICAL RESISTANCE OF METALS
=
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Resistance Ratings: A Good; F Fair; Caution - depends on conditions; X Not recommended.
(= =
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Notes continued on opposite page 1- In absence of oxygen.
125° maximum. All percents .. 70°. To boiling. 5% room temperature. To 122°. Iron and steel may rust considerably In presence of water and air. 8. Hi"h copper alloys prohibited by Codes .. ye low brass acceptable. 9. Hastelloy "c" recommended to 105°.
2. 3. 4. 5. 6. 7.
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Where color is not important. Do not use with c.p. acid. Room temperature to 212°. Moisture In· hibits attack. Gas .. 70°. To 500°. Hastelloy "c" at room temperature. Room temperature to 158°. At room temperature. W here discoloration is not objectionable. 5% maximum; 150° maximum. Satisfactory vapors to 212°.
-
231
CHEMICAL RESISTANCE OF GASKETS (SEE CHEMICALS ON OPPOSITE PAGE)
Resistance Ratings: Same as facing page
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20. Highly corrosive to nickel alloys at elevated temperatures. Recommendation applies to "dry" gas at ordinary temperatures. 21. 48% - boil at 330°. 22. Room temperature - over 80%. 23· Not for temperatures over 390°F. 24. Up to 140°F. 25. Up to 200°F. 26. Up to 176°F. 27. 10% maximum; boiling. 28. 50%; 320°. 29. Do not use if iron contamination is not
30. 31. 32. 33.
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permissible. 10% - room temperature. Hot. U1zsatisfactory for hot gases. Hastelloy "c" to 158°· Room temperature to 158°. Corrosion increases with increase in concentration as well as temperature. Dilute at room temperature. Attack increases when only partially sub· merged; fumes very corrosive. Hastelloy "c" to 212°.
232
FABRICATING CAPACITIES THE TABLES BELOW ARE FOR DATA OF FABRICATING CAPACITIES OF THE SHOP WHICH HAVE TO BE KNOWN BY THE VESSEL DESIGNER. THE COLUMNS HAVE BEEN LEFT OPEN AND ARE TO BE FILLED IN BY THE USER OF THIS HANDBOOK ACCORDING TO THE FACILITIES OF THE SHOP CONSIDERED. MAXIMUM WIDTH in.
MAXIMUM THICKNESS in.
MINIMUM DIAMETER in.
MAXIMUM SIZE
MINIMUM DIAMETER in.
MINIMUM SIZE
MINIMUM DIAMETER in.
MAXIMUM SIZE
MINIMUM DIAMETER in.
MAXIMUM SIZE
MINIMUM DIAMETER in.
MAXIMUM SIZE
MINIMUM DIAMETER in.
ROLLING PLATES TENSILE STRENGTH OF PLATE psi. NOTE: FOR MATERIAL OF HIGHER STRENGTH THE THICKNESS OR WIDTH OF THE PLATE MUST BE REDUCED IN DIRECT PROPORTION TO THE HIGHER STRENGTH
~ ROLLING ANGLES
~
~ ~ ROLLING BEAMS
ROLLING CHANNELS
LEG IN LEG OUT
LEG IN LEG OUT
~ FLANGES ON ~FLANGES IN
e:::tFLANGES OUT
ROLLING FLAT BAR
~ ON
EDGE
I
233
FABRICATING CAPACITIES NOMINAL PIPE SIZE
MINIMUM RADIUS in.
SCHEDULE
BENDING PIPES
PLATE THICKNESS in.
MINIMUM INSIDE RADIUS in.
PLATE THICKNESS in.
MINIMUM INSIDE RADIUS in.
PLATE THICKNESS in.
MAXIMUM DIAMETER OF HOLE in.
PLATE THICKNESS in.
MAXIMUM DIAMETER OF HOLE in.
BENDING PLATES WITH PRESS BRAKE
PUNCHING HOLES
MINIMUM INSIDE DIAMETER OF VESSEL ACCESSIBLE FOR INSIDE WELDING
inches
TYPES OF WELDINGS AVAILABLE FURNACES FOR STRESS RELIEVING
HEIGHT WIDTH ft. MAX. TEMPERA TU RE
ft. f.
LENGTH
ft.
234
PIPE AND TUBE BENDING * In bending a pipe or tube, the outer part of the bend is stretched and the inner section compressed, and as the result of opposite and unequal stresses, the pipe or tube tends to flatten or collapse. To prevent such distortion, the common practice is to support the wall of the pipe or tube in some manner during the bending operation.
This support may be in the form of a filling material, or,
when a bending machine or fixture is used, an internal mandrel or ball-shaped member may support the inner wall when required.
MINIMUM RADIUS:
The safe minimum radius for a given diameter, material,
and method of bending depends upon the thickness of the pipe waU, it being possible, for example, to bend extra heavy pipe to a smaller radius than pipe of standard weight. As a general rule, wrought iron or steel pipe of standard weight may readily be bent to a radius equal to five or six times the nominal pipe diameter. The minimum radius for standard weight pipe should, as a rule, be three and one-half to four times the diameter. It will be understood, however, that the minimum radius may vary considerably, depending upon the method of bending. Extra heavy pipe may be bent to radii varying from two and one-half times the diameter for smaller sizes to three and one-half to four times the diameter for larger sizes.
R
R
(3 Y2 to 4d)
(2Y2 to 4d)
Standard Pipe
Extra Heavy Pipe MINIMUN( RADIUS
*From Machinery's Handbook, 1969 Industrial Press, Inc. - New York
235
PIPE ENGAGEMENT LENGTH OF THREAD ON PIPE TO MAKE A TIGHT JOINT
t/1~~~ l
C
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t--
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Nominal Pipe Size
Dimension A inches
Nominal Pipe Size
Dimension A inches
1/8
1/4
3-1/2
1-1/16
1/4
3/8
4
1-1/8
3/8
3/8
5
1-1/4
1/2
1/2
6
1-5/16
3/4
9/16
8
1-7/16
11/16
10
1-5/8
1-1/4
11/16
12
1-3/4
1-1/2
11/16
2
3/4
2-1/2
15/16
3
1
~J
~~~
DIMENSIONS DO NOT ALLOW FOR VARIATION IN TAPPING OR THREADING
DRILL SIZES FOR PIPE TAPS Nominal Pipe Size
Tap Drill Size in.
Nominal Pipe Size
Size in.
1/8
11/32
2
2-3/16
1/4
7/16
2-1/2
2-9/16
3/8
19/32
3
3-3/16
1/2
23/32
3-1/2
3-11/16
3/4
15/16
4
4-3/16
1
1-5/32
5
5-5/16
1-1/4
1-1/2
6
6-5/16
1-1/2
1-23/32
Tap
Drill
236 BEND ALLOWANCES For 90 0 Bends in Low-Carbon Steel Metal Thickness (t) in.
1/32
1/16
3/32
1/8
1/4
1/2
0.032 0.050 0.062 0.078 0.090 0.125 0.188 0.250 0.313 0.375 0.437 0.500
0.059 0.087 0.105 0.128 0.146 0.198 0.289 0.382 0.474 0.566 0.658 0.750
0.066 0.101 0.118 0.142 0.160 0.211 0.302 0.395 0.488 0.580 0.672 0.764
0.079 0.114 0.132 0.155 0.173 0.224 0.316 0.409 0.501 0.593 0.685 0.777
0.093 0.129 0.145 0.169 0.187 0.243 0.329 0.424 0.515 0.607 0.699 0.791
0.146 0.168 0.183 0.202 0.217 0.260 0.383 0.476 0.569 0.661 0.752 0.845
0.254 0.276 0.290 0.310 0.324 0.367 0.443 0.519 0.676 0.768 0.860 0.952
Bend Allowance Inches With Inside Radius (r) in.
w=a+b-
bend allowance
w=a+b+c-
w=a+b+c+d-
w=a+b+c+d+e-
(2 x bend allowance) (3 x bend allowance) (4 x bend allowance)
Note: w = developed width (length) of blank, t r = inside radius of bend.
= metal thickness,
EXAMPLE: Carbon steel bar bent at two places. The required length of a 1/4 in. thick bar bent to 90 degrees with 1/4 in inside radius as shown above when the sum of dimensions a, band c equals 12 inches, is 12 - (2 x 0.476) = 11.048 inches MINIMUM RADIUS FOR COLD BENDING: The minimum permissible inside radius of cold bending of metals when bend lines are transverse to the direction of the final rolling, varies in terms of the thickness, t from 1-1/2 t up to 6 t depending on thickness and ductility of material. When bend lines are parallel to the direction of the final rolling the above values may have to be approximately doubled.
237 LENGTH OF STUD BOLTS FOR FLANGES *
.-_______~~==~~--------------------------1-.--------_4~--,_ Height of Heavy Nut (Equals nominal stud diam.) Min. Thickness of Flange
A
/ 2 . Plus tolerance for flange thickness 'Raised Face or Depth of Groove
L
L
1/16" See Note 5.
L = 2A + t + r
---L3.
"t" Minus Tolerance for Stud Length
L---~~~!!Sr.===]fC=::rr:::=-- 4.
"r" Rounding-off
1. Length of the stud bolts do not include the heights of the point. (1.5 times thread pitch) 2. Plus tolerance of fig. thk's. Sizes 18 in. & smaller 0.12 in. Sizes 20 in. and larger 0.19 in. 3. Minus tolera'nce of stud length
For lengths up to 12" incl. 0.06 in. For lengths over 12" to 18" incl. 0.12 in. For lengths over 18" 0.25 in. 4. Rounding-off to the next larger 0.25 in. increment. 5. Gasket thickness for raised face, M & F and T & G flanges 0.12 in. For ring type j oint see table on page 356 and take half of the dimensions shown, since in dimension "A" only half of the gasket thickness is included.
*Extracted from American National Standard: ANSI B 16.5 - 1973 Steel Pipe Flanges and Flanged Fittings.
238
PRESSURE VESSEL DETAILING IN THE PRACTICE THERE ARE SEVERAL DIFFERENT WAYS OF DETAILING PRESSURE VESSELS. BY MAKING THE DRAWINGS ALWAYS WITH THE SAME METHOD, CONSIDERABLE TIME CAN BE SAVED AND ALSO THE POSSIBILITIES OF ERRORS ARE LESS. THE RECOMMENDED METHOD IN THE FOLLOWING PROVED PRACTICAL AND GENERALLY ACCEPTED.
HORIZONTAL VESSELS
,-
,
$-C~-·-·~
End View
Ref. line
&
ELEVATION
Saddle MISCELLANEOUS DETAILS 1
GENERAL SPECIFICATIONS
TITLE BLOCK
A. Select the scale so that all openings, seams, etc., can be shown without making the picture overcrowded or confusing.
B. Show right-end view if necessary only for clarity because of numerous connections, etc., on heads. In this case it is not necessary to show on both views the connections etc., in shell. C. Show the saddles separately, if showing them on the end view would overcrowd the picture. On elevation show only a simple picture of saddle and 1he centerlines. D. Locate davit. E. Locate name plate. F. Locate seams, after everything is in place on elevation. The seams have to clear nozzles, lugs and saddles. G. Show on the elevation and end view a simple picture of openings, internaIs, etc., if a separate detail has to be made for these. H. Dimensioning on the elevation drawmg. All locations shall be shown with tailed dimensions measured from the reference line. The distance from ref. line to be shown for one saddle only. The other saddle shall be located showing the dimension between the anchor bolt holes of the saddles.
END VIEW
I. Two symbolic bolt holes
shown in flanges make clear that the noles are straddling the parallel lines with the principal centerlines of vessel.
239 PRESSURE VESSEL DETAILING (cont.)
VERTICAL VESSELS
I-
I I
~ IJE--------E Elevation
Orien tation
Base
MISCELLANEOUS DETAILS I
rr. General SpecifiCations
Tille Block
A. Select the scale so that all openings, trays, seams, etc., can be shown without making the picture overcrowded or confusing. B. If the vessel diameter is unproportionally small to the length, draw the width of the vessel in a larger scale to have space enough for all details. C. The orientation is not a top view, but a schematic information about the location of nozzles, etc. D. Show the orientation so rotated that the downcomers on the elevation can be shown in their true position.
t 00
- :t.a-Seam Shell No_ 1,3
B.-_l. .....~_
ORIENTATION PLAN
E. Dimensioning. All locations on the elevation drawing shall be shown with tailed dimensions measured from the reference line. F. Locate long seams, after everything is in place on elevation. G. Mark vessel centerlines vi! degrees: 0 0 , 90 0 , 180 0 , 270 0 and use it in the same position on all other orientations.
240 PRESSURE VESSEL DETAILING (cont.)
00
Nozzle on Top or Bottom \
H. It is not necessary to show internals on vessel orientation if their position is clear from detail drawings or otherwise.
N
®
J. Draw separate orientations for showing different internals, lugs, etc. if there is not space enough to show everything on one.
K. For vessels with sections, show 2 tions if necessary, the upper section, the lower section.
Seal Pan Baffle -->---~ Partition t
00
L. Two, symbolic bolt holes shown in flanges make clear that the holes are straddling the lines parallel with the principal centerlines of vessel.
270 0
90 0 Ladder Lugs
--I ...
conical orientaone for one for
L '1
M. If there is a sloping tray, partition plate, coil, etc., in the vessel, show in the orientation the direction of slope.
180 0
00
270 0
Lowest Point of Plate "D"
180 0
ORIENTATIONS
241 PREFERRED LOCATIONS Of Vessel Components and Appurtenances L
A. Anchor bolts straddle principal centerlines of vessel.
B. Skirt access openings above base minimum to clear anchor lugs, maximum 3'-0".
c.
E
I
Skirt vent holes as high as possible.
D. Name plate above manway or liquid level control, or level gauge. If there is no man way , 5'-0" above base. E. Lifting lugs - if the weight of the vessel is uniform, "E" dimension is equal .207 times the overall length of vessel.
I
H
~J
F. Manway 3'-0" above top of platform - floor plate. G. Insulation ring must clear girth seam and shall be cut out to clear nozzles, etc. H. Insulation ring spacing 8 - 12 feet (approx. length of _metal jacket sheet).
J. Girth seams shall clear trays, nozzles, lugs. K. Long seams to clear nozzles, lugs, tray downcomers. Do not locate long seams behind downcomers. Seams shall be located so that visual inspection can be made with all internals in place. Longitudinal seams to be staggered 1800 if possible.
o
L. Ladder and platform relation.
M. Davit and hinge to be located as the manway is most accessible, or right hand side. N. Ladder rung level with top of platform floor plate. The height of first rung above base varies, minimum 6", maximum 1'-6".
242 COMMON ERRORS in detailing pressure vessels
A.
Interferences Openings, seams, lugs, etc. interfere with each other. This can occur: 1. When the location on the elevation and orientation is not checked. The practice of not showing openings etc. on the elevation in their true position, may increase the probability of this mistake. 2. The tail dimensions or the distances between openings on the orientation do not show interference, but it is disregarded, that the nozzles, lugs etc., have certain extension. Thus it can take place that: a. b. c. d. e.
Skirt access opening does not clear the anchor lugs. Ladder lug interferes with nozzles. The reinforcing pads of two nozzles overlap each other. Reinforcing pad covers seam. Vessel-davit interferes with nozzles. This can be overlooked especially if the manufacturer does not furnish the vessel-davit itself, but the lugs only. f. Lugs, open~lgs, etc. are on the vessel seam. g. There is no room on perimeter of the skirt for the required number of anchor lugs. Particular care should be taken when ladder, platform, vessel-davit etc., are shown on separate drawings, or more than one orientations are used.
B.
Changes. Certain changes are necessary on the drawing which are carried out on the elevation, but not shown 011 the orientation or reversed. Making changes, it is advisable to ask the question: "What does it affect?" For example: The change of material affects:
Bill of material Schedule of openings General specification Legend
The change of location affects:
Orientation Elevation Location of internals Location of other components.
C.
Showing O.D. (outside diameter) instead of LD. (inside diameter) or reversed.
D.
Dimensions shown erroneously: I'-O·instead of 102!.O'instead of 20·etc.
E.
Overlooking the requirement of special material
243
PRESSURE VESSEL DETAILING (cont.)
GENERAL SPECIFICATIONS VESSEL TO BE CONSTRUCTED IN STRICT ACCORDANCE WITH THE LATEST EDITION OF THE ASME CODE SECTION VIII. DIV. I. FOR PRESSURE VESSELS AND IS TO BE SO STAMPED. INSPECTION BY COMMERCIAL UNION INSURANCE CO. OF AMERICA.
DESIGN
MAX. A. WORKING.
MAX. A. N. &C.
HYDRO. TEST
PRESSURE PSIG. @ TEMPERATURE of.
~~L-I-M-I-T-E-D-B-y------------~--------+---------4----------4--------~
a~------------------~--------~--------~---------+--------~ WIND PRESS. LBS/SQ. FT. CORROSION ALLOW. IN.
z
ffi~~------------------~--------~-------------------+--------~ SEISMIC COEFFICIENT ~~2~~~:~r~~c
Q~E~R~E~C=T~IO~N~(-S-H-IP~P-I-N-G~)--~---------+~L~O~N~G~I=T~U~D~I~N~A~L-J~O~I~N~T~~------~ WEIGHT LBS.
EFFICIENCY
WEIGHT FULL W/WATER LBS.
POST WELD HEAT TREATMENT@1100oF
OPERATING WEIGHT LBS.
DATA NOT SHOWN ARE NOT FACTOR OF DESIGN SA.
SA.
SHELL
HEAD THK.
...
FLANGE
TYPE THK
-SKIRT
~ a:: w
NOZZLE NECK
BASE
BOLTING
ANCH. BOLT
:IE
COUPLING
SADDLES
~
WELDED FITTING
GASKET PAINT
VESSELS REQUIRED:
APPROX. SHIPPING WEIGHT LBS.
N
~ ~
CHIP I.S. TO SOUND
CH. 1.1. TO SOUNO
METAL. WELD 'b'
METAL. WELD
'"0
:;0 tTl
CHIP I.S. TO SOUND
en en
METAL. WELD 'b'
VIII
C
IX
:;0 tTl
Go·
a f
,
iii
o
c3 f
"! -
I CHIP 1.5. TO SOUND METAL. WELD 'b'
GoO
~
i-~~~::::
CHIP 1.5. TO SOUND
0
IoC
~
< tTl en en tTl
Z r Z 0tTl C1 -i rJJ
METAL. WELD
~
r (;0·
\7
Z
SHOP NOTES
0
,-.. (')
0
1. Drill and Tap %" 0 Telltale hole in reinforcing
~
pacts.
2. Flange bolt holes to straddle principal centerlines
CHIP TO SOUNDJ
of vessel.
METAL. WELD
LONG & GIRTH SEAM WELD DETAIL
•
HEAD TO SHELL WELD DETAIL
3. Inside edges of Nozzle Necks shall be rounded. The radius of roundness 1/8" min. or one-half the wall thickness if the pipe wall is less than %".
~
-:......
Detailing openings as shown on the opposite page with data exemplified in the schedule of openings below, eliminates the necessity of detailing every single opening on the shop drawing. '"t:I
~ tTl til til
c::
~
o""'C
~
<: tTl
til til
Z
tTl
Z
otTl
~ rJJ
t"'"
~
~
C
z
o '6 o ::s ..... ~
c-/
DRAIN
N-I 11-/
INLET
MAR"
MAtVWAY
I
SERVICE
2" 6000~ CPLG. n W,N. 3 300* 18" 300"
ISIZEI RATING I
W.N.
IXH·lxH lXH !XH.
TYPE
: 15CH. IBORE,
• .3(}()
5Ye
.5"00 6~" ~A53-8 WALL
LG.
cff.... 1MIN.I v 1 - 1%"1"'11\1. 8" IMW.I /I 1/1/ I%"1 ""IN.
SA 5".JB
MAT"L.
NECK
24"xf2" ISA6"ls"70 110" O.D .• THK. RE'AD
MAT'L.
I g" I VI IIY 1%·jNll\I·I%"
0.5. I
1.5.
PROJ.
WELD DETAIL DWG.
• I b I C WELD SIZE
N
SCHEDULE
OF
OPENINGS
~
Vl
246 TRANSPORTATION OF VESSELS
Shipping capabilities and limitations.
1.
TRANSPORTATION BY TRUCK.
The maximum size of loads which may be carried without special permits a. weight approximately 40.000 lbs. b. width of load 8 ft., 0 in. c. height above road 13 ft., 6 in. (height of truck 4 ft., 6 in. to 5 ft., 0 in.) d. length of load 40 ft., 0 in. Truck shipments over 12 ft., 0 in. width require escort. It increases considerably the costs of transportation. 2.
TRANSPORTATION BY RAILROAD.
Maximum dimensions of load which may be carried without special routing. a. width of load 10ft., 0 in. b. height above bed of car 10 ft.-, 0 in. With special routing, loads up to 14 ft., 0 in. width and 14 ft., 0 in. height may be handled.
247
PAINTING OF STEEL SURF ACES
PURPOSE
The main purpose of painting is the preservation of a steel surface. The paint retards the corrosion 1., by preventing the contact of corrosive agents from the vessel surface and 2., by rust inhibitive, electro-chemical properties of the paint material. The paints must be suitable to resist the effects of the environment, heat, impact, abrasion and action of chemicals. SURFACE PREPARATION
The primary requisite for a successful paint job is the removal of mill scale, rust, dirt, grease, oil and foreign matter. Mill scale is the bluish-gray, thick layer of iron oxides which forms on structural steel subsequent to the hot rolling operation. If the mill scale is intact and adheres tightly to the metal, it provides protection to the steel, however, due to the rolling and dishing of plates, completely intact mill scale is seldom encountered in practice. If mill scale is not badly cracked, a shop primer will give long life in mild environments, provided that the loose mill scale, rust, oil, grease, etc. are removed. ECONOMIC CONSIDERATIONS
The selection of paint and surface preparation beyond the technical aspects is naturally a problem of economics. The cost of paint is normally 25-30% or less of the cost of painting a structure, thus the advantage of using high quality paint is apparent. Sixty percent or more of the total expense of a paint job lies in the surface preparation and the cost of preparation to different degrees is varying in a proportion of 1 to 10-12. For example, the cost of sandblasting is .about 10-12 times higher than that of the hand wire brushing. The cost of surface preparation should be balanced against the increased life of the vessel. SELECTION OF PAINT SYSTEMS
The tables on the following pages serve as guides to select the proper painting system and estimate the required quantity of paint for various service conditions. The data tabulated there have been taken from the Steel Structures Painting Council's specifications and recommendations. Considering the several variables of painting problems, it is advisable to request the assistance of paint manufacturers. SPECIAL CONDITIONS ABRASION
When the painting must resist abrasion, the good adhesion of the coating is particularly important. For maximum adhesion, blast cleaning is the best and also pickling is satisfactory. Pretreatments such as hot phosphate or wash primer are excellent for etching and roughening the surface. Urethane coatings, epoxies and vinyl paints have very good abrasion resistance. Zincrich coating, and phenolic paints are also good. Oleoresinous paints may develop much greater resistance by incorporation of sand reinforcement.
248 HIGH TEMPERATURE
Below temperatures of 500-600 0 F to obtain a good surface for coating, hot phosphate treatment is satisfactory. Above 500-600 0 F a blast cleaned surface is desirable. Recommended Paints: Up to
200 200 300 300 700 -
250 F 300 F 400 F 550 F 800 F
Oil base paints limited period An alkyd or phenolic vehicle Specially modified alkyds Colored silicones Inorganic zinc coatings above 550 F Black or Aluminum silicones 800 - 1200 F Aluminum silicones up to 1600-1800 F Silicone ceramic coatings
CORROSIVE CHEMICALS
See tables I and V for the selection of paint systems. THE REQUIRED QUANTITY OF PAINT
Theoretically, one gallon of paint covers 1600 square feet surface with 1 mil (0.001 inch) thick coat when it is wet. The dry thickness is determined by the solid (non volatile) content of the paint, which can be found in the specification on the label, or in the supplier's literature. If the content of solids by volume is, for example, 60%, then the maximum dry coverage (spreading rate) theoretically will be 1600 x .60 = 960 square feet. THE CONTENT OF SOLIDS OF PAINTS BY VOLUME % Spec. No.
1 2 3
4 5 6
a 9 11
Paint Red Lead and Raw linseed Oil Primer Red Lead, Iron Oxide, Raw Linseed Oil and Alkyd Primer Red Lead, Iron Oxide, and Fractionated Linseed Oil Primer Extended Red Lead, Raw and Bodied Linseed Oil Primer Zinc Dust, Zinc Oxide, and Phenolic Varnish Paint Red Lead, Iron Oxide, and Phenolic Varnish Paint Aluminum Vinyl Paint White (or Colored) Vinyl Paint Red Iron Oxide, Zinc Chromate, Raw Linseed Oil and Alkyd Primer
%
Spec. No.
96
12
~2
13
96
14
70
15 16
60 47 14 17 70
101 102 103 104 106 107
Paint
%
Cold Applied Asphalt Mastic 50 (Extra Thick Film) Red or Brown One-Coat Shop 60 Paint Red Lead, Iron Oxide & Linseed 96 Oil Primer Steel Joist Steel Shop Paint 70 Coal Tar Epoxy-Polyamide Black 75 (or Dark Red) Paint 40 Aluminum Alkyd Paint 37 Black Alkyd Paint 57 Black Phenolic Paint White or Tinted Alkyd Paint, 47 - 50 Types I, II, III, IV 13 Black Vinyl Paint Red Lead, Iron Oxide and 60 Alkyd Intermediate Paint
In practice, especially with spray application, the paint never can be utilized at 100 percent. Losses due to overspray, complexity of surface (piping, etc.) may decrease the actual coverage to 40-60%, or even more.
249 PAINTING TABLE I, PAINT SYSTEMS System Number SSPCPS
Paint and Dry Thickness, mils See Table IV CONDITION
1.01 Not
1.02 1.03
Condensation, chemical fumes, brine drippings and other extremely corrosive conditions are not present
Req'd
or
2.01 Steel surfaces exposed to the weather, high humidity, infrequent immersion in fresh or salt water or to mild chemical atmospheres
6
Not
or
Req'd
Total 4th 5th ThickCoat Coat ness
14 (1.7) 14 (1.7) I (1.7)
104 (1.3) 14
104 (1.0) 104
104
104 (1.3) 104
104 (1.0) 104
104
104
C
104
A (1.7) C (1.5) D (1.5) B (l.5)
E
8
2.04
4.0 5.0 4.0 4.0 4.0
(1.5) 104 ( 1.5) 104 ( 1.5)
104
104 5.0
104 ( 1.0) 104 (1.0) 104
4.0 4.0 3.5
(1.5)
Steel surfaces exposed to alternate immersion, high humidity and condensation 3.00 or to the weather or moderately severe chemical atmospheres or immersed in fresh water Immersion in salt water or in many chemical solutions, condensation, very severe 4.01 weather exposure or chemical atmospheres 4.02
Fresh water immersion, condensation, very severe weather or chemical atmospheres
4.03
Complete or alternate immersion in salt water, high humidity, condensation, and exposure to the weather
4.04
3rd Coat
(1.7)
1.06
2.03
2nd Coat
2
1.05
2.02
1st Coat
Condensation, or very severe weather exposure, or chemical atmospheres
4.05 Condensation, severe weather, mild chemical atmospheres
5,6,
8, or 10
1,2, 3, or 4
10
( 1.5)
5, or 6 ( 1.5)
103 ( 1.0)
5,6 or 103
G
G
9
9
5, or 6
5.5
( 1.5)
10
6
Not Req'd
.. ..
-3
or
8 6 or 8 6 or 8
Not Req'd
3
H (1.5)
H
G
9
H
H
fl.O 8
(1.5 )
4.0
9 (1.2)
9
9
G (1.5)
F
F
9
4.0
0.02 6.03
7.01
8.01
9.01
10.01
10.02
8
6 or 8
3
( 1.5)
Not Req'd
13 (1.0)
1.0
Not Req'd
M 31 (wet)
31 (wet)
Not Req'd
12 63
6
Not Req'd
N
6
Not Req'd
6 or
Dry, non corrosive environment, inside nomina of buildings or temporary weather pro- cleantection ing I and Longti me protection in sheltered or in2 or accessible places, short term or temporary 3 protection in corrosive environments Corrosive or chemical atmospheres, but should not be used in contact with oils, solvents, or other agents Underground and underwater steel structures Underground. underwater or for damp, corrosive environments. Not recommended for potable water or for high temperature
• Four coats are recommended in severe exposures
7.0
0.5) G 0.5)
10 Steel vessels and noating structures exposed to fresh or salt water, fouling water and weather
4.5
1
G 0.01
4.0 or 5.0
6
G
(2.0)
G
J
J
7.0
G
L
K
6.25
G
G
G G
G
63
N
(.5-2)
N (31 )
(31 )
0 (15-18)
0 (25)
(8-15)
63100
P 35
"The dry film thickness of the wash coat 0,3-0,5 mils.
250 TABLE I, PAINT SYSTEMS (continued) Paint and Dry Thickness, mils See Table IV
System Number SSPCPS
1st Coat
CONDITION
2nd Coat
3rd Coat
Total 4th 5th ThickCoat Coat ness
11.01
Fresh or sea water immersion, tidal and splash zone exposure, condensation, burial in soil and exposure of brine, crude oil, sewage and alkalies, chemical fumes, mists
12.00
High humidity or marine atmospheric exposures, fresh water immersion. With proper topcoating in brackish and seawater immersion and exposure to chemical acid and alkali fumes
Zinc-rich coatings comprise a number of different commercial types such as; chlorinated rubber, styrene, epoxies, polyesters, vinyls, urethanes, silicones, silicate esters, silicates, phosphates.
13.00
Industrial exposure, marine environment fresh and salt water immersion, and areas subject to chemical exposure such as acid and alkali.
Epoxy Paint System
6 or 10
Not Req'd
16
16
(16)
(16)
32
T ABLE III, PRETREATMENT SPECIFICATIONS Reference to Table I
Title and Purpose
WETTING OIL TREATMENT
Specification Number
SSPC ..PT 1-64
Saturation of the surface layer of rusty and scaled steel with wetting oil that is compatible with the priming paint, thus improving the adhesion and performance oT the paint system to be applied. 2
COLD PHOSPHATE SURFACE TREATMENT
SSPC-PT 2-64
Converting the surface of steel to insoluble salts of phosphoric acid for the purpose of inhibiting corrosion and improving the adhesion and performance of paints to be applied. 3
BASIC ZINC CHROMATE-VINYL BUTYRAL WASHCOAT (Wash Primer)
SSPC-PT 3-64
Pretreatment which reacts with the metal and at the same time forms a protective vinyl film which contains an inhibitive pigment to help prevent rusting. 4
HOT PHOSPHATE SURFACE TREATMENT
Converting the surface of steel to a heavy crystaline layer of insoluble salts of phosporic acid for the purpose of inhibiting corrosion and improving the adhesion and performance of paints to be applied.
SSPC-PT 4-64
251 PAINTING TABLE Il,SURFACE PREPARATION SPECIFICATIONS
Reference to Table I
Title and Purpose
SOLVENT CLEANING
Specification Number SSPC-SP 1-63
Removal of oil, grease, dirt, soil, saits, and contaminants with solvents, emulsions, cleaning compounds, or steam.
2
HAND TOOL CLEANING
SSPC-SP 2-63
Removal of loose mill scale, loose rust, and loose paint by hand brushing, hand sanding, hand scraping, hand chipping or other hand impact tools, or by combination of these methods. 3
POWER TOOL CLEANING
SSPC-SP 3-63
Removal of loose mill scale, loose rust, and loose paint with power wire brushes, power impact tools, power grinders, power sanders, or by combination of these methods.
4
FLAME CLEANING OF NEW STEEL
SSPC-SP 4-63
Removal of scale, rust and other detrimental foreign matter by high-velocity oxyacetylene flames, followed by wire brushing.
5
WHITE METAL BLAST CLEANING
SSPC-SP 5-63
Removal of all mill scale, rust, rust-scale, paint or foreign matter by the use of sand, grit or shot to obtain a gray-white, uniform metallic color surface.
6
7
COMMERCIAL BLAST CLEANING
SSPC-SP 6-63
Removal of mill scale, rust, rust-scale, paint or foreign matter completely except for slight shadows, streaks, or discolorations caused by rust, stain, mill scale oxides or slight, tight residues of paint or coating that may remain. BRUSH-OFF BLAST CLEANING
SSPC-SP 7-63
Removal of all except tightly adhering residues of mill scale, rust and paint by the impact of abrasives. (Sand, grit or shot) 8
PICKLING
SSPC-SP 8-63
Complete removal of all mill scale, rust, and rustscale by chemical reaction, or by electrolysis, or by both. The surface shall be free of unreacted or harmful acid, alkali, or smut. 10
NEAR-WHITE BLAST CLEANING
Removal of nearly all mill scale, rust, rust-scale, paint, or foreign matter by the use of abrasives (sand, grit, shot). Very light shadows, very slight streaks, or slight discolorations caused by rust stain, mill scale OXides, or slight, tight residues of paint or coating may remain.
SSPC-SP 10-63T
252 PAINTING T ABLE IV. P AIN:rS
Reference to Table I 1 2
3 4
5 6
8 9
11 12 13 14 15 16 102 103 104 106 107
Material
Red Lead and Raw Linseed Oil Primer Red Lead, Iron Oxide, Raw Linseed Oil and Alkyd Primer Red Lead, Iron Oxide, and Fractionated Linseed Oil Primer Extended Red Lead, Raw and Bodied Linseed Oil Primer Zinc Dust, Zink Oxide, and Phenolic Varnish Paint Red Lead, Iron Oxide, and Phenolic Varnish Paint Aluminum Vinyl Paint White (or Colored) Vinyl Paint Red Iron Oxide, Zinc Chromate, Raw Linseed Oil and Alkyd Primer Cold Applied Asphalt Mastic (Extra Thick Film) Red or Brown One-Coat Shop Paint Red Lead, Iron Oxide & Linseed Oil Primer Steel Joist Shop Paint Coal Tar Epoxy-Polyamide Black (or Dark Red) Paint Black Alkyd Paint Black Phenolic Paint White or Tinted Alkyd Paint, Types I, II, III, IV Black Vinyl Paint Red Lead, Iron Oxide and Alkyd Intermediate Paint
Number
1-64TNo.
1
2-64 No.
2
3-64T No.
3
tfl
4-64TNo. 5-64TNo. 6-64TNo. 8-64 No. 9-64 No.
4
Z 0
--
5
E-o
6 -< 8 u 9 ~ u
11-64T No. 11 ~ 12-6.J No. 12 Q., 13-64 No. 13 tfl 14-64T No. 14 u 15-68T No. 15 Q., 16-68T No. 16 ~ 102-64 No.1 02 103-64T No.1 03 104-64 No.1 04 106-64 No. 106 107-64T No.1 07
-.------r-----~------------~~--------------~~~~~~~--~
A B
C D E F G
H I J K L M N
o
P
Paint; Red-Lead Base, Ready-Mixed Type I red lead-raw and bodied linseed oil Type II red lead, iron oxide, mixed pigmentalkyd-linseed oil Type III red lead alkyd Primer; Paint; Zinc Chromate, alkyd Type Paint; Zinc Yellow-Iron Oxide Base, Ready Mixed, Type II-yellow, alkyd Paint; Outside, White, Vinyl, Alkyd Type Primer; Vinyl-Red Lead Type Vinyl Resin Paint Paint; Antifouling, Vinyl Type Paints; Boottopping, Vinyl-Alkyd, Bright Red Undercoat and Indian Red Finish Coat Enamel, Outside, Gray No. 11 (Vinyl-Alkyd) Enamel, Outside, Gray No. 27 (Vinyl-Alkyd) Compounds; Rust Preventive Coal Tar Enamel and Primers Coal Tar Base Coating Coating, Bituminous Emulsion
TT-P-86c TT-P-86c TT-P-86c TT-P-645
II
•
::s-< .~....= 1-0
C':I
o S C':I <'U ::s~
~
g~'-0
MIL-P-15929B CI') o...::s C':I MIL-P-16738B "; ~ 1-0 ::s MIL-P-15929B Q)~ ~ II VR-3 ~~ MIL-P-15931A II > ~
~
~ d MAP-44 >: MIL-E-15935B ;"1:1 .~ -< MIL-E-15936B :-= Q) 52-MA-602a ::s\I .S+=l MIL-P-15147C MIL-C-18480A i ~ MIL-C-15203c
·s
...J·c
253 PAINTING TABLE V, CHEMICAL RESISTANCE OF COATING MATERIAL
'"
;::I
~
o t:: or;;
>. < .. 0 c.~
o
~o
Acetaldehyde . . . . . . . . Acetic acid, 10% ...... Acetic acid, glacial . . . . . Acetone . . . . . . . . . . . . Alcohol, amyl . . . . . . . . Alcohol butyl, normal ... Alcohol, ethyl . . . . . . . . Alcohol, isopropyl . . . . . Alcohol, methyl . . . . . . . Aluminum chloride . . . . . Aluminum sulphate. . . . . Ammonia, liquid . . . . . . Ammonium chloride .... Ammonium hydroxide .. Ammonium nitrate . . . . . Ammonium sulphate .... Aniline . . . . . . . . . . . . . Benzene . . . . . . . . . . . . Boric acid. . . . . . . . . . . Butyl acetate. . . . . . . . . Calcium chloride. . . . . . . Calcium hydroxide . . . . . Calcium hypochlorite ... Carbon disulphide . . . . . Carbon tetrachloride .... Chlorine gas . . . . . . . . . Chlorobenzene . . . . . . . . Chloroform . . . . . . . . . . Chromic acid, 10% ..... Chromic acid, 60% ..... Citric acid. . . . . . . . . . . Copper sulphate . . . . . . . Diethyl ether. . . . . . . . . Ethylene glycol . . . . . . . Ferric chloride. . . . . . . . Ferric sulphate . . . . . . . . Formaldehyde, 40% .... Formic acid, 20%. . . . . . Formic acid, conc . . . . . . Gasoline . . . . . . . . . . . . Glycerine . . . . . . . . . . . Hydrochloric acid, 10%. . Hydrochloric acid, 30% .. Hydrochloric 4cid, conc .. Hydrofluoric acid, 10%. . Hydrofluoric acid, 40% . .
1 2 1 1 1 1 3 223 323 1 211 1 143 344 3 4 1 2 1 1 1 143 344 3 4 3 331 1 1 4 4 4 4 4 3 4 1 1 1 1 1 143 333 2 3 1 111 1 1 3 2 2 2 2 1 3 1 111112111112 1 I I I 1 121 1 1 1 1 2 1 111112111112 1 112224113313 1 111114112212 1 11322313313 1 111113113312 1 11322313313 1 1 1 1 1 131 133 1 2 1 1 1 1 1 131 133 1 2 4 4 2 4 2 3 2 244 4 441 1 133 344 3 4 1 111111111111 1 I I I 1 1 344 3 3 1 3 1 111112112212 1 1 121 121 122 1 2 1 2 2 3 224 1 } 221 3 4 441 1 144 444 3 4 4 441114444444 1 224 444 2 1 443 4 4 441114444444 4 441 1 144 444 4 4 2 224 3 342 244 2 4 2 224 3 3 4 2 244 2 4 1 111112112212 1 111111111111 4 441 1 144 4 4 444 1 1 1 1 1 121 1 1 1 1 2 1 111 1 131 133 1 3 1 1 1 1 1 121 122 1 2 1 111113112213 1 1 1 1 1 131 122 1 3 1 111113112213 4 4 1 1 1 121 1 4 4 2 4 1 1 1 1 1 121 1 1 1 1 2 1 1 1 1 1 131 133 1 3 1 221 1 131 133 1 3 1 221 113 1 133 1 3 1 2 1 1 1 1 3 2 2 2 2 1 2 1 2 1 1 1 1 322 221 3
254 PAINTING TABLE V, CHEMICAL RESISTANCE OF COATING MATERIAL (continued)
u
.....u
Hydrofluoric acid, 75% .. 1 Hydrogen peroxide, 3% .. 1 Hydrogen perioxide, 30%. 2 Hydrogen sulphide ..... 1 Hypocholorous acid . . . . 1 Kerosene . . . . . . . . . . . 4 Lubricating oil . . . . . . . . 4 Magnesium sulphate .... 1 Methyl ethyl ketone .... 1 Mineral oil . . . . . . . . . . 4 Nitric acid, 5% . . . . . . . . 1 Nitric acid, 10% . . . . . . 2 Nitric acid, 40% . . . . . . . 2 Nitric acid, conc . . . . . . . 3 Nitrobenzene . . . . . . . . . 4 Oleic acid . . . . . . . . . . . 3 Oxalic acid . . . . . . . . . . 1 Phenol, 15-25% . . . . . . . Phenol. . . . . . . . . . . . . Phosphoric acid, 10% . . . 1 Phosphoric acid, 60% ... 1 Phosphoric acid, conc. . . 1 Potassium alum . . . . . . . 1 Potassium hydroxide, 20% 1 Potassium hydroxide, 95% 1 Potassium permanganate . 2 Potassium sulphate ..... 1 Sea water . . . . . . . . . . . 1 Sil ver ni tra te . . . . . . . . . 1 Sodium bisulphate ..... 1 Sodium carbonate. . . . . . 1 Sodium chloride. . . . . . . 1 Sodium hydroxide, 10% . 1 Sodium hydroxide, 20% . 1 Sodium hydroxide, 40% . 1 Sodium hypochlorite.... 1 Sodium nitrate . . . . . . . . 1 Sodium sulphate. . . . . . . 1 Sodium sulphite . . . . . . . 1 Sulphur dioxide . . . . . . . 1 Sulphuric acid, 10% .... 1 Sulphuric acid, 30% .... 1 Sulphuric acid, 60% .... 1 Sulphuric acid, conc .... 2 Toluene . . . . . . . . . . . . 4 Trichloroethylene ..... 4
2 1 2 1 2 4 4 1 1 4 1 2 2 3 4 3 1 1 1 1 1 2 2 2 1 1 1 1 1 1 2 2 2 2 1 1 1 1 1 1 1 2 4 4
1 1 1 1 1 1 1 1 2 1 1 1 2 2 4 2 1 3 3 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 2 4 4
1 3 3 1 4 1 1 1 1 1 4 4 4 4 1 1 1 I
1 2 2 1 3 1 1 1 1 1 2 2 3 3 1 1 1 1
1 2 2 1 3 1 1 1 1 1 2 2 3 3 1 1 1 1
32 3 1 3 2 2 1 4 1 2 1 2 1 2 1 4 4 2 1 4 1 4 2 4 2 4 2 3. 3 3 2 2 1
2 1 2 1 1 1 1 1 4 1 1 2 2 2 3 2 1
2 3 3 2 3 4 4 2 3 4 3 3 4 4 4 4 2
2 3 3 2 3 4 4 2 3 4 3 3 4 4 4 4 2
2 1 3 1 1 2 2 1 I 2 1 1 2 2 3 2 1
1 1 1 1 4 4 3 1 1 1 1 4 1 4 4 4 4 1 1 1 1 1 1 1 1 1 1
1 1 1 1 2 2 2 1 1 1 1 2 1 2 2 2 3 1 1 1 1 1 1 1 1 1 1
1 1 1 1 2 2 2 1 1 1 1 2 1 2 2 2 3 1 1 1 1 1 1 1 1 1 1
3 3 3 2 4
1 1 1 1 1 1 2 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 2 3 4
3 3 3 2 2 2 3 2 1 1 2 2 1 1 2 2 3 2 2 2 2 2 3 3 3 4 4
3 3 3 2 2 2 3 2 1 1 2 2 1 1 2 2 3 2 2 2 2 2 3 3 3 4 4
1 1 1 1 1 1 3 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 3 4
3 2 1 2 3 4 1 4 4 4 4 2 2 2 2 3 3 3 3 3 4
1 1 1 1 1 1 2 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 1 2 3 4
3 4 4 2 4 4 4 2 3 4 3 3 4 4 4 4 2 4 4 3 3 3 2 3 3 4 2 1 2 2 4 1 3 3 3 4 2 2 2 2 2 3 3 3 4 4
c<:t ..... s::: o u .....
u
... :a ...o ~
.5
o
U
bll
I:
:a.!!l
:c::s ~
255
CHECK LIST FOR INSPECTORS QC I. Codes and Addenda .............................................................................. 2. Drawings: a) All info & details required by QC Manual shown on drawing ....... b) Heads correctly identified ............................................................... c) All metal correctly identified .......................................................... d) Name plate facsimilie stamped correctly: MAWP, MDMT and RT ................................................................. e) Approval by fabricator (on drawing) .............................................. f) Revisions or metal substitution shown and approved ..................... 3. Bill of Material: a) All material identified as SA or SB ................................................ b) Requirements of UCS 79 (d) specified were applicable ................. c) Required material test reports specified ......................................... d) Shop order, serial number, andlor job number shown .................... e) Material revision or substitution approved and shown when applicable ............................................................ 4. Calculations: a) Dimensions used match drawing .................................................... b) Correct stress values and joint efficiencies (S & E) used ............... c) Correct formula & dimensions used for heads ............................... d) Do nozzle necks comply with UG-45? ........................................... e) Required reinforcement calculations available for all openings ..... f) Special flange or structural loading calculations available ............ g) Identification with S/O or SIN and approved by fabricator ............ h) External design pressure correct - template calculations & template available ................................................... i) MA WP & MDMT matches drawing and specifications. MDMT correct for materials used (UCS-66, UHA-51) ................. 5. Purchase Orders: a) Is job number shown (when applicable)? ....................................... b) Correct specification (SA or SB) used ............................................ c) USC 79(d) & UG 81 requirements specified as applicable ............ d) Material Test Reports requested ..................................................... e) Is material ordered identical to Bill of Material or drawing requirements? ............................................................... 6. Welding: a) Are correct WPS(s) shown on drawings? ....................................... b) Are complete weld details for all welds shown on drawing? ......... c) Are copies ofWPS(s) available to shop supervisor for instruction? ..............................................................
AI
256
CHECK LIST FOR INSPECTORS (continued) QC d) Is a Welder's Log and Qualification Directory kept up-to-date and available? ........................................................ e) Are WPS, PQR, & WPQ forms correct and signed? ...................... f) Are welders properly qualified for thickness, position, pipe diameter and welding with no backing (when required)? ............... g) Is sub-arc flux, electrodes and shielding gas(es) used the same as specified on applicable WPS? ........................................... h) Do weld sizes (fillet & butt weld reinforcement) comply with drawing and Code requirements? .............................. , i) Is welder identification stamped or recorded per QC Manual and/or Code requirements? ..........................................
7.
Non-Destructive Examination & Calibration: a) Are SNT-TC-I A qualification records with current visual examination available for all RT technicians used? ....................... b) Do film reader sheets or check off records show film intemretation by a SNT- t~· LevelIorIfexaminer or interpreter? .................................................................................. c) Are the required number of film shots in the proper locations for the joint efficiency and welders used (UW-II, 12, & 52)? ........................................................................ d) Is an acceptable PT and/or MT procedure and personnel qualified and certified in accordance with Sec. VIII, Appendix 6 or 8 available? ............................................................. e) Is the PT material being used the same as specified in the PT procedure? ........................................................ f) Do all radiographs comply with identification, density, penetrameter, and acceptance requirements of Sect. VIII and V? ........................................................................ g) For B31.1 fabrication, is a visual examination procedure and certified personnel available? ................................. h) Are tested gases marked or identified and calibrated as stated in QC Manual? ................................................ i) Is a calibrated gage size per UG-l 02 available for demo vessel? ..............................................................................
ABBREVIA TIONS: Authorized Inspector AI Maximum Allowable Working Pressure MAWP Maximum Design Metal Temperature MDMT Quality Control QC Radiographic Examination RT Serial Number SIN SIO Shop Order Welding Procedure Specification WPS
Al
257
PART II. GEOMETRY AND LAYOUT OF PRESSURE VESSELS 1.
Geometrical Formulas .................................................................................. 258
2.
Geometrical Problems and Construction ................................................... 268
3.
Solution of Right Triangles ........................................................................ 270
4.
Optimum Vessel Size ................................................................................... 272
5.
Flat Rings Made of Sectors...... .................. .................................. .............. 274
6.
Frustum of Concentric Cone...................................................................... 276
7.
Frustum of Eccentric Cone......................................................................... 278
8.
Bent and Mitered Pipes................ ................................................ .............. 280
9.
Intersections ............................................................................................... 281
10. Drop at the Intersection of Vessel and Nozzle .......................................... 291
11. Table for Locating Points on 2: 1 Ellipsodial Heads .................................. 293
12. Length of Arcs............................................................................................ 297
13. Circumferences and Areas of Circles ......................................................... 300
14. Appurtenances ........................................................................................... 312
258
GEOMETRICAL FORMULAS (See examples on the facing page.) SQUARE A Area A a2 d 1.414 a 2 d A
a
2
0,7071 d or a=-fA
RECTANGLE A Area A axb d -Va2 +b2 a -V d 2 - b2 or a =4
b
-V d 2
- a2 or b =..4. a
PARALLELOGRAM A Area A axb A a b A b
a
RIGHT-ANGLED TRIANGLE Area A axb A -2-
a b c
-V c2 -b2 -Vc2 -a2 -Va2 +b2
ACUTE ANGLED TRIANGLE A Area cxh A -2A s
-V s (s - a) X (s - b) \Ii (a + b + c)
X (s -
c)
OBTUSE ANGLED TRIANGLE Area A bxh A
2
A
-V s (s - a)
s
\Ii(a+b+c)
X (s - b) X (s -
c)
259
EXAMPLES (See formulas on the facing page.) SQUARE Given:
Find:
Side
Area Diagonal Area
a = 8 in.
A·- a2 = 82 = 64 sq. in. d = 1.414 a = 1.414 x 8 = 11.312 in. A = ~ = 11.~122 = 64 sq. in.
Side a = 0.7071 d = 0.7071 x 11.312 = 8 in. Side a = RECfANGLE Given: Side Area Find:
Diagonal
a
=
{64 = 8 in.
a = 3 in., and b = 4 in. A = a x b = 3 x 4 = 12 sq. in. d = -Yal + b2 = -Y32 + 42 = -Y9 + 16 =
Side a =
t J
Side b=
~
=
=
m = 5 in.
= 3 in.
~2=
4 in.
PARALLEWGRAM Given: Height a = 8 in., and the side b = 12 in. Area A = a x b = 8 x 12 = 96 sq. in. Find:
Height
-t = i~ = 8 in. = 4= 9 6 = 12 in. 8
a =
Side b
RIGHT ANGLED TRIANGLE Given: Side a = 6 in., and side b = 121n. axb 6x8 . Find: Area A = -2- = -2- = 24 sq, Ill.
Sidee=-Ya2+b2 = ~ = ~ = -VI00 = lOin. Sidea=-Ve2 _b 2 = -YI02- 82 = -Y100-64 = -{36 =6in. Side b = -Ye2 - a2 = -V102 - 62 = -Y100 - 36 =
-%4 = 8 in.
ACUTE ANGLED TRIANGLE Side a = 6 in., side b = 8 in:; and side e = 10 in. Given: Area s = ~(a+b+e) = ~(o+8+ 10) = 12 Find: A = -vs(s-a)x(s-b)x(s-e)=
-Y12 (12 - 6) x (12 - 8) x (12 -10) =24 sq. in.
OBTUSE ANGLED TRIANGLE Given: Find:
Side Area
a = 3 in., side b = 4 in., and side e = 5 in. s=~(a+b+e)=~(3+4+5)=6
A = -ys(s-a)x(s-b)x(s-e)= -Y6 (6 - 3) x (6 - 4) x (6 - 5) =
f36 = 6 sq. in.
260
GEOMETRICAL FORMULAS (See examples on the facing page.) RIGHT TRIANGLE WITH 2 45° ANGLES A = Area A =a
2
2
A = 1.414a h=0.7071a a= 1.414h
EQUILATERAL TRIANGLE A = Area A=axh
2
h=0.886a a=1.155h
TRAPEWID A
=
Area
A = (a+b)h 2
REGULAR HEXAGON A = Area R = Radius of circumscribed circle r = Radius of inscribed circle A = 2.598 a 2 = 2.598 R2 = 3.464r2 R=a=1.155r r = 0.866 a = 0.866R a=R=1.155r
REGULAR OCTAGON A = Area R = Radius of circumscribed circle r = Radius of inscribed circle A = 4.828 a 2 = 2.828 R2 = 3.314r2 R = 1.307 a = 1.082r r = 1.207 a = 0.924R a = 0.765 R = 0.828r REGULAR POLYAGON A = Area n = Number of sides 360 0 oc 13= 1800 = oc
n-
A
2
=n a
r
R = ...Jr2 + a
2
4
= ...JR2 - a; a = 2...JR2- r2
261
EXAMPLES (See formulas on the facing page.)
RIGHT TRIANGLE WITH 2 45° ANGLES
Given:
Side
Find:
Area
8 in. a2 A = 2=
Side
b= 1.414
a
=
"4 2- ="2 = 32 sq. in. Q2
a=1.414x8=11.312in.
h = 0.7071 a=0.7071 x8 = 5.6568 in. EQUILATERAL TRIANGLE
Given:
Side
Fine:
A = 8 in.
h = 0.866 x a = 0.866 x 8 = 6.928 in.
Area
= 27712 . A = a 2x h = 8 x 26.928 = .5.5A24. 2 . sq. m.
TRAPEZOID
Given:
Side
Find:
Area
= 4 in., b = 8 in., and height h = 6 in. (a+b)h (4+8)x6 . A= 2 = 2 = 36 sq. m. a
REGULAR HEXAGON
Given:
Side
a = 4 in.
Find:
Area
A = 2.598 x a = 2.598 x 4 = 41.568 sq. m.
2
2
•
r = 0.866 x a= 0.866 x 4 = 3.464 in. R= a = 1.155r = 1.155 x 3.464 =4in. REGULAR OCTAGON
Given: Find:
R = 6 in., radius of circumscribed circle 2
2
Area
A = 2.8 28 R = 2.828 x 6 = 101.81 sq.
Side
a = 0.765
•
m.
R = 0.765 x 6 = 4.59 in.
REGULAR POLYGON
Given:
Number of sides n = 5, side a= 9.125 in.
Find:
Radius of circumscribed circle, R = 7.750 _12(ii _I 2 9.125 2 • r = -'1R -"4 = -'17.750 --4- = 6.25 m. Area
A= nra= 5x6.252 x9.125 = 14258 . 2 . sq. m.
262
GEOMETRICAL FORMULAS (See examples on the facing page.) CIRCLE A
Area
A
r 2 n=r2 x3.1416=d2 x 0.7854
C = Circumference
C =dxn=dx3.1416
Length of arc for angle oc = 0.008727 d x ex: a
CIRCULAR SECTOR A Area a = Arc
ex: = Angle
2
A = r n x 360 a
r x oc x 3.1416
180
ex: = 57.297xa
r
r = 2A
a
CIRCULAR SEGMENT A Area ex: = Angle c = Cord A Area of sector minus area of triangle h see table on page 290 c see table on page 290 ELLIPSE A = Area P = Perimeter A = Jrxa)(b=3.1416xaxb An approximate formula for perimeter:
a
P = 3.1416 -V2 (a 2 + b2)
ELLIPSE Locating points on ellipse a C = Ratio of minor axis to major axis b -Va2 - 2C x y2) x a
y
N =
(lj-Y,
where
N = The required number of holes (diameter d) of which total area equals area of circle diameter D.
263
EXAMPLES (See formulas on the facing page.) CIRCLE: Given: Radius r = 6 in. Find Area: A = r2 x n = 6 2 x 3.1416 = 113.10 sq. in. or A = J2 x 0.7854 = 122 x 0.7854 = 113.10 sq. in. Circumference C= d x n = 12 x 3.1416 = 37.6991 in. The length of arc for an angle, if IX = 60° Arc = 0.008727 d x IX = 0.008727 x 12 x 60 = 6.283 in. CIRCULAR SECTOR: Given: Radius r = 6 in. Angle = 60° . Find Area: A = r2 n x ~ 360 -- 62 n x 60 360 -- 18 .85 sq. m. Arc a = r x ex 1~~·1416 = 6 x 60 1~03.1416 = 6.283 in. Angle
ex = 57,296 x a = 57,296 x 6.283
CIRCLULAR SEGMENT: Radius r = 6 in. Given: Find Area: A Area of sector
r2
Jr
=
600
6
r
Angle ex = 90°
x360=6 2 x3.1416x
~~O
= 28.274 sq. in.
Minus area oftriangle = 18.000 sq. in. Area of segment A = 10.274 sq. in. Chord
c = 2r x sin ~ = 2 x 6 x sin 90= 2 x 6 x 0.7071 = 8.485 in. 2
ELLIPSE: Given: Half axis,
a
Find:
A =
Area Perimeter
=
8 in. and
b = 3 in.
a x b = 3.1416 x 8 x 3 = 75.398 in. P = 3.1416"2(a2 +b 2 ) =3.1416"2(8 2 +3 2 ) = 7t X
3.1416 "146 = 37.96 in. ELLIPSE: Given: Half-axis, Find:
y=
~~2
i
a = 8 in. and b = 4 in., then C = [;= = 2, x = 6 in. 2 2 = ...)8 6 = ~ = ~= 2.6457 in.
"9=
2
X= ~a2 - (2C xy2)
=..J8 2- (2 x 2 x 2.64572) = ~64 - 4 x 7 =....f36 =6 in.
EXAMPLE: How many V4 in. ¢ holes have same areas as a 6 in. diam. pipe? N= (D/d)2 (6/0.25)2 242 576 holes Area of6 in. ¢pipe = 28,274 in. 2 Area of576, V4 in. ¢ holes = 28,276 in. 2
=
= =
264
GEOMETRICAL FORMULAS (See examples on the facing page.) CUBE ~
V= Volume V= a 3 a =
,
,
tv
SQUARE PRISM 01;;>
V = Volume
V = axbxe V
a
Q
V
a=liC
V
b=
ae
V
e=aJi
PRISM V = Volume A = Area of end surface V = h x A This formula can be applied for any shape of end surface if h is perpendicular to end surface. CYLINDER V = Volume
S = Area of cylindrical surface V = 3. 1416 x r2 x h = 0.785 x d 2 x h
S = 3.1416 x d x
h
CONE V = Volume 2 S = Area of conical surface V = 3. 1416 x r x h = 1.0472 x r2 x h
3
h
I d
e
~r2
S
3.1416 re = 1.5708 de
x h2
FRUSTUM OF CONE V = Volume S = Area of conical surface V = 0.2618h (D2 + Dd + d 2) a = R-r e = ~a2 + h2 S = 1.5708e(D+d)
265
EXAMPLES (See formulas on the facing page.) CUBE Given:
Side
Find:
Volume V = a 3
a = 8 in.
= 83 = 512 cu. in.
a
=
~512
SQUARE PRISM a Given: Side
=
8 in., b = 6 in., and c
Side
Find:
Volume V = a x b x c x Side
a =~
=
V c =-axb
=--
bxc
PRISM Given: End surface Find:
=
=
4 in.
x 6 x 4 = 192 cu. in.
192 = 8 in.· b =~= 192 = 6 in. 6x4 ' a x e 8x4 192 = 4 in. 8x6
and h
6 in.,
Volume V = 3.1416 x
r2
and h = 8 in.
= 8 x 12 = 96 cu. in.
V= h x A
r
=8
A = 12 sq. in.,
Volume
CYLINDER Given: Find:
8 in.
=
=
x h
12 in. =
3.1416 x 6 2 x 12 = 1357.2 cu. in.
Area of Cylindrical Surface: S = 3.1416 x d x h=
CONE Given: Find:
r
=
3.1416 x 12 x 12 = 452.389 sq. in.
=
6 in.,
and h = 12 in.
Volume V = 1.0472 x c
= ~r2 + h 2
Area of Conical Surface: S
=
r2
=
x h = 1.0472 x 6 2 x 12 = 452.4 cu. in.
-/36 + 144 = -V180
=
13.416 in.
3.1416 x r x c =
= 3.1416 x 6 x 13.416 = 252.887 sq. in. FRUSTUM OF CONE Given: Diameter D
=
24 in., and d= 12 in., h = 10.375 in.
Find:
=
0.2618 h (D2 + Dd = d2) =
Volume
V
= 0.2618 x 10.375 (242 + 24 x 12 + 122) Surface:
=
2737.9 cu. in.
S = 1.5708 c (D + d) = 1.5708 x 12 (24 + 12) =678.586 sq. in.
266
GEOMETRICAL FORMULAS (See examples on the facing page.)
SPHERE V = Volume
A = Area of Surface 3 V= 4lrxr"3= lrxd 4.1888 r3 = O.5236d 3
3
6
A = 4lr x r2 = lrd2
SPHERICAL SEGMENT V = Volume
A = Area of Spherical Surface
V = 3.1416 x m2(r-~) A = 2lr x r x m
SPHERICAL ZONE V = Volume V = O.5236h
A = Area of Spherical Surface
(3C: 4
-t-
3C} + h 2 )
4
A = 2lr rh = 6.2832 rh
TORUS R
r
V = Volume
A
Area of Surface
V = 19.739 Rr2 2.4674 Dd2 39.478Rr A 9.8696Dd
See tables for volume and surface of cylindrical shell, spherical, elliptical and flanged and dished heads, beginning on page 416.
267
EXAMPLES (See formulas on the facing page.) SPHERE Given: Radius Find: Volume or Area or
r = V = V = A = A =
6 in. 4.1888 r3 = 4.1888 x 216 = 904.78 cu. in. 0.5236 d 3 = 0.5236 x 1728 = 904.78 cu. in. 4 lCr 2 = 4 x 3.1416 x 6 2 = 452.4 sq. in. lCd 2 = 3.1416 x 122 = 452.4 sq. in.
SPHERICAL SEGMENT Given:
Radius r = 6 in. and m = 3 in.
Find:
Volume V = 3.1416m 2 (r-'3)=3.1416x3 2 Area
(6-~)=141.37cu.in.
A = 2lC x r x m = 2 x 3.1416 x 6 x 3 = 113.10 sq. in.
SPHERICAL ZONE Given:
Radius r = 6 in., C1 - 8 in., C2 = 11.625 in., and h = 3 in.
Find:
2 Volume V= 0.5236 x 3 x (3; 8 + 3 x ~1.6252 + 32) = 248.74 cu. in. Area
A = 6.2832 x 6 x 3 = 113.10 sq. in.
TORUS Given:
Radius R = 6 in. and r = 2 in.
Find:
Volume V= 19.739 R x r2 = 19.739 x 6 x 22 = 473.7 cu. in. Area
A = 39.478 Rr = 39.748 x 6 x 2 = 473.7 sq. in.
268
GEOMETRICAL PROBLEMS & CONSTRUCTIONS A
LOCATING POINTS ON A CIRCLE EXAMPLE R = 5 in. X = 3 in. Y = -VR2 - Xl Find Y= ~ 52 - 3 2 = X = -V R2 - y2 = ~ 25 - 9 =
116
= =4 in. LENGTH OF PLATE FOR CYLINDER L = 7r X D EXAMPLE L
Length of plate D = Mean diameter
Inside diameter = 24 in. Thickness of plate: 1 in. The length of plate = L = 25 x 3.1416 = 78.5398 in.
=
TO FIND THE RADIUS OF A CIRCULAR ARC (C/2)~ M2 EXAMPLE R 2M c = 6 in., M = 2 in. ( 6/2)2 + 22 Find: R= 2 x 2 = 3.25 in. TO FIND THE CENTER OF A CIRCULAR ARC When the radius, R, and chord, C, are known, strike an arc from point A and from point B with the given length of the adius. The intersecting point, 0, of the two arcs is the center of the circular arc. Y
=
~ R2 _ (C/2)2
TO FIND THE CENTER OF A CIRCULAR ARC When the chord, C, and dimension, M, are known, strike an arc from point A and from point B on both sides of the arc. Connect the intersecting points with straight lines. The intersecting point of the straight lines, 0, is the center of the circular arc. R = C2 + 4M2. Y = R _ M 8M
'
CONSTRUCTION OF A CIRCULAR ARC The radius is known, but because of its extreme length it is impossible to draw the arc with a compass. Detennine the length ofchord, C and dimension M. Draw at the center ofthe chord, C a perpendicular line. Measure on this line dimensionM. Connect points AD and BD. Bisect lines AD and BD and measure MI4 dimension perpendicular. Repeating this procedure to the requested accuracy, M will be 4 times less at each bisection 4 times less. The vortices ofthe trian les are the oints ofthe circular arc.
269 GEOMETRICAL PROBLEMS AND CONSTRUCTIONS A
TO FIND THE FOCUS OF AN ELLIPSE Given the minor and major axis of the ellipse. Find the focus. Strike an arc with radius, a (one half of the major axis) with center at B. The intersecting points of the arc and major axis are the two foci of the ellipse. c = ~a2 - b2 THE CONSTRUCTION OF ELLIPSE Place a looped string around points F 1, Band F 2 . Draw the ellipse with a pencil moving it along the maximum orbit of the string while it is kept taunt.
y= b
v'l-~
THE CONSTRUCTION OF ELLIPSE Describe a circle of which diameter is equal to the major axis of the ellipse and with the same center a circle of which diameter is equal to the minor axis. Draw a number of diameters. From the intersecting points of the large circle draw perpendicular lines to the major axis and from the intersections of the small circle draw lines parallel with the minor axis. The intersections of these parallel and perpendicular lines are points of the elliptical curve. PROPERTIES OF 2: 1 ELLIPTICAL HEAD d R r
=
0.8 D (approx.) 0.9 D (approx.) 0.173 D (approx.)
The upper portion of the head within diameter, d is a spherical segment with negligible deviation.
E
x
LOCATING POINTS ON A 2: 1 ELLIPTICAL HEAD
I X = V'R2
i
- 4 y:z
Y
= VR 2 - X2 2
Note: The curvature of an elliptical head on one side only is a true ellipse (inside or outside). The opposite parallel curve is geometrically undetermined. To locate points on this curve expecially in the case of a heavy walled head is possible by means of layout only. See tables on page 293.
270
SOLUTION OF RIGHT TRIANGLES REQUIRED KNOWN SIDE OR ANGLE (ENCIRCLED) a,b
@...L:J'
tan A
=...!..
b
a, b
~<;
b
b tan B = a
b
a, b
~a
=~
c
@.£j.
a sin A = c
a, c
~.
a cos B = c
a, c
/'1
A, b
A~
b
=~
Find Angle B =~= 0.500 12 cos 0.500 = 60 0 Find side b =~ v'25-9 =V16 = 4 in.
b = a x cot A
Angle A = 25 0 , side a = 6 in. Find side b = 6 x cot 25 0 = 6 x 2.1445 = 12.867 in.
~
a c = sin A
Angle A = 30 0 , side a = 6 in. =_6_= 12 in. Find side c = _6_ _ 0.500 sin 30 0
a =- b x tan A
Angle A = 25 0 , side b = 12.867 in. Find side a = 12.867 x tan 25 0 = ~ 2.867 x 0.4663 = 6 in.
c -
b cos A
b
A, c
AL:::1
a = cxsinA
A, c
;/1
b = c x cos A
A
= 12 in. 6 Find Angle A = - = 0.500 12 sin 0.500 = 30 0
lbJ
A.2::J· A
=V
3 2 + 4 2 =-v'9+i6 =v'25 = 5 in.
Side a = 3 in. c = 5 in. a
/1a
A, b
Find side c
Side a = 6 in. c = 12 in.
(I»
A, a
Side a = 6 in. b = 12.867 in. 12.867 Find Angle B = 2.1445 6 tan 2.1445 = 65 0
Side a = 6 in. c
a, c
A
Side a = 6 in. b = 12.867 in. =_6_ _ = Find Angle A 0.4663 12.867 tan 0.4663 = 25 0
Side a = 3 in. b = 4 in.
b
A, a
EXAMPLES
FORMULAS
C~
Angle A = 30 0 , side b = 12 in. b 12 Find side c ="'CoSJO'O = 0.866 = 13.856 in. Angle A = 30 0 , side c = 12 in. Find side a = 12 x sin 30 0 = 12 x 0.500 = 6 in. Angle A = 300 , side c = 12 in. Find side b = 12 x cos 30 0 12 x 0.866 = 10.392 in.
271 Frustum of ECCENTRIC CONE EXAMPLE Given:
Mean diameter at the large end, 0 = 36 in. Mean diameter at the small end, 01 = 24 in. Height of frustum. HI = 24 in. Determine the Required Plate
Half of the Required Plate
Tan a = _
0-01 36-24 H = ~= 0.500 = 26 0 .34' 1
o
36 2. H = 'taii"Q. =0':500 = 72 in., H2 = H -H 1 = 72- 24 = 48 in. 3. Divide the base circle into 12 equal parts. 4. Draw chords Cl, C2, C3, etc. to the dividing points. 5. Calculate the length of the chords C \ ' C 2' C 3' etc. using Factor, C from table "Segments of Circles for Radius = 1 on page 290 . 6. Calculate the lengths of SI, S2, etc. and Si, S2' etc. At The Bottom Factor c times mean radius
=
30 0 60 0
Chords, CI C 2 ·· . in. 9.317~ CI = 18.000~
VH2
At The Top
+
Factor c times mean radius
=
=
C2 I, 2
S 1, 2 ... ft.-in. SI =
6'-0
%
90 0
C2 = C3 =
25.452"
6' - 2 0/16 S3 = 6'-4%
120 0
C4 =
31.176 "
S4 =
1500
C5
34.776"
S5 = 6' - 710/16
=
S6
S2 =
6'-6 7/16
=V H2 + 0 2 = 6' - 8Vl
v'H~
Chords, C I C 2 etc. in. Cl= 6.212 • C2 = 12.000-
+
=
C'2 1,2 ...
• SI,2 . . . ft.-in.
S ... = 4'-0 % S2 = 4'-1 ~ = 4'-2'0/,6
53
C3 =,
16.968"
C4=
20.784 "
S4 = 4'-40/,6
C5 = 23.184 "
S5 = 4'-50/,6
S·6 =VHi + 0 2I
4'-5 11h6
272
OPTIMUM VESSEt SIZE* To build a vessel of a certain capacity with the minimum material, the correct ratio of length to diameter shall be determined. The optimum ratio of length to the diameter can be found by the following procedure: (The pressure is limited to 1000 psi and ellipsoidal heads are assumed) F=
P
CSE
, where
p
C S E
DeSign pressure, psi. Corrosion allowance, in. Stress value of material, psi. Joint efficiency
Enter chart on facing page at the left hand side at the desired capacity of the vessel. Move horizontally to the line representing the value of F. From the intersection move vertically and read the value of D. The length of vessel
=
4 V 2 ,where V D D
1T
= =
Volume of vessel, cu. ft. Inside diameter of vessel, ft.
EXAMPLE Design Data: P = 100 psi, V = 1,000 cu. ft., S = 16,000 psi., Find the optimum diameter and length F= _ _ _--"1:. .: 0-=.0 _ __
0.0625 x 16,000 x 0.8
E = 0.80,
C = 0.0625 in.
= 0.125 in.- 1
From chart D = 5.6 ft., say 5 ft. 6 in. Length = 4 x 1,000 3.14 X 5.5 2 = 42.1, say 42 ft. 1 in.
·FROM: " Nomographs Gives Optimum Vessel Size," by K. Abakians, Originally published in HYDROCARBON PROCESSING, Copyrighted Gulf Publishing Company, Houston. Used with permission.
273 100,000 80,000 60,000 50,000 40,000 30,000 20.000
t:
10,000 8,000 6.000 5.000 4,000 3.000
B2.000 uJ
:::;:: :l
:; 1,000 ;;. 800 ...I 600 uJ Vl 500 Vl uJ 400 ;;. 300 200
100 80 60 SO 40 30
/
/
/ 1/
/
20
10
/
V I.S
2
3 4 5 6 VESSEL DIAMETER, D FT.
8
910
15
CHART FOR DETERMINING THE OPTIMUM VESSEL SIZE (See facing page for explanation)
20
274 FLAT RINGS MADE OF SECTORS
B §
I~I
Making flat rings for base, stiffeners etc., by dividing the ring into a number of sectors, less plate will be required. ONE PIECE
The cost of the welding must be balanced against the saving in plate cost. 2 SECTORS
3 SECTORS
0,7070
I~I
i"
~
6 SECTORS
=
Outside diameter of ring. Inside diameter of ring.
1. Determine Df d and D2 (the area of square plate would be required for the ring made of one piece) 2. Read from chart (facing page) the percentage of the required area when the ring divided into the desired number of sectors 3. Determine the required area of plate
~
sr
D d =
4 SECTORS
~
# #
The chart on facing page shows the total plate area required when a ring is to be divided into sectors. This area is expressed as a percentage of the square that is needed to cut out the ring in one piece. The figures at the left of this page show the width of the required plate using different number of sectors.
DETERMINATION OF THE REQUIRED PLATE SIZE
0.3830
I;'
Since the sectors shall be welded to each other, the welding will be increased by increasing the number of sectors.
8 SECTORS
: it
THE REQUIRED WIDTH OF PLATE FOR RINGS MADE OF SECTORS
4. Divide the area by the required width of plate as shown at the left of this page to obtain the length of the plate. 5. Add allowance (max. 1 inch) for flame cutting between sectors and at the edges of the plate
See Example On Facing Page.
275 FLAT RINGS MADE OF SECTORS (cont.) 100r------.------.------.------,,------r-----~
0
N
0
d
I.l.
20
0
E-<
Z
70
~
60
~ ~
18 16
~ CI')
-< tZl < ~
40
1.3
-<
30
12
1:4-
~ ~
E-<
-<
.....l
20
1.1
~
10
0
2
EXAMPLE
3
4
5
6
7
8
NUMBER OF SECTORS
Determine the required plate size for a 168 in. 0.0., 120 in. I.D. ring made of 6 sectors 1. D/d = 1.4; 02 = 28,224 sq. in. 2. From chart (above) the required area of plate is 50% of the area that would be required for the ring made of one piece. 3. Area required 28.224 x 0.50 = 14,112 sq. in. 4. Divide this area by the required width of plate (facing page). Width = 0.5 x 168 = 84 14,112/84 = 167.9 inches, the length of plate. 5. Add allowance for flame cut.
276
FRUSTUM OF CONCENTRIC CONE Given: D = Mean diameter at the large end. D J = Mean diameter at the small end. H = Height of the frustum.
Determine the Required Plate.
The Required Plate b
r D
c= --.jH2 + b2 fJ= r.. x 360
D-D]
b=-2-' e
R
=--.!;L Sin a
tan a= Q H R = c+e
CONICAL TANK ROOF
D
R- r -cos
r
jJ=L x 360 R
The Required Plate
r
D
=-]
] 2
277 FRUSTUM OF CONCENTRIC CONE Made from two or more Plates
Given: D
Mean diameter at the large end. Mean diameter at the small end. Height of the fustrum Number of plates (sector)
DJ H
n
Determine the Required Plate b = D-D J
2
tan
D Elevation
IX
12.
H
rJ
~b2 + H2 DJ 12
e
..!..) --
R
c+e D x 1fX 57.296 2Rn
C
Z
=
sm
y
IX
X Y
R x sin r + W' R x sinr + I"
Z -=
e x sin
V = e x cos
One Sector of Plate
r
r
Width ofthe Required Plate = R - V + 1" Length of the Required Plate if the Frustum made from: 2 Plates: 2X + Y + Z
x
IENGlH y
Z
x
3 Plates: 2X + 2Y + 2Z 4 Plates: 2X+ 3Y+ 3Z 6 Plates: 2X + 5 Y + 5Z
-r--tt---t-t--::::=*=~=t- YJ" typical
~
cl_
Required Plate
278
THE FRUSTUM OF ECCENTRIC CONE Determination of the Required Plate by Layout and by Calculation Half of the plate Symmetrical
LAYOUT
1.
2. 3.
Draw the side view and half of the bottom view of the cone. Divide into equal parts the base and the top circle. Draw arcs from points 2 1, 3 1, 4 1, etc. with the center ]1.
4. Side view of cone
From the points /0, 2°, 3", etc. strike arcs with center O.
5.
Half of the bottom view
Fig. A
o
- 6.
Starting from a point on arc 1 1, (marked 1) measure the spacing of the bottom circle of the cone and intersect arc 2°. From the point marked 2 measure again one space intersecting arc 3°, etc. The points or intersections are points on the curvature of the plate at the bottom of the cone. To determine the curvature of the plate at the top of the cone, repeat steps 4 and 5, but measure on the arcs drawn with center 0 the spaces of the top circle.
CALCULATION To find the curvature of the plate by calculation, the simensions ]1 - 2 1, ]1 _ 31, etc. and 0 - ]1, 0 _ 21 , etc. shall be determined. Fig. B shows as an example the calculation of 0-4 1 only (marked S, ). If the bottom circle is divided into 12 equal spaces, C3 = 2 R x sin 45° S3
Fig.B
=
VH2 + C]
Where R denotes the mean radius of the base circle. See example on the following page.
279
FRUSTUM OF ECCENTRIC CONE EXAMPLE Given: Mean diameter at the large end, D = 36 in. Mean diameter at the small end, I?J = 24 in. Height of frustum, H / = 24 in. Determine the required Plate.
s
Half of the Required Plate
il4 = 0.500=260-34'
Tana=D D 1 = 36
il/
=~ = 72 in. H =H-H = tan a 0.500 '2 1 72 - 24 = 48 in. Divide the base circle into equal parts. H=.J2.
4.
Draw chords C 1 , C2 , C3 , etc. to the dividing points.
5.
Calculate the length of the chords C1 ' C2' C3' etc. using Factor C from table "Segments of Circles for Radius = 1" on page 290.
6.
Calculate the lengths of S1' S2' etc. and Sj, Sj, etc. At The Bottom Factor c times mean radius = hords, c/ ' C2 ... in.
30° 60° 90° 150°
C]
=
C2 =
C3 = C = C5 =
9.137" 18.000" 25.452" 31.176" 34.776"
...f H2 + C2}, 2= S}, 2 . . . [1. in,
S. = 6' - 6 7116 S5 = 6' - 7 15 116
At The To
Factor c times mean radius = Chords, C], C2 etc. in.
C] =
6.212"
C =
16.968" 20.784" 23.184"
C = C5 =
...fH22 + C2],2 =... S/*.2 . .. [1. in. S]* =4' - 0 3/8 S = 4' - 2 15116 S,,* =4' - 4 5116 S5* =4' - 5 5116
S6 =V H } + Dl = 4' - 511 116
280 BENT AND MITERED PIPE The length of a pipe bent to any shape is equal to the length measured on the centerline of pipe. Example: (The pipe bent as shown) Given: R = 8 in., RI = 6 in., Find the length of pipe, L. L = R It''x
ex
=
nO
~ = 36 0
1=
2 in.
~ + RI ". -'l- + 180
180
8x3.14 x 2L-+6x3.14 x 180
36 +2 180
25.13 x 0.40 + 18.85 x 0.20 + 2 =
15.82 in.
The Required Length of Pipe for Coil L = V(n x D x".)2 + H2 Where n Number of turns L = Length of required pipe EXAMPLE Given: D = 10 in., H = 24 in., n = 12 L
=V (12 x 10 x 3.14)2 + 242
= 378 in.
The Required Length of Pipe for Coil 2 Where L = r ". c d + C Clearance between turns of pipe. Outside disl!1eter of pipe. (Approximation) d L Required length of pipe.
=
EXAMPLE Given: r 10 in. d = 2.375 in., c = 1 in. L = 10 2 x 3.14 = 93.08 in. 2.375 + 1
Mitered Elbow To find the angle of cut for any elbow, divide the total number of degrees of the elbow by twice the number of cuts. EXAMPLES 90 0 : 6 = 15 0 3 cuts x 2 6 90 0 : 4 = 22V20 2 cuts x 2 = 4 2 cuts x 2 = 4 120 0 :4= 300 The length of pipe required to form any shapes by mitering is the sum of the centerline lengths of the pipe sections.
281
INTERSECTION OF CYLINDER & PLANE When the intersecting plane is not perpendicular to the axis of the cylinder, the intersection is an ellipse. CONSTRUCTION OF THE INTERSECTING ELLIPSE
Divide the circumference of the cylinder into equal parts and draw an element at each division point. The major axis of the ellipse is the longest distance between the intersecting points and the minor axis is the diameter of the cylinder. The points of the ellipse can be determined by using the chords of the cylinder spaced by projection as shown or by calculations as exemplified below. With this method may be laid out sloping trays, baffles, down-comers etc. The thickness of the plate and the required clearance shall also be taken into consideration. DEVELOPMENT
The length, H is equal to the circumference of the cylinder. Divide this line into the same number of equal parts as the circumference of the cylinder. Draw an element through each division perpendicular to this line. Determine the length . of each element as shown or by calculation. By connecting the end points of the elements can be obtained the stretched-out line of the intersection and may be used for cutting out pattern for pipe mitering, etc.
la
EXAMPLE
11
(a 4 - a 3 ) cos 40 0
12
(a 4 - a 2 ) cos 40 0
for calculation of length of elements. The circumference of the cylinder is divided into 16 equal parts. The angle of a section = 22-1 /2 degrees. The angle of the intersecting plane to the axis of the cylinder = 40 degrees. c 1 = r X cos 22-1/2 0 r X cos 45 0 r x sin 22-1/2 0 etc.
a1
=
hI
--=--~
~n 40 0
a
2
h2 = ----"'--,..... 0 ~n 40
etc.
282
INTERSECTION OF CYLINDERS of equal diameters with angle of intersection 90 0
I
I
!
I
L
/
-~--,~ f--
---
-+"\.
!'\
/
I I
""
I
'"1"\ - 1/
I
/l
'.:Ie,
.......
I j
.......
/'
./
~ C31 C4 ........
./
./
1 I
I
!
~ ~"
t-
~
'/4 OF f-
l-
~
L w
~ C3 C2
z
w ~
I
~
ci\ C3 \ C4
~ ~ ~
~-~c, «
w
a:
Ll-
V
C1
V
(..)
\
'/40F
Divide the circumference of the cylinders into equal parts and draw an element at each division point. The intersecting points of the elements determine the line of intersection.
.......
\
OF
THE LINE OF INTERSECTION
I
I
lL'
'12
::) (..)
a:
U
DEVELOPMENT OF PATTERNS
Draw straight line of equal length to the circumference of the cylinders. Divide the . lines into the same number of equal parts as the circumference of the cylinders. Draw an element through each division perpendicular to these lines. Determine the length of each element by projection or calculation. (See example below). By connecting the end point of the elements the stretched out curve of the intersection can be developed. EXAMPLE
for calculation of length of elements If the circumference of cylinders is divided into 16 equal parts a = 22-1/2 0 c1 c2 c3 c4
= = = =
r sin a rsin2a r cos a r
283
INTERSECTION OF CYLINDERS of unequal diameters with angle of intersection 90 0
+-+-+~.--.
c b
Q
Q
b c
THE LINE OF INTERSECTION
w U Z
w
c:: W
LL
~ ;:)
u
c::
u
Divide the circumference of the small cylinder into as many equal parts as necessary for the desired accuracy. Draw an element at each division point. Project distances C 1 ' c 2 etc. to the circumference of the larger cylinder and draw elements at each points. The intersecting points of the elements of the large and small cylinder determine the curve of intersection. DEVELOPMENT OF PATTERNS
Draw a straight line of equal length to the circumfer-ence of the cylinders. Divide the line for the small cylinder into the same number of equal parts as the circumference of the small cylinder. Draw an element thrsugh each division perpendicular to the line. Determine the length of the elements by projection or calculation. (See example below). By connecting the end point of the elements the stretched out curve of the intersection can be developed. The curvature of the hole in the large cylinder is determined by the length of elements c 1 ' c2 etc. spacing them at distances a, b, c etc., which are the length of arcs on the partial view of the large cylinder.
EXAMPLE
for calculation of length of elements. Dividing the circumference of the cylinder into 12 equal parts, a = 300 c 1 = r sin 300 c2 = r cos 300 c 3 = r
284
INTERSECTION OF CYLINDERS with non intersecting axes abc
d
e
f
THE LINE OF INTERSECTION Divide the circumference of the branch cylinder on both views into as many equal parts as necessary for the intended accuracy. Draw an element at each division point. The points of intersection of the corresponding elements determine the line of intersection.
l L
J
L
/
DEVELOPMENT OF PATTERN Draw a straight line of equal length to the circumference of the branch cylinder and divide it into the same number of equal parts as the circumference. Draw an element through each division perpendicular to the line. Determine the length of the elements by projection or calculation. (See example below). By connecting the end point of the elements the stretched out curve of the intersection can be developed.
w
u z
w
a: w
V lh
u.. ~
:::>
12~
u
13 ' \ 14 ~ I~
Ie
1
1
a:
U
The curvature of the hole in the main cylinder is determined by the length of elements c 1 , c 2 etc. spacing them at distances a, b, c, etc., which are the length of arcs on the main cylinder (see elevation). EXAMPLE for calculation of length of elements
Dividing the circumference of the cylinder into 12 equal parts, a =30 0 C
1=
r
sin 300
c'2, = r cos
c3 = r
'6
R
30 0
11 = yR2_ (r + C2)2
=V R2_ (r + e l )2
1'2, 13 = 14= 15 =
V R2_ r2 VR2-(r -c l )2
v' R2_ (r - C2)2
285
INTERSECTION OF CONE AND CYLINDER
THE LINE OF INTERSECTION Divide the circumference of the cylinder on both views into as many equal parts as necessary for the desired accuracy. Draw an element at each division point. Draw circles on plan view with radius r l' r 2' etc. The line of intersection on the plan is determined by the points of intersections of elements and the corresponding circles. Project these points to the elevation. The intersecting points of the projectors and elements will determine the line of intersection on the elevation. The stretched out curvature of the hole in the cone is to be determined by the length of arcs a 2 , a 3 , etc. transferred from the plan view or calculated as exemplified below. The spacing of arcs a 2 , a 3' etc. may be obtained as shown or may be calculated. (See example below). DEVELOPMENT OF PATTERN Draw a straight line of length equal to _the circumference of the cylinder and divide it into the same number of equal parts as the circumference. Draw an element through each division point perpendicular to the line. Determine the length of the elements by projection or by calculating the length of 1 1 , 12 , etc.(See example below). w U
Z
w
cr: w u. ~ ::J
U
cr: u
EXAMPLE for calculation of length of elements
c 6 :::: r sin a: radius, R6
h6 tan {3
arc a 6 :::: 2R6 16::::
JR~ - c~
11'
X -2JL 360 etc.
286
INTERSECTION OF CYLINDER AND SPHERE .1
l
I I
112
R
--------f--- - - - -7- - - - I /
I
I
•
/
-Ii
""-V '
I
;,
\ \. "J\ -_~+_+ -
"""'-I
3
,
~
o
\ ,,'V"'
4
2
I
i
- ~b..-"J-..t- - - - - r - - + 03)(
5
/
I
1'-..,1;
~
R,
Y2 Y,
!J
-/
'/ V
-----
R2
0, : '
:/
~
I
I
OJ w
THE LINE OF INTERSECTI ON Divide the diameter of the cy linder into equal spaces. The horizontal pIa nes through the division points cut elements f rom the cylinder and circles from the sphere. The intersections of the elements with the corr esponding circles are points on the curvature 0 f intersection.
u z w
J
II:
12
w
11
u.
I
~
::>
u
II:
-u
\
\ I
,r--........
i' I
I I
"
I
!
"
'23t567
v
1\ .K~>-+>-~-~ LJ I !J I
I
\\,\
-H
DEVELOPMENT OF THE CYLINDER Draw a straight line of eq ual length to the circumference of the cylinde r and divide it in_ to the same number of parts as the cylinder. The spacing of the division points are determined by the length of arc s of the cylinder. Draw an element through ea ch division point perpendicular to the line. Determine the length of the elements by projection or by calculation of the lengths 0 f I}, 12 , etc.
i
"i
34 ~
T
EXAMPLE for calculation elements.
of
length
of
Calcula te the distances, x I ' x 2 , etc. XI is given; x 2 = XI + r X sin 0/ ,etc.,
VR;- x;, RI = VR2 - y;,
II =
etc_ etc_
Pipe in 2: 1 Ellipsoidal Head The center portion of the head is approximately a spherical segmen t the radius of which is equal 0.9 times th e diameter of the head. When the pipe is wit hin a limit of 0.8 times the diameter of the head the line of intersection and development of the cylinder can be found in the above described manner. Pipe in Flanged and Dished Head Similar way the center portion of the head within the knuckles is a spherical segment the radius of which is equal to the radius of the dish.
287
TRANSITION PIECES connecting cylindrical and rectangular shapes DEVELOPMENT D~
______
~
Divide the circle into equal parts and draw an element at each division point. Find the length of each element by triangulation or by calculation. The elements are the hypotenuse of the triangles one side of which is A-I', A-2', A-3' etc. and the other side is the height of the transition piece.
____- ,
A
A-3' A-2' A-4'
Begin the development on the line I-S and draw the right triangle I-S-A, whose base SA is equal to half the side AD and whose hypotenuse A-I found by triangulation or calculation. Find the points 1, 2, 3 etc. The length of 1-2, 2-3, 3-4 etc. may be taken equal to the cord of the divisions of the top circle if they are small enough for the desired accuracy. Strike an arc with 1 as center and the chord of divisions as radius. With A as center and A-2 as radius draw arc at 2. The intersection of these arcs give the point 2. The points 3, 4 etc. in the curve can be found in a similar manner. EXAMPLE
for calculation of length of elements c=r
X
e=b-c D
~=
cos a
Vf2 + e 2
d=r
X
sin a
f=a-d gr-:2-+-h-=-2
k
=V
LENGTH OF ELEMENTS
In the above described manner can be found the development for transition pieces when: 1. one end is square 2. one or both sides of the rectangle are equal to the diameter of the circle 3. the circular and rectangular planes are eccentric 4. the circular and rectangular planes are not parallel
288
TRANSITION PIECES connecting cylindrical and rectangular shapes
DEVELOPMENT Divide the circle into equal parts and draw an element at each division point. Find the length of each element by triangulation or by calculation. The elements are the hypotenuse of the triangles one side of which is A-I', A-2', A-3' etc. and the other side is the height of the transition piece.
A-1
Begin the development on the line I-S and draw the right triangle I-S-A, whose base SA is equal to half the side AD and whose hypotenuse A-I found by triangulation or calculation. Find the points I, 2, 3 etc. The length of 1-2, 2-3, 3-4 etc. may be taken equal to the cord of the divisions of the top circle if they are small enough for the desired accuracy. Strike an arc with 1 as center and the chord of divisions as radius. With A as center and A-2 as radius draw arc at 2. The intersection of these arcs give the point 2. The points 3, 4 etc. in the curve can be found in a similar manner.
EXAMPLE for calculation of length of elements c = r X cos ex
d == r X sin ex
e = V(b-d)2+(c-a)2 k
= v' e2 + h2
In the above described manner can be found the development for transition pieces when: 1. one end is square 2. one or both sides of the rectangle are equal to the diameter of the circle 3. the circular and rectangular planes are eccentric 4. the circular and rectangular planes are not parallel
289
DIVISION OF CIRCLES INTO EQUAL PARTS The best method for division of a circle into equal parts is to find the length of the chord of a part and measure this length with the divider on the circumference. The length of the chord, C = diameter of
+
circle x c, where c is a factor tabulated below. EXAMPLE: It is required to divide a 20 inch diameter circle into 8 equal spaces. c for 8 spaces from the table: 0.38268
C
= Diameter
x 0.38268
= 20
X
= 7.6536 inches
0.38268
To find the length of chords for any desired number of spaces not shown in the table: 180 C = Diameter X sin number of spaces EXAMPLE: It is required to divide a 100 inch diameter circle into 120 equal parts C
= 100
x sin
~ = 100 120
x sin 1° 30
1
= 100
X
0.0262
= 2.62 inches
Spaces
C
No. of Spaces
C
No. of Spaces
C
No. of Spaces
1 2 3
4
0.00000 1.00000 0.86603 0.70711
26 27 28 29
0.12054 0.11609 0.11196 0.10812
51 52 53 54
0.06153 0.06038 0.05924 0.05814
76 77 78 79
0.04132 0.04079 0.04027 0.03976
5 6 7 8
0.58779 0.50000 0.43388 0.38268
30 31 32 33
0.10453 0.10117 0.09802 0.09506
55 56 57 58
0.05709 0.05607 0.05509 0.05414
80 81 82 83
0.03926 0.03878 0.03830 0.03784
9 10 11 12
0.34202 0.30902 0.28173 0.25882
34 35 36 37
0.09227 0.08964 008716 008481
59 60 61 62
0.05322 0.05234 0.05148 0.05065
84 85 86 87
0.03739 0.03695 0.03652 0.03610
13 14 15 16
0.23932 0.22252 0.20791 0.19509
38 39 40 41
0.08258 0.08047 0.07846 0.07655
63 64 65 66
0.04985 0.04907 0.04831 0.04758
88 89 90 91
0,03569 0.03529 0.03490 0.03452
17 18 19 20
0.18375 0.17365 0.16460 0.15643
42 43 44 45
0.07473 0.07300 0.07134 0.06976
67 68 69 70
0.04687 0.04618 0.04551 0.04487
92 93 94 95
0.03414 0.03377 0.03341 0.03306
21 22 23 24 25
0,14904 0.14232 0.13617 0.13053 0.12533
46 47 48 49 50
0.06824 0.06679 0.06540 0.06407 0.06279
71 72 73 74 75
0.04423 0.04362 0.04302 0.04244 0.04188
96 97 98 99 100
0.03272 0.03238 0.03205 0.03173 0.03141
No. of
C
290 1
,
V ~
e De~
I
2 3 4 5 6 7 8 9 10 II
12 13 14 15 16 17 18 19 20 21 ~~
23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44
45 46 47 48 49 SO 51 52 53 54 55 56 57 58 59 60
h t
~
" ~aa.\\l.S -c~ ./ Area
I
h
C
0.017 0.034 0.052 0.069 0.087 0.104 0.122 0.139 0.157 0.174 0.191 0.209 0.226 0.244 0.261 0.279 0.;'96 0.314 0.331 0.349 0.366 0.383 0.401 0.418 0.436 0.453 0.471 0.488, 0.506 0.523 0.541 0.556 0.575 0.593 0.610 0.628 0.645 0.663 0.680 0.698 0.715 0.733 0.750 0.767 0.785 0.803 0.820 0.838 0.855 0.873 0.890 0.908 0.925 0.942 0.960 0.977 0.995 1.012 1.030 1.047
0.0000 0.0001 0.0003 0.0006 0.0009 0.0013 0.0018 0.0024 0.0030
0.017 0.034 0.052 0.069 0.087 0.104 0.122 0.13'l 0.156 0.174 0.191 0.209 0.226 0.243 0.261 0.27!! 0.295 0.312 0.330 0.347 0.364 0.381 0.398 0.415 0.432 0.449 0.466 0.483 0.500 0.51; 0.534 0.551 0.568 0.584 0.601 0.618 0.634 0.651 0.667 0.684 0.700 0.716 0.733 0.749 0.765 0.781 0.797 0.813 0.829 0.845 0.861 0.877 0.892 0.908 0.923 0.939 0.954 0.970 0.985 1.000
0.003~
0.0046 00054 0.0064 0.0074 O.O()85 0.0097 0.01 JO. 0.0123 0.0137 0.015 I 0.0167 0.0183 0.0200 0.0218 0.0237 0.0256 0.0276 0.0297 0.0318 0.0340 0.0363 0.0387 0.0411 0.0436 0.0462 0.0489 0.0516 0.0544 0.0573 0.0603 0.0633 0.0664 0.0695 0.0728 0.0761 0.0795 0.0829 0.0865 0.0900 0.0937 0.0974 0.1012 0.1051 0.1090 0.1130 0.1171 0.1212 0.1254 0.1296 0.1340
of Seg-
SEGMENTS OF CIRCLES FOR RADIUS = 1 Length of are, height of segment, length of chord, and area of segment for angles from 1 to 180 degrees and radius = 1. For other radii, multiply the values of 1, hand c in the table by the given radius r, and the values for areas, by r2, the square of the radius.
e Deg
U.UWl
1.065 1.082 1.100 1.117 1.134 1.152 1.169 '1.187 U04 1.222 1.239 1.257 1.274 ,1.291 1.309 1.326 77 1.344 78 1.361 79 1.379 80 1.396 81 1.414 82 1.431 83 1.449 84 1.466 85 1.483 86 1.501 87 1.518 88 :1.536 89 1.553 90 1.571 91 1.588 92 1.606 93 1.623 94 1.641 95 1.658 96 1.675 97 1.693 98 1.710 99 1.728 100 1.745 101 1.763 102 1.780 103 1.798 104 1.815 105 1.833 106 1.850 107 1.867 108 1.885 109 1.902 110 1.920 111 1.937 112 1.955 113 1.972 114 1.990 115 2.007 116 2.025 117 2.042 118 2.059 119 2.077 12012.094
0.0000 0.0000 0.0000 0.0000 0.0001 0.0001 0.0002 0.0003 0.0004 0.0005 0.0007 0.0009 0.0012 0.0014 0.0018 0.00;'1 0.0025 0.0030 0.0035 0.0040 0.0046 0.0053 0.0060 0.0068, 0.0077 0.0086 0.0096 0.0106 0.0118 0.0130 0.0142' 0.0156 0.0171 0.0186 0.0202 0.0219 0.0237 0.0256 0.0276 0.02'l7 0.0319. 0.0342 0.0366 0.0391 0.0417 0.0444 0.0473 0.0502 0.0533 0.0564 0.0597 0.0631 0.0667 0.0703 0.0741 0.0780 0.0821 0.0862 0.0905
h
C
of Seg-
e
men!
Deg
0.1384 0.1428 0.1474 0.1520 0.1566 0.1613 0.1661 0.1710 0.1759 0.1808 0.1859 0.1910 0.1961 0.2014 0.2066 0.2120 0.2174 0.2229 0.2284 0.2340 0.2396 0.2453 0.2510 0.2569 0.2627 0.2686 0.2746 0.2807 0.2867 0.2929 0.2991 0.3053 0.3116 0.3180 0.3244 0.3309 0.3374 0.3439 0.3506 0.3572 0.3639 0.3707 0.3775 0.3843 0.3912 0.3982 0.4052 0.4122 0.4193 0.4264 0.4336 0.4408 0.4481 0.4554 0.4627 0.4701 0.4775 0.4850 0.4925 0.5000
1.015 1.030 1.045 1.060 1.075 1.089 1.104 1.118 1.133 1.147 1.161 1.176 1.190 1.204 1.217 1.231 1.245 1.259 1.272 1.286 1.299 1.312 1.325 1.338 1.351 1.364 1.377 1.389 1.402 1.414 1.426 1.439 1.451 1.463 1.475 1.486 1.498 1.509 1.521 1.532 1.543 1.554 1.565 1.576 1.587 1.597 1.608 1.618 1.628 1.638 1.648 1.658 1.668 1.6 T7 1.687 1.696 1.705 1.714 1.723 1.732
0.0950 0.0995 0.1042 0.1091 0.1140 0.1191 0.1244 0.1298 0.1353 0.1410 0.1468 0.1527 0.1588 0.1651 0.1715 0.1780 0.1847 0.1916 0.1985 0.2057 0.2130 0.2204 0.2280 0.2357 0.2436 0.2517 0.2599 0.2682 0.2767 0.2854 0.2942 0.3032 0.3123 0.3215 0.3309 0.3405 0.3502 0.3601 0.3701 0.3803 0.3906 0.4010 0.4117 0.4224 0.4333 0.4444 0.4556 0.4669 0.4784 0.4901 0.5019 0.5138 0.5259 0.5381 0.5504 0.5629 0.5755 0.5883 0.6012 0.6142
Area
1
men! A
Area
1
h
C
A
61 62 63 64 65 66 67 68 69 70 71 7;' 73 74 75 76
of Segmen!
A
121 122 123 124 125 126 127 128 129 130 131 132 133 134 135 136 137 138 139 140 141 142 143 144 145 146 147 148 149 150 151 152 153 154 155 156 157 158 159 160 161 162 163 164 165 166 167 168 169 170 171 172 173 174 175 176 177 178 179 180
2.112 2.129 2.147 2.164 2.182 2.199 2.217 2.234 2.251 2.269 2.286 2.304 2.321 2.339 2.356 2.374 2.391 2.409 2.426· 2.443 2.461 2.478 2.496 2.513 2.531 2.548 2.566 2.583 2.600 2.618 2.635 2.653 2.670 2.688 2.705 2.723 2.740 2.758 2.775 2.792 2.810 2.827 2.845 2.862 2.880 2.897 2.915 2.932 2.950 2.967 2.984 3.002 3.019 3.037 3.054 3.072 3.089 3.107 3.124 3.142
a.SOif! 0.5152 0.5228 0.5305 0.5383 0.5460 0.5538 0.5616 0.5695 0.5774 0.5853 0.5933 0.6013 0.6093 0.6173 0.6254 0.6335 0.6416 0.6498 0.6580 0.6662 0.6744 0.6827 0.6910 0.6993 0.7076 0.7160 0.7244 0.7328 0.7412 0.7496 0.7581 0.7666 0.7750 0.7836 0.7921 0.8006 0.8092 0.8178 0.8264 0.8350 0.8436 0.8522 0.8608 0.8695 0.8781 0.8868 0.8955 0.9042 0.9128 0.9215 0.9302 0.9390 0.9477 0.9564 0.9651 0.9738 0.9825 0.9913 1.000
1.741 1.749 1.758 1.766 1.774 1.782 1.790 1.798 1.805 1.813 1.820 1.827 1.834 1.841 1.848 1.854 1.861 1.867 1.873 1.879 1.885 1.891 1.897 1.902 1.907 1.913 1.918 1.922 1.927 1.932 1.936 1.941 1.945 1.949 1.953 1.956 1.960 1.963 1.%6 1.970 1.973 1.975 1.978 1.980 1.983 1.985 1.987 1.989 1.991 1.992 1.994 1:995 1.996 1.997 1.998 1.999 1.999 2.000 2.000 2.000
0.6273 0.6406 0.6540 0.6676 0.6812 0.6950 0.7090 0.7230 0.7372 0.7514 0.7658 0.7803 0.7950 0.8097 0.8245 0.8395 0.8545 0.8697 0.8850 0.9003 0.9158 0.9313 0.9470 0.9627 0.9786 0.9945 1.0105 1.0266 1.0427 1.0590 1.0753 1.0917 1.1082 1.1247 1.1413 1.1580 1.1747 1.1915 1.2083 1.2252 1.2422 1.2592 1.2763 1.2933 1.3105 1.3277 1.3449 1.3621 1.3794 1.3967 1.4140 1.4314 1.4488 1.4662 1.4836 1.5010 1.5185 1.5359 1.5533 1.5708
291
~
Shell I. S. Diam.
DROP AT THE INTERSECTION OF SHELL AND NOZZLE (Dimension,d Inches)
NOMINAL PIPE SIZE
1'/.t
IV2
2
2V2
3
3V2
4
5
6
8
12
0.0625
0.0625
0.1250
0.1875
0.2500
0.3750
0.4375
0.6875
1.0000
1.8125
14
0.0625
0.0625
0.1250
0.1250 0.2500
0.3125
0.3750
0.5625
0.8125
1.5000
16
0.0625
0.0625
0.0625
0.1250 0.1875
0.2500
0.3125
0.5000
0.6875
1.2500
0.1250 0.1875
0.2500
0.3125
0.4375
0.6250
1.1250
18
0.0625
0.0625
0.0625
20
0.0625
0.0625
0.0625
0.1250 0.1250
0.1875
0.2500
0.3750
0.5625
1.0000
0.1875
0.2500
0.3750
0.5000
0.8750
22
0.0625
0.0625
0.1250 0.1250
24
0.0625
0.0625
0.0625
0.1250
0.1875
0.1875
0.3125
0.4375
0.8125
0.1250
0.1875
0.3125
0.4375
0.7500
26
0.0625
0.0625
0.0625
0.1250
28
0.0625
0.0625
0.0625
0.1250
0.1250
0.1875
0.3125
0.3750
0.6875
0.1875
0.2500
0.3750
0.6250
30
0.0625
0.0625 0.1250
0.1250
32
0.0625
0.0625
0.1250
0.1250
0.1250 0.2500
0.3750
0.5625
34
0.0625
0.0625 0.0625
0.1250
0.1250 0.2500
0.3125
0.5625
36
0.0625
0.0625
0.0625
0.1250
0.1250 0.2500
0.3125
0.5000
0.3125
0.5000
38
0.0625
0.0625
0.0625
0.1250
0.1250 0.1875
40
0.0625
0.0625
0.0625
0.1250
0.1250 0.1875
0.2500
0.5000
0.2500
0.4375
42 48
0.0625
0.0625
0.0625
0.1250
0.1250 0.1875
0.0625
0.0625
0:0625
0.1250 0.1875
0.2500
0.3750
0.1875
0.3750
54
0.0625 0.0625
0.0625
0.1250 0.1250
60
0.0625
0.0625
0.0625
0.0625 0.1250
0.1875
0.3125
0.1875
0.3125
0.1250
0.2500
66
0.0625 0.0625
0.0625
0.0625 0.1250
72
0.0625
0.0625
0.0625 0.1250
78
0.0625
0.0625
0.0625 0.1250
0.1250
0.2500
84
0.0625
0.0625
0.0625 0.1250
0.1250
0.2500
90
0.0625
0.0625
0.0625 0.0625
0.1250
0.1875
96
0.0625
0.0625
0.0625 0.0625
0.1250
0.1875
102
0.0625
0.0625 0.0625
0.1250
0.1875
108
0.0625
0.0625 0.0625
0.1250
0.1875
114
0.0625
0.0625 0.0625
0.1250
0.1875
0.0625
0.1250
120
0.0625 0.0625
126
0.0625 0.0625
0.0625
0.1250
132
0.0625 0.0625
0.0625
0.1250
138
0.0625 0.0625
0.0625
0.1250
144
0.0625 0.0625
0.0625
0.1250
292
~
Shell I. S. Diam.
DROP AT THE INTERSECTION OF SHELL AND NOZZLE (Dimension d, Inches) NOMINAL PIPE SIZE
10
12
3.0625
12
14
16
18
20
22
24
26
30
14
2.5000 4.1250
7.000
16
2.0625
3.1875
4.1250
8.000
18
1.7500 2.6250
3.3750
4.8750
9.0000
20
1.5625
2.3125
2.8750
4.0000
5.6250 10.0000
22
1.3750 2.0625
2 5000
3.4375
4.6875
6.4375
24
1.2500
1.8125
2.2500
3.0625
4.0625
5.3750
26
1.1875
1.6875
2.0625
2.7500
3.6250 4.6875
28
1.0625
1.5000
1.8750
2.5000
3.2500 4.1875
5.3125 6.8125
8.9125
30
1.0000
1.4375
1.7500
2.3125
3.0000
3.8125
4.8125
7.5000
15.0000
11.0000 7.1875 12.0000 I
6.0625 8.0000 13.0000
6.0000
32
0.9375
1.3125
1.6250
2.1250
2.7500
3.5000
4.3750 5.4375
6.6875
10.4375
34
0.8750
1.2500
1.5000
2.0000
2.5625
3.2500
4.0625 4.8125
6.0625
9.0000
36
0.8125 0.8125
1.4375
1.8750
2.4375
3.0625
3.7500 4.5625
5.5625
8.1250
38
0.7500
1.1250
1.3125
1.7500 2.2500
2.8750
3.5000 4.2500
5.1250
7.3125
40
0.7500
1.0625
1.2500
1.6875
2.1250
2.6875
3.3125 4.0000
4.8125
6.7500
42
0.6875
1.0000
1.1250
1.5675
2.0000
2.5625
3.1250 3.7500
4.5000
6.3125
48
0.3125
0.875
1.0625
1.1875
1.7500 2.1875
2.6875
3.1875
3.8125
5.2500
54
0.5625
0.7500
0.9375
1.1875
1.5625
1.9375
2.3125
2.8125
3.3125
4.5625
60
0.4375
0.6875
0.8125
1.0625
1.3750
1.6875
2.1250 2.5000
2.9375
4.0000
66
0.4375
0.6250
0.7500
1.0000
1.2500
1.5625
1.8750 2.2500
2.6875
3.6250
72
0.3750 0.5625
0.6875
0.8750
1.1250
1.4375
1.7500 2.0625
2.4375
3.2500
78
0.3750 0.5000
0.6250
0.8125
1.0625
1.3125
1.5625
1.8750
2.2500
3.0000
84
0.3750 0.5000
0.5625
0.7500
1.0000
1.1875
1.4375
1.7500
2.0625
2.7500
90
0.3125 0.4375
0.5625
0.6875
0.4375
1.1250
1.3750 1.8750
1.9375
2.5625
96
0.3125
0.5000
0.6875
0.8750
1.0625
1.2500 1.5000
1.8125
2.3750
1.1875
1.4375
1.6875
2.2500
1.1250 1.3750
1.5625
2.1250
0.4375
102
0.3125 0.3750
0.5000
0.6250
0.8125
1.0000
108
0.2500 0.3750
0.4375
0.6250
0.7500
0.9375
114
0.2500 0.1875
0.4375
0.5625
0.6875
0.8750
1.062<;
1.2500
1.5000
2.0000
120
0.2500 0.1875
0.4375
0.5625
0.6875
0.8125
1.0000 1.1875
1.4375
1.8750
0.9375
1.1250
1.3750
1.8125
0.9375
1.1250
1.3125
1.7500
126
0.2500 0.3125
0.3750
0.5000
0.6250
0.8125
132
0.2500 0.3125
0.3750
0.5000
0.6250
0.7500
138
0.1825 0.3125
0.3750
0.4375
0.5625
0.7500
0.8750 1.0625
1.2500
1.6250
144
0.1825
0.3125
0.4375
0.5625
0.6875
0.8750 1.0000
1.1875
1.5625
0.3125
293 TABLE FOR LOCATING POINTS ON 2: 1 ELLIPSOIDAL HEADS
R
V'! I
x 1 2 3 4 5 6 x 1 2 3 4 5 6 7 x
1 2 3 4 5 6 7 8 x 1 2 3 4 5 6 7 8 9
D= 12 Y 2.9580 2.8284 2.5980 2.2360 1.6583 0 D= 14 y 3.4641 3.3541 3.1622 2.8722 2.4494 1.8027 0 D= 16 y 3.9686 3.8729 3.7081 3.4641 3.1225 2.6457 1.9364 0 D= 18 y 4.4721 4.3878 4.2426 4.0311 3.7416 3.3541 2.8284 2.0615 0
! x 1 2 3 4 5 6 7 8 9 10 x 1 2 3 4 5 6 7 8 9 10 11
x 1 2 3 4 5 6 7 8 9 10 11
x
~IC jy
T!lngent Lme
From these tables the dimension y can be found if the diameter, D and dimension x are known, or x can be determined if D and yare given. The tables based on the formula: _ 1 VRl h - x 2 ,were y -2' R = the radius of head.
D= 20 Y 4.9749 4.8989 4.7697 4.5825 4.3301 4 3.5707 3 2.1794 0 D= 22 Y 5.4772 5.4083 5.2915 5.1234 4.8989 4.6097 4.2426 3.7749 3.1622 2.2912 0 D= 24 y 5.9791 5.9160 5.8094 5.6568 5.4543 5.1961 4.8734 4.4721 3.9686 3.3166 2.3979
12
0 D= 26 y x 1 6.4807 2 6.4226 3 6.3245 4 6.1846 5 6 6 5.7662 7 5.4772 8 5.1234 9 4.6904 10 4.1533 11 3.4641 12 2.5 13 0 D= 28 y x
1 2 3 4 5 6 7 8 9 10 11 12 13 14
6.9821 6.9282 6.8374 6.7082 6.5383 6.3245 6.0621 5.7445 5.3619 4.8989 4.3301 3.6055 2.5980 0 D;;: 30 y x 1 7.4833 2 7.4330 3 7.3484
7.2284 7.0710 6.8738 6.6332 6.3442 6 5.5901 11 5.0990 12 4.5 13 3.7416 14 2.6925 15 0 D-32 x Y 1 7.9843 2 7.9372 3 7.8581 4 7.7459 5 7.5993 6 7.4162 7.1937 7 8 6.9282 6.6143 9 10 6.245 11 5.8094 12 5.2915 13 4.6636 14 3.8729 15 2.7838 16 0 D=34 x Y 1 8.4852 8.4409 2 3 8.3666 4 8.2613 8.1240 5 7.9529 6 4 5 6 7 8 9 10
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18
7.7459 7.5 7.2111 6.8738 6.4807 6.0208 5.4772 4.8218 4 2.8722 0 D= 36 Y 8.9861 8.9442 8.8741 8.7749 8.6458 8.4852 8.2915 8.0622 7.7942 7.4833 7.1239 6.7082 6.2249 5.6568 4.9749 4.1231 2.9580 0
x 1 2 3 4 5
D= 38 y 9.4868 9.4472 9.3808 9.2870 9.1651
7 8 9 10 11 12 13 14 15 16 17 x
294 TABLE FOR LOCATING POINTS ON 2: 1 ELLIPSOIDAL HEADS (Cont.)
6 7 8 9 10 11 12 13 14 15 16 17 18 19
D=38 9.0138 8.8317 8.6168 8.3666 8.0777 7.7459 7.3654 6.9282 6.4226 5.8309 5.1234 4.2426 3.0413 0 D-40
x
y
1 2 3 4 5 6 7 8 9 10 11
12 13 14 15 16 17 18 19 20
9.9874 9.9498 9.8868 9.7979 9.6824 9.5393 9.3675 9.1651 8.9302 8.6602 8.3516 8 7.5993 7.1414 6.6143 6 5.2678 4.3589 3.1225 0 D=42
x 1 2 3 4 5 6 7
y
10.4881 10.4523 10.3923 10.3078 10.198 10.0623 9.8994
8 9 10 11 12 13 14 15 16 17 18 19 20 21
9.7082 9.4868 9.2330 8.9442 8.6168 8.2462 7.8262 7.3484 6.8007 6.1644 5.4083 4.4721 3.2015 0 D=48
x 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24
y
x 1 2 3 4 5
11.9896 11.9583 11.9059 11.8322 11.7367 11.619 11.4782 11.3137 11.1243 10.9087 10.6654 10.3923 10.0871 9.7467 9.3675 8.9442 8.4705 7.9372 7.3314 6.6332 5.8094 4.7958 3.4278 0 D= 54 y
13.4907 13.4629 13.4164 13.351 13.2665
6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27
13.1624 13.0384 12.8939 12.7279 12.5399 12.3288 12.0934 11.8322 11.5434 11.225 10.8743 10.4881 10.0623 9.5916 9.0691 8.4852 7.8264 7.0710 6.1846 5.0990 3.6400 0 D=60
x 1
1 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23
y
14.9917 14.9666 14.9248 14.8661 14.7902 14.6969 14.586 14.4568 14.3091 14.1421 13.9553 13.7477 13.5185 13.2665 12.9904 12.6886 12.3592 12 11.6082 11.1803 10.7121 10.198 9.6306
24 25 26 27 28 29 30
9 8.2915 7.4833 6.5383 5.3851 3.8405 0 D=66
x 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33
y
16.4924 16.4697 16.4317 16.3783 16.3095 16.225 16.1245 16.0078 15.8745 15.7242 15.5563 15.3704 15.1658 14.9416 14.6969 14.4309 14.1421 13.8293 13.4907 13.1244 12.7279 12.2984 11.8322 11.3248 10.7703 10.1612 9.4868 8.7321 7.8740 6.8738 5.6558 4.0311 0 D= 72
x 1 2
y
17.9931 17.9722
3 4 5 6· 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36
17.9374 17.8885 17.8255 17.7482 17.6564 17.5499 17.4284 17.2916 17.1391 16.9706 16.7854 16.5831 16.3631 16.1245 15.8666 15.5885 15.2889 14.9666 14.6202 14.2478 13.8474 13.4164 12.9518 12.4499 11.9059 11.3137 10.6654 9.9498 9.1515 8.2462 7.1937 5.9160 4.2130 0
D=78
x 1 2 3 4 5 6 7 8 9 10 11
Y 19.4936 19.4743 19.4422 19.3972 19.3391 19.2678 19.1833 19.0853 18.9737 18.8481 18.7083
I
295 TABLE FOR LOCATING POINTS ON 2: 1 ELLIPSOIDAL HEADS (Cont.)
12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39
D=78 18.554 18.3848 18.2003 18 17.7834 17.5499 17.2988 17.0294 16.7407 16.4317 16.1012 15.748 15.3704 14.9666 14.5344 14.0712 13.5739 13.0384 12.4599 11.8322 11.1467 10.3923 9.5524 8.6023 7.5 6.1644 4.3874 0 D=84
x
y
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16
20.994 20.9762 20.9464 20.9045 20.8507 20.7846 20.7063 20.6155 20.5122 20.3961 20.267 20.1246 19.9687 19.799 19.615 19.4165
17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42
19.2029 18.9737 18.7283 18.4662 18.1865 17.8885 17.5713 17.2337 16.8745 16.4924 16.0857 15.6525 15.1905 14.6969 14.1686 13.6015 12.9904 12.3288 11.6082 10.8167 9.9373 8.9442 7.7942 6.4031 4.5552 0 D=90
20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45
20.1556 19.8997 19.6278 19.3391 19.0329 18.7083 18.3644 18 17.6139 17.2047 16.7705 16.3095 15.8193 15.2971 14.7394 14.1421 13.5 12.8062 12.052 11.225 10.3078 9.2736 8.0777 6.6332 4.7169 0 D=96 y
x
y
x
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19
22.4944 22.4778 22.4499 22.4109 22.3607 22.2991 22.2261 22.1416 22.0454 21.9374 21.8174 21.6852 21.5407 21.3834 21.2132 21.0297 20.8327 20.6216 20.3961
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19
23.9948 23.9792 23.9531 23.9165 23.8694 23.8118 23.7434 23.6643 23.5744 23.4734 23.3613 23.2379 23.103 22.9565 22.798 22.6274 22.4444 22.2486 22.0397
20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48
21.8174 21.5812 21.3307 21.0654 20.7846 20.4878 20.1742 19.8431 19.4936 19.1246 18.735 18.3235 17.8885 17.4284 16.9411 16.4241 15.8745 15.2889 14.6629 13.9911 13.2665 12.48 11.619 10.6654 9.5916 8.3516 6.8556 4.8734 0 D= 108
x
y
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16
26.9954 26.9815 26.9583 26.9258 26.884 26.8328 26.7722 26.7021 26.6224 26.533 26.4339 26.3249 26.2059 26.0768 25.9374 25.7876
17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48 49 50 51 52 53 54 x 1 2 3 4 5 6 7
25.6271 25.4558 25.2735 25.0799 24.8747 24.6577 24.4285 24.1868 23.9322 23.6643 23.3827 23.0868 22.7761 22.4499 22.1077 21.7486 21.3717 20.9762 20.5609 20.124f 19.666 19.1833 18.6748 18.1384 17.5713 16.9706 16.3325 15.6525 14.9248 14.1421 13.2947 12.3693 11.3468 10.198 8.8741 7.2801 5.1720 0 D= 120
I
y
29.9958 29.9833 29.9625 29.9333 29.8957 29.8496 29.7951
296 TABLE FOR LOCATING POINTS ON 2: 1 ELLIPOIDAL HEADS (Cont.)
8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48 49 50 51 52 53 54
D=120 29.7321 29.6606 29.5804 29.4915 29.3939 29.2874 29.l719 29.0474 28.9137 28.7706 28.6182 28.4561 28.2843 28.1025 27.9106 27.7083 27.4955 27.2718 27.037 26.7909 26.533 26.2631 25.9808 25.6856 25.3772 25.0549 24.7184 24.367 24 23.6167 23.2164 22.798 22.3607 21.9032 21.4243 20.9225 20.3961 19.8431 19.2614 18.6481 18 17.3133 16.5831 15.8035 14.9666 14.0624 13.0767
55 56 57 58 59 60
x 1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39
10.9896 10.7703 9.3675 7.6811 5.4543 0 0= 132 y
32.9962 32.9848 32.9659 32.9393 32.9052 32.8634 32.8139 32.7567 32.6917 32.619 32.5384 32.45 32.3535 32.249 32.1364 32.0156 31.8865 31.749 31.603 31.4484 31.285 31.1127 30.9314 30.7409 30.541 30.3315 30.1123 29.8831 29.6437 29.3939 29.1333 28.8617 28.5788 28.2843 27.9777 27.6586 27.3267 26.9815 26.6224
40 41 42 43 44 45 46 47 48 49 50 51 52 53 54 55 56 57 58 59 60 61 62 63 64 65 66X
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18
26.2488 25.8602 25.4558 25.035 24.5967 24.1402 23.6643 23.1679 22.6495 22.1077 21.5407 20.9464 20.3224 19.666 18.9737 18.2414 17.4642 16.6358 15.748 14.7902 13.7477 12.5996 11.3137 9.8361 8.0622 5.7227 0 0= 144 Y 35.9965 35.9861 35.9687 35.9444 35.9131 35.8748 35.8295 35.7771 35.7176 35.6511 35.5774 35.4965 35.4083 35.3129 35.2101 35.0999 34.9821 34.8569
19 20 21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48 49 50 51 52 53 54 55 56 57 58 59 60 61 62 63 64 65 66
34.7239 34.5832 34.4347 34.2783 34.1138 33.9411 33.7602 33.5708 33.3729 33.1662 32.9507 32.7261 32.4923 32.249 31.9961 31.7333 31.4603 31.1769 30.8828 30.5778 30.2614 29.9333 29.5931 29.2404 28.8747 28.4956 28.1 025 27.6948 27.2718 26.8328 26.3771 25.9037 25.4116 24.8998 24.367 23.8118 23.2325 22.6274 21.9943 21.3307 20.6337 19.8997 19.1246 18.303 17.4284 16.4924 15.4839 14.3875
67 68 69 70 71 72
13.1814 11.8322 10.2835 8.4261 5.9791 0
NOTE: The curvature of an ellipsoidal head either inside or outside is a true ellipse. The parallel curve of the opposite side is not ellipse and the data of this table are not applicable to locate points on that geometrically undetermined curve. ( especially in the case of heavy walled heads)
297 LENGTH OF ARCS 1. These tables are for locating points on pipes and shells by measuring
the length of arcs. 2. The length of arcs are computed for the most commonly used pipe-
sizes and vessel diameters. 3. The length of arcs for any diameters and any degrees, not shown in the table, can be obtained easily using the values given for diam. 1 or degree 1. 4. All dimensions are in inches. EXAMPLES
A.
270"
90"
O.D. = 30" Nozzle located @ 30° From table the length of arc = 7.8438 in.
180"
B.
O.D. = 30" Nozzle located @ 60° The arc to be measured from the closest centerline The nozzle is @ 30° from the 90°
270"
180"
c. 270"
90"
I.D. = 30" Wall thickness = 3/8", than O.D. = 30 %" Nozzle located @ 300 From table length of 30° arc for dia. 1 = 0.26180 0.26180 x 30.75 = 8.0503 in.
180"
D.
270"
90"
1800
O.D. = 30" Nozzle located @ 22~0 From table length of 1° arc on 30" 0.0. Pipe =0.26180 0.26180 x 22.5 =5.890 in.
298 LENGTH OF ARCS DEGREES Diam. 1
~
N
t il ~
1
5
0.00873
0.04363
10 0.08727
15
20
25
0.13090
0.17453
0.21817
1
0.01148
0.0625
0.1250
0.1875
0.2188
1'h
0.01658
0.0938
0.1563
0.2500
0.3438
30 0.26180
0.2813
0.3438
0.4063
0.5000
2
0.02073
0.0938
0.2188
0.3125
0.4063
0.5313
0.6250
2'h
0.02509
0.1250
0.2500
0.3750
0.5000
0.6250
0.7500 0.9063
3
0.03054
0.1563
0.3125
0.4688
0.6250
0.7500
3'h
0.03491
0.1875
0.3438
0.5313
0.6875
0.8750
1.0625
-< Z
4
0.03927
0.1875
0.4063
0.5938
0.7813
0.9688
1.1875
5
0.04855
0.2500
0.5000
0.7188
0.9688
1.2188
1.4688
~
6
0.05781
0.2813
0.5938
0.8750
1.1563
1.4375
1.7500
8
0.07527
0.3750
0.7500
1.1250
1.5000
1.8750
2.2500
10
0.09381
0.4688
0.9375
1.4063
1.8750
2.3488
2.8125
12
0.11126
0.5625
1.1250
1.6563
2.2188
2.7813
3.3438
12
0.10472
0.5313
1.0625
1.5625
2.0938
2.6250
3.1563
14
0.12217
0.6250
1.2188
1.8438
2.4375
3.0625
3.6563
16
0.13963
0.6875
1.4063
2.0938
2.7813
3.5000
4.1875
Q" Q" ~
0 Z
18
0.15708
0.7813
1.5625
2.3438
3.1563
3.9375
4.7188
20
0.17453
0.8750
1.7500
2.6250
3.5000
4.3750
5.2500
22
0.19199
0.9688
1.9063
2.8750
3.8438
4.8125
5.7500
24
0.20944
1.0625
2.0938
3.1563
4.1875
5.2500
6.2813
26
0.22689
1.1250
2.2813
3.4063
4.5313
5.6875
6.8125
28
0.24435
1.2188
2.4375
3.6563
4.8750
6.0938
7.3488
30
0.26180
1.3125
2.6250
3.9375
5.2500
6.5313
7.8438
32
0.27925
1.6172
2.7813
4.1875
5.5938
6.9688
8.3750
34
0.29671
1.6224
5.9375
7.4063
8.9063
0.31416
1.5625
2.9688 3.1563-
4.4375
36
4.7188
6.2813
7.8438
9.4375
:x::
38
0.33161
1.6563
3.3125
4.9688
6.6250
8.2813
9.9375
Z
40
0.34907
1.7500
3.5000
5.2500
6.9688
8.7188
10.4688
~ ~ ~
42
0.36652
1.8438
3.6563
5.5000
7.3438
9.1563
11.0000
48
0.41888
2.0938
4.1875
6.2813
8.3750
12.5625
:x:: til
54
0.47124
2.3438
4.7188
7.0625
9.4375
10.4688 11.7813
~
60
0.57360
2.6250
5.2500
7.8438
10.4688
13.0938
15.7188 17.2813
til ~
U
0
14.1250
66
0.57596
2.8750
5.7500
8.6250
11.5313
14.4063
72
0.62832
3.1250
6.2813
9.4375
12.5625
15.7188
18.8438
~
78
0.68068
3.4063
6.8125
10.2188
13.6250
17.0313
20.4063
-<
84
0.73304
3.6563
7.3438
11.0000
14.6563
18.3125
22.0000
90
0.78540
3.9375
7.8438
11.7813
15.7188
19.6250
23.5625
96 102
0.83776
4.1875
8.3750
12.5625
16.7500
20.9375
25.1250
0.89012
4.4375
8.9063
13.3438
17.8125
22.2500
26.7188
108
0.94248
4.7188
9.4375
14.1250
18.8438
23.5625
28.9063
114
0.99484
4.9688
9.9375
14.9375
19.9063
24.8750
29.8438
120
1.04720
5.2500
10.4688
15.7188
20.9375
26.1875
31.5313
126
1.09956
5.5000
11.0000
16.5000
22.0000
27.5000
33.0000
132
1.15192
5.7500
11.5313
17.2813
23.0313
28.8125
34.5625
138
1.20428
6.0313
12.0313
18.0625
24.0938
30.0938
36.1250
144
1.25664
6.2813
12.5625
18.8438
25.1250
31.4063
37.6875
~
~ ~
~
~
299 LENGTH OF ARCS DEGREES Diam.
"-l N
r;;
"-l i:I..
35
40
45
90
180
270
360
2.35619
3.14159
1
0.30543
0.78540
1.57080
1 1 V,
0.4063
0.4688
0.5313
1.0313
2.0625
3.0938
0.5938
0.6563
0.7500
1.5000
3.0000
4.4688
5.9688
2
0.7188
0.8438
0.9375
1.8750
3.7188
5.5938
7.4688
2V,
0.8750
1.0000
1.1250
2.2500
4.5313
6.7813
9.0313
3
1.0625
1.2188
1.3750
2.7500
5.5000
8.2500
11.0000
0.34907
0.39270
4.1250
Q:
3%
1.2188
1.4003
1.5625
9.4375
12.5625
4
1.3750
1.5625
1.7813
3.1563 3.5313
6.2813
.J
7.0625
10.5938
14.1250
5
1.6875
1.9375
2.1875
4.3750
8.7500
13.0938
17.4688
6
2.0313
2.3125
2.5938
5.2188
10.4063
15.6250
20.8125 27.0938
< Z
i
0
Z
8
2.6250
3.0938
3.3750
6.7813
13.5625
20.3125
10
3.2813
3.7500
4.2188
8.4375
16.8750
25.3438
33.7813
12
3.9063
4.4375
5.0000
10.0000
20.0313
30.0313
40.0625
12
3.6563
4.1875
4.7188
9.4375
18.8438
29.2813
37.0625
14
4.2813
4.8750
5.5000
11.0000
22.0000
33.0000
43.9688
16
4.8750
5.5938
6.2813
12.5625
25.1250
37.6875
50.2500
18
5.5000
6.2813
7.0313
14.1250
28.2813
42.4063
56.5625
20
6.9688
7.8438
15.7188
31.4063
47.1250
62.8438
22
6.0938 6.7188
7.6875
8.6563
17.2813
34.5625
51.8438
69.1250
24
7.3438
8.3750
9.4375
18.8438
37.6875
56.5625
75.4063
26
7.9375
9.0625
10.2188
20.4063
40.8438
61.2500
81.6875
28
8.5625
9.7813
11.0000
22.0000
43.9688
65.9688
87.9688
30
9.1563
10.4688
11.7813
23.5625
47.1250
70.6875
94.2500
32
9.7813
11.1563
12.5625
25.1250
50.2500
75.4063
100.5313
34
10.3750
11.8750
13.3438
26.7188
53.4060
80.1250
106.8125
36
11.0000
12.5625
14.1250
28.2813
56.5625
84.8125
113.0938
38
11.5938
13.2500
14.9375
29.8438
59.6875
89.5313
119.3750
-
40
12.2188
13.9688
15.7188
31.4063
62.8438
94.2500
125.6563
42
12.8438
14.6563
16.5000
33.0000
65.9688
98.9688
131.9375
48
14.6563
16.7500
18.8438
37.6875
75.4063
113.0938
150.7813
"-l
54
16.5000
18.8438
21.2188
42.4063
84.8125
127.2500
169.6563
til
60
18.3125
20.9375
23.5625
47.1250
94.2500
141.3750
188.5000
0
'-
66
20.1563
23.0313
25.9065
51.8438
103.6875
155.5000
20~.3.~
~
72
22.0000
25.1250
28.2813
56.5625
113.0938
169.6563
226.1875
~
78
23.8125
27.2188
30.6250
61.2500
122.5313
183.7813
245.0313
84
25.6563
29.3125
33.0000
65.9688
131.9375
197.9063
263.9063
90
27.5000
31.4063
35.2438
70.6875
141.3750
212.0625
282.7500
96
29.3125
33.5000
37.6875
75.4063
150.7813
226.1875
301.5938
102
31.1563
35.5938 40.1250
80.1250
160.2188
240.3438
320.4375
til
"-l
::z::
U
Z
.J .J
::z::
"-l
"-l
::!!
-< Q
108
33.0000
37.6875
42.4063
84.8125
169.6563
354.4688
339.2813
114
34.8125
39.7813 49.7813
89.5313
179.0625
268.5938
358.1250
120
36.6563
41.8750 47.1250
94.2500
188.5000
282.7500
377.0000
126
38.5000
43.9688
49.4688
98.9688
197.9063
296.8750
395.8438
132
40.3125
46.0625
51.8438
103.6563
207.3438
311.0313
414.6875
138
42.1563
48.1563
54.1875
108.3750
216.7813
325.1563
433.5313
144
43.9688
50.2500
56.5625
113.0938
226.1875
339.2813
452.3750
300
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia.
}(4 ~2
;(4 ~6 ~2
VB %2
~6 }{2
}i
% Yi6 IJ{2
VB lYa2 Ks 1%'2
Yz IJ{2
Us
1~2
% 2J{2
IY(S 2Ya2
~ 2%2 l~(S 2J{2
VB
2~2
l?{S 3}{2
Circum. .04909 .09818 .14726 .19635 .29452 .39270 .49087 .58905 .68722
Area .00019 .00077 .00173 .00307 .00690 .01227 .01917 .02761 .03758
.78540 .88357 .98175 1.0799 1.1781 l.2763 1.3744 1.4726
.04909 .06213 .07670 .09281 .11045 .12962 .15033 .17257
1.5708 1.6690 1.7671 1.8653 1.9635 2.0617 2.1598 2.2580
.19635 .22166 .24850 .276.88 .30680 .33824 .37122 .40574
2.3562 2.4544 2.5525 2.6507 2.7489 2.8471 2.9452 3.0434
.44179 .47937 .51849 .55914 .60132 .64504 .69029 .73708
Dia. 2. ~6
Va
~6 }i ~6
VB J{6
Yz
Us % lY(6
~ I;J{S
VB
1?{6
3.
k6 VB ;J{s
7'4
~{6
% J{s
Yz
Us % lY(s ~ Ws
VB
I%;
4.
k6 VB
--1.
k6 VB
~6
}i ?{6
% J{6
Yz Yt6
% lk6 % 1;J{6
VB
1~6
3.1416 3.3379 3.5343 3.7306 3.9270 4.1233 4.3197 4.5160 4.7124 4.9087 5.1051 5.3014 5.4978 5.6941 5.8905 6.0868
.7854 .8866 .9940 1.1075 l.2272 1.3530 1.4849 1.6230 1.7671 1.9175 2.0739 2.2365 2.4053 2.5802 2.7612 2.9483
~6
}i Yi6
VB K6
Yz
Yt6
% lY(S ~ 1:l16
VB lYis 5.
h'6
Va
I
Circum.
Area
Dia.
3.1416 3.3410 3.5466 3.7583 3.9761 4.2000 4.4301 4.6664 4.9087 5.1572 5.4119 5.6727 5.9396 6.2126 6.4918 6.7771
~6 }4 Yi6
\
6.2832 6.4795 6.6759 6.8722 7.0686 7.2649 7.4613 7.6576 7.8540 8.0503 8.2467 8.4430 8.6394 8.8357 9.0321 9.2284 9.4248 9.6211 9.8175 10.014 10.210 10.407 10.603 10.799 10.996 11.192 11.388 11.585 11.781 11.977 12.174 12.370
i
7.0686 7.3662 7.6699 7.9798 8.2958 8.6179 8.9462 9.2806 9.6211 9.9678 10.321 10.680 11.045 11.416 11. 793 12.177
12.566 12.763 12.959 13.155 13.352 13.548 13.744 13.941 14.137 14.334 14.530 14.726 14.923 15.119 15.315 15.512
12.566 12.962 13.364 13.772 14.186 14.607 15.033 15.466 15.904 16.349 16.800 17.257 17.728 18.190 18.665 19.147
15.708 15.904 16.101
19.635 20.129 20.629
VB K6
Yz Yt6
% 1!{6 ~ W6
VB
1~i6
6.
Va
}4
VB Yz % ~
Ys
7.
VB
}i
VB Yz % ~
Ys 8.
VB
}i
VB Yz % ~
Ys 9.
Va
}i
VB Yz % ~
Ys 10.
Va
}i
I
Circum.
I
Area
16.297 16.493 16.690 16.886 17.082 17.279 17.475 17.671 17.868 18.064 18.261 18.457 18.653
21.135 21.648 22.166 22.691 23.221 23.758 24.301 24.850 25.406 25.967 26.535 27.109 27.688
18.850 19.242 19.63) 20.028 20.420 20.813 21.206 21.598
28.274 29.465 30.680 31.919 33.183 34.472 35.785 37.122
21.991 22.384 22.776 23.169 23.562 23.955 24.347 24.740
38.485 39.871 41.282 42.718 44.179 45.664 47.173 48.707
25.133 25.525 25.918 26.311 26.704 27.096 27.489 27.882
50.265 51.849 53.456 55.088 56.745 58.426 60.132 61.862
28.274 28.667 29.060 19.452 29.845 30.238 30.631 31.023
63.617 65.397 67.201 69.029 70.882 72.760 74.662 76.589
31.416 31.809 32.201
78.540 80.516 82.516
301
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 10.
%
Circum.
Area 84.541 86.590 88.664 90.763 92.886
34.558 34.950 35.343 35.736 36.128 36.521 36.914 37.306
95.033 97.205 99.402 101.62 103.87 106.14 108.43 110.75
37.699 38.092 38.485 38.877 39.270 39.663 40.055 40.448
113.10 115.47 117.86 120.28 122.72 125.19 127.68 130.19
40.841 41.233 41.626 42.019 42.412 42.804 43.197 43.590
132.73 135.30 137.89 140.50 143.14 145.80 148.49 151.20
43.982 44.375 44.768 45.160 45.553 45.946 46.338 46.731
153.94 156.70 159.48 162.30 165.13 167.99 170.87 173.78
Y2 % %: VB
47.124 47.517 47.909 48.302 48.695 49.087 49.480 49.873
176.71 179.67 182.65 185.66 188.69 191. 75 194.83 197.93
VB
50.265 50.658
201.06 204.22
11.
VB ~
%
Y2 % %: VB 12.
VB
7.i
%
Y2 % %: VB 13.
VB
~
%
Y2 % %: VB 14.
VB ~
%
Y2 % %: VB 15.
VB
~
%
16.
Dia.
Circum.
Area
Dia.
Circum.
~
51.051 51.444 51.836 52.229 52.622 53.014
207.39 210.60 213.82 217.08 220.35 223.65
VB
69.508 69.900 70.293 70.686 71.079 71.471 71.864
384.46 388.82 393.20 397.61 402.04 406.49 410.97
53.407 53.800 54.192 54.585 54.978 55.371 55.763 56.156
226.98 230.33 233.71 237.10 240.53 243.98 247.45 250.95
72.257 72.649 73.042 73.435 73.827 74.220 74.613 75.006
415.48 420.00 424.56 429.13 433.74 438.36 443.01 447.69
56.549 56.941 57.334 57.727 58.119 58.512 58.905 59.298
254.47 258.02 261.59 265.18 268.80 272.45 276.12 279.81
75.398 75.791 76.184 76.576 76.969 77.362 77.754 78.147
452.39 457.11 461.86 466.64 471.44 476.26 481.11 485.98
59.690 60.083 60.476 60.868 61.261 61.654 62.046 62.439
283.53 287.27 291.04 .294.83 298.65 302.49 306.35 310.24
78.540 78.933 79.325 79.718 80.111 80 503 80.896 81.289
490.87 495.79 500.74 505.71 510.71 515.72 520.77 525.84
62.832 63.225 63.617 64.010 64.403 64.795 65.188 65.581
314.16 318.10 322.06 326.05 330.06 334.10 338.16 342.25
81.681 82.074 82.467 82.860 83.252 83.645 84.038 84.430
530.93 536.05 541.19 546.35 551.55 556.76 562.00 567.27
65.973 66.366 66.759 67.152 67.544 67.937 68.330 68.722
346.36 350.50 354.66 358.84 363.05 367.28 371.54 375.83
84.823 85.216 85.608 86.001 86.394 86.786 87.179 87.572
572.56 577.87 583.21 588.57 593.96 599.37 604.81 610.27
69.115
380.13
I
32.594 32.987 33.379 33.772 34.165
Y2 % % VB
(continued)
%
Y2 %
%
VB 17.
VB
~
%
Y2 % % VB 18.
VB ~
%
Y2 % %: VB 19.
VB ~
%
Y2 % % VB 20.
VB
~
%
Y2 % %: VB 21.
VB ~
%
Y2 % %: ~
22.
~
%
Y2 %
%
Ys 23.
VB ~
% Y2 % %: VB 24.
VB
~
%
Y2 % %: VB 25.
VB ~
%
Y2 % %: VB 26.
VB
~
%
Y2 % %: VB 27.
VB
~
%
Y2 %
%
VB
II
Area
302
CIRCUMFERENCES AND AREAS OF CIRCLES
Circum.
Area
87.965 88.357 88.750 89.143 89.535 89.928 90.321 90.713
615.75 621.26 626.80 632.36 637.94 643.55 649.18 654.84
34.
91.106 91.499 91.892 92.284 92.677 93.070 93.462 93.855
660.52 666.23 671.96 677.71 683.49 689.30 695.13 700.98
35.
706.86 712.76 718.69 724.64 730.62 736.62 742.64 748.69
36.
7.i % % %
94.248 94.640 95.033 95.426 95.819 96.211 96.604 96.997 97.389 97.782 98.175 98.567 98.960 99.353 99.746 100.138
754.77 760.87 766.99 773.14 779.31 785.51 791.73 797.98
37.
Ys 7.i % % %
100.531 100.924 101.316 101.709 102.102 102.494 102.887 103.280
804.25 810.54 816.86 823.21 829.58 835.97 842.39 848.83
38.
103.673 104.065 104.458 104.851 105.243 105.636 106.029 106.421
855.30 861.79 868.31 874.85 881.41 888.00 894.62 901.26
39.
Dia. 28.
%
7.i % % % ~ ~
29.
%
7.i % % % ~
VB
30.
%
~ ~
31.
~ ~
32.
Ys
7.i % % % ~
VB
Dia.
%
7.i VB % % ~ ~
%
7.i VB % % ~
VB
Ys 7.i VB Y2 % ~ ~
%
7.i VB
Y2
% ~
Ys
Ys
7.i % Y2
% ~ ~
Circum.
Area
106.814 107.207 107.600 107.992 108.385 108.778 109.170 109.563
907.92 914.61 921.32 928.06 934.82 941.61 948.42 955.25
40.
109.956 110.348 110.741 111.134 111.527 111.919 112.312 112.705
962.11 969.00 975.91 982.84 989.80 996.78 1003.8 1010.8
41.
113.097 113.490 113.883 114.275 114.668 115.061 115.454 115.846
1017.9 1025.0 1032.1 1039.2 1046.3 1053.5 1060.7 1068.0
42.
)16.239 116.632 117.024 117.417 117.810 118.202 118.596 118.988
1075.2 1082.5 1089.8 1097.1 1104.5 1111.8 1119.2 1126.7
43.
119.381 119.773 120.166 120.559 120.951 121.344 121.737 122.129
1134.1 1141.6 1149.1 1156.6 1164.2 1171.7 1179.3 1186.9
122.522 122.915 123.308 123.700 124.093 124.486 124.878 125.271
1194.6 1202.3 1210.6 1217.7 1225.4 1233.2 1241.0 1248.8
Dia.
%
7.i VB % % ~ ~
%
7.i % % % ~ ~
%
7.i % Y2
% ~ ~
Ys
I
7.i VB ~
% ~
Ys
44.
Ys 74 % %
% ~
!
Ys
I
(continued)
Circum.
Area
125.664 126.056 126.449 126.842 127.235 127.627 128.020 128.413
1256.6 1264.5 1272.4 1280.3 1288.2 1296.2 1304.2 1312.2
128.805 129.198 129.591 129.983 130.376 130.769 131.161 131.554
1320.3 1328.3 1336.4 1344.5 1352.7 1360.8 1369.0 1377.2
131.947 132.340 132.732 133.125 133.518 133.910 134.303 134.696
1385.4 1393.7 1402.0 1410.3 1418.6 1427.0 1435.4 1443.8
135.088 135.481 135.874 136.267 136.659 137.052 137.445 137.837
1452.2 1460.7 1469.1 1477.6 1486.2 1494.7 1503.3 1511.9
138.230 138.623 139.015 139.408 139.801 140.194 140.586 140.979
1520.5 1529.2 1537.9 1546.6 1555.3 1564.0 1572.8 1581.6
141.372 141.764 142.157 142.550 142.942 143.335 143.728 144.121
1590.4 1599.3 1608.2 1617.0 1626.0 1634.9 1643.9 1652.9
I
33.
Ys
7.i % Y2 % ~
Ys
Ys
7.i VB
Y2 % ~
Ys
45. I
Ys 74 %
72 % ~
Ys
303
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia.
Circum.
Area
Dia.
46.
144.513 144.906 145.299 145.691 146.084 146.477 146.869 147.262
1661.9 1670.9 1680.0 1689.1 1698.2 1707.4 1716.5 1725.7
52.
147.655 148.048 148.440 148.833 149.226 149.618 lSO.011 150.404
1734.9 1744.2 1753.5 1762.7 1772.1 1781.4 1790.8 1800.1
53.
lSO.796 151.189 151.582 151.975 152.367 152.760 153.153 153.545
1809.6 1819.0 1828.5 1837.9 1847.5 1857.0 1866.5 1876.1
54.
153.938 154.331 154.723 155.116 155.S09 155.902 156.294 156.687
1885.7 1895.4 1905.0 1914.7 1924.4 1934.2 1943.9 1953.7
55.
157.080 157.472 157.865 158.258 158.650 159.043 159.436 159.829
1963.5 1973.3 1983.2 1993.1 2003.0 2012.9 2022.8 2032.8
56.
160.221 160.614 161.007 161.399 161.792 162.185 162.577 162.970
2042.8 2052.8 2062.9 2073.0 2083.1 2093.2 2103.3 2113.5
57.
Va
~
% % % %
Ys 47.
Va
~
% 72 % %
Ys
48.
Ys
7.i % 72 % %
Ys
49.
Ys ~
% % % %
Ys SO.
Ys
7.i % % % %
Ys
51.
Ys
7.i % % % %
Ys
Va
~
% % % %
Ys
Ys
7.i % }1
% %
Ys
Ys
7.i % % % %
Ys
Ys
~
% 72 % %
Ys
Ys
~
% 72 % %
Ys
Ys
7.i % 72 % %
Ys
I
Area
Dia.
163.363 163.756 164.148 164.541 164.934 165.326 165.719 166.112
2123.7 2133.9 2144.2 2154.5 2164.8 2175.1 2185.4 2195.8
58.
166.504 166.897 167.290 167.683 168.075 168.468 168.861 169.253
2206.2 2216.6 2227.0 2237.5 2248.0 2258.5 2269.1 2279.6
59.
16~.646
2290.2 2300.8 2311.5 2322.1 2332.8 2343.5 2354.3 2365.0
60.
170.039 170.431 170.824 171.217 171.609 172.002 172.395 172.788 173.180. 173.573 173.966 174.358 174.751 175.144 175.536
2375.8 2386.6 2397.5 2408.3 2419.2 2430.1 2441.1 2452.0
61.
175.929 176.322 176.715 177.107 177.500 177.893 178.285 178.678
2463.0 2474.0 2485.0 2496.1 2507.2 2518.3 2529.4 2540.6
62.
179.071 179.463 179.856 180.249 180.642 181.034 181.427 181.820
2551.8 2563.0 2574.2 2585.4 2596.7 2608.0 2619.4 2630./
63.
Circum.
I
I
Va ~
VB % %
%
Ys
Ys
7.i % 72 % %
Ys
Ys
~
% 72 % %
Ys
Ys
7.i % % % %
Ys
Ys
7.i % 72 % %
Ys
Ys
7.i % % % %
Ys
I
(continued)
Circum.
I
Area
182.212 182.605 182.998 183.390 183.783 184.176 184.569 184.961
2642.1 2653.5 2664.9 2676.4 2687.8 2699.3 2710.9 2722.4
185.354 185.747 186.139 186.532 186.925 187.317 187.710 188.103
2734.0 2745.6 2757.2 2768.8 2780.5 2792.2 2803.9 2815.7
188.496 188.888 189.281 189.674 190.066 190.459 190.852 191.244
2827.4 2839.2 2851.0 2862.9 2874.8 2886.6 2898.6 2910.5
191.637 192.030 192.423 192.815 193.208 193.601 193.993 194.386
2922.5 2934.5 2946.5 2958.5 2970.6 2982.7 2994.8 3006.9
194.779 195.171 195.564 195.957 196.350 196.742 197.135 197.528
3019.1 3031.3 3043.5 3055.7 3068.0 3080.3 3092.6 }l04.9
197.920 198.313 198.706 199.098 199.491 199.884 200.277 200.669
3117.2 3129.6 3142.0 3154.5 3166.9 3179.4 3191.9 3204.4
304
CIRCUMFERENCES AND AREAS OF CIRCLES
~I 64.
VB ~
%
Yz
% %
Ys
65.
VB }i
%
Yz Ys
% Ys 66.
VB
~
% ~1
Ys
% Ys 67.
VB 3i
%
Yz Ys
% Ys
68.
VB
~
%
Yz
% % VB
69.
VB ~
%
Y2
% % Ys
Circum.
I
Area
Dia.
3217.0 3229.6 3242.2 3254.8 3267.5 3280.1 3292.8 3305.6
70.
204.204 204.596 204.989 205.382 205.774 206.167 206.560 206.952
3318.3 3331.1 3343.9 3356.7 3369.6 3382.4 3395.3 3408.2
7l.
207.345 207.738 208.131 208.523 208.916 209.309 209.701 2lO.094
3421.2 3434.2 3447.2 3460.2 3473.2 3486.3 3499.4 3512.5
72.
210.487 210.879 211.272 211.665 212.058 212.450 212.843 213.236
3525.7 3538.8 3552.0 3565.2 3578.5 3591.7 3605.0 3618.3
73.
213.628 214.021 214.414 214.806 215.199 215.592 215.984 216.377
3631.7 3645.0 3658.4 3671.8 3685.3 3698.7 3712.2 3725.7
74.
216.770 217.163 217.555 217.948 218.341 218.733 219.126 219.519
3739.3 3752.8 3766.4 3780.0 3793.7 3807.3 3821.0 3834.7
75.
201.062 201.455 201.847 202.240 202.633 203.025 203.418 203.811
VB
~
%
Yz
% %
Ys
VB
~
%
Yz Ys
% Ys
VB
~
%
Yz Ys
% Ys
VB ~
%
~
Ys
% Ys
VB
~
%
Yz Ys
% Ys
VB
~
%
Y2 Ys
% VB
I
Area
Dia.
219.911 220.304 220.697 221.090 221.482 221.875 222.268 222.660
3848.5 3862.2 3876.0 3889.8 3903.6 3917.5 3931.4 3945.3
76.
223.053 223.446 223.838 224.231 224.624 225.017 225.409 225.802
3959.2 3973.1 3987.1 4001.1 4015.2 4029.2 4043.3 4057.4
77-
226.195 226.587 226.980 227.373 227.765 228.158 228.551 228.944
4071.5 4085.7 4099.8 4114.0 4128.2 4142.5 4156.8 4171.1
78.
229.336 .229.729 230.122 230.514 230.907 231.300 231.692 232.085
4185.4 4199.7 4214.1 4228.5 4242.9 4257.4 4271.8 4286.3
79.
232.478 232.871 233.263 233.656 234.049 234.441 234.834 235.227
4300.8 4315.4 4329.9 4344.5 4359.2 4373.8 4388.5 4403.1
80.
235.619 236.012 236.405 236.798 237.190 237.583 237.976 238.368
4417.9 4432.6 4447.4 4462.2 4477.0 4491.8
8l.
Circum.
I
4506.7 4521.5
(continued)
Circum.
Area
238.761 239.154 239.546 239.939 240.332 240.725 241.117 241.510
4536.5 4551.4 4566.4 4581.3 4596.3 4611.4 4626.4 4641.5
241.903 242.295 242.688 243.081 243.473 243.866 244.259 244.652
4656.6 4671.8 4686.9 4702.1 4717.3 4732.5 4747.8 4763.1
245.044 245.437 245.830 246.222 246.615 247.008 247.400 247.793
4778.4 4793.7 4809.0 4824.4 4839.8 4855.2 4870.7 4886.2
Yz
248.186 248.579 248.971 249.364 249.757
% %
250.149 250.542
4901.7 4917.2 4932.7 4948.3 4963.9 4979.5 4995.2 5010.9
VB
~
%
Yz
% %
Ys VB
~
%
Yz Ys
% Ys
VB
~
3/
/8
Yz Ys
% Ys
VB
}i
%
Ys Ys ~
%
Yz Ys
% VB
VB
~
%
Y2
% % VB
I
250.935 251.327 251.720 252.113 252.506 252.898 253.291 253.684 254.076
5026.5
5042.3 5058.0 5073.8 5089.6 5105.4 5121.2 5137.1
254.469 254.862 255.254 255.647 256.040 256.433 256.825 257.218
5153.0 5168.9 5184.9 5200.8 5216.8 5232.8 5248.9 5264.9 I
305
CIRCUMFERENCES AND AREAS OF CIRCLES
~1~cum·I~~_
Dia.
Circum.
82.
257.611 258.003 258.396 258.789 259.181 259.574 259.967 260.359
5281.0 5297.1 5313.3 5329.4 5345.6 5361.8 5378.1 5394.3
88.
260.752 261.145 261.538 261.930 262.323 262.716 263.108 263.501
5410.6 5426.9 5443.3 5459.6 5476.0 5492.4 5508.8 5525.3
89.
263.894 264.286 264.679 265.072 265.465 265.857 266.250 266.643
5541.8 5558.3 5574.8 5591.4 5607.9 5624.5 5641.2 5657.8
90.
267.035 267.428 267.821 268.213 268.606 268.999 269.392 269.784
5674.5 5691.2 5707.9 5724.7 5741.5 5758.3 5775.1 5791.9
91.
270.177 270.570 270.962 271.355 271. 748 272.140 272.533 272.926
5808.8 5825.7 5842.6 5859.6 5876.5 5893.5 5910.6 5927.6
92.
273.319 273.711 274.104 274.497 274.889 275.282 275.675 276.067
5944.7 5961.8 5978.9 5996.0 6013.2 6030.4 6047.6 6064.9
VB 34 %
Yz
%
% :Va
Area
1- - - -
VB 74 %
Yz
%
% :Va
---- - ---83.
Ys 74 %
Yz
%
% :Va --84.
VB 34 %
Yz
%
% :Va 85.
VB 34 %
Yz
%
Ys 74 %
Yz
% %
Ys
VB 74 %
Yz
% % :Va VB 34 %
Yz
% %
% :Va --- ---- ---86.
VB 74 %
7:!
%
% :Va
87.
VB 34 %
Yz
%
%1 :Va
I
Ys Ys
74 %
Yz
% %
Dia.
Circum.
Are.
295.310 295.702 296.095 296.488 296.881 297.273 297.666 298.059
6939.8 6958.2 6976.7 6995.3 7013.8 7032.4 7051.0 7069.6
298.451 298.844 299.237 299.629 300.Q22 300.415 300.807 301.200
7088.2 7106.9 7125.6 7144.3 7163.0 7181.8 7200.6 7219.4
301.593 301.986 302.378 302.771 303.164 303.556 303.949 304.342
7238.2 7257.1 7276.0 7294.9 7313.8 7332.8 7351.8 7370.8
304.734 305.127 305.520 305.913 306.305 306.698 307.091 307.483
7389.8 7408.9 7428.0 7447.1 7466.2 7485.3 7504.5 7523.7
307.876 308.269 308.661 309.054 309.447 309.840 310.232 310.625
7543.0 7562.2 7581.5 7600.8 7620.1 7639.5 7658.9 7678.3
311.018 311.410 311.803 312.196 312.588 312.981 313.374 313.767
7697.7 7717.1 7736.6 7756.1 7775.6 7795.2 7814.8 7834.4
276.460 276.853 277.246 277.638 278.031 278.424 278.816 279.209
6082.1 6099.4 6116.7 6134.1 6151.4 6168.8 6186.2 6203.7
94.
279.602 279.994 280.387 280.780 281.173 281.565 281.958 282.351
6221.1 6238.6 6256.1 6273.7 6291.2 6308.8 6326.4 6344.1
95.
282.743 283.136 283.529 283.921 284.314 284.707 285.100 285.492
6361.7 6379.4 6397.1 6414.9 6432.6 6450.4 6468.2 6486.0
96.
285.885 286.278 286.670 287.063 287.456 287.848 288.241 288.634
6503.9 6521.8 6539.7 6557.6 6575.5 6593.5 6611.5 6629.6
97.
289.027 289.419 289.812 290.205 290.597 290.990 291.383 291.775
6647.6 6665.7 6683.8 6701.9 6720.1 6738.2 6756.4 6774.7
98.
292.168 292.561 292.954 293.346 293.739 294.132 294.524 294.917
6792.9 6811.2 6829.5 6847.8 6866.1 6884.5 6902.9 6921.3
99.
VB 34 %
Yz
%
% :Va Ys
74 %
Yz
% % Ys
VB 74 %
Yz
% % :Va VB 74 %
Yz
% % Ys Ys
34 %
7:!
% %
Ys - - - - - - - ----93.
VB 74 %
Yz
% %
Ys
(continued)
Ys
Ys
74 %
Yz
%
% Ys
306
CIRCUMFERENCES AND AREAS OF CIRCLES ( continued)
Dia. 100.
Ys
!4 %
Yz
% % :Va 101.
Ys !4 %
Yz
% % :Va 102.
Ys
!4
%
Yz
% % :Va
103.
VB !4 %
Yz
% % :Va 104.
Ys
!4 %
Yz
% % :Va --lOS.
Ys
!4 %
Yz
% % :Va
Circum.
Area
Dia.
314.16 314.55 314.95 315.34 315.73 316.12 316.52 316.91
7854 7873 7893 7913 7933 7952 7972 7992
106.
317.30 317.69 318.09 318.48 318.87 319.27 319.66 320.05
8012 8032 8052 8071 8091 8111 8131 8151
107.
320.44 320.84 321.23 321.62 322.Dl 322.41 322.80 323.19
8171 8191 8211 8231 8252 8272 8292 8312
108.
323.59 323.98 324.37 324.76 325.16 325.55 325.94 326.33
8332 8352 8372 8393 8413 8434 8454 8474
109.
326.73 327.12 327.51 327.91 328.30 328.69 329.08 329.48
8495 8515 8536 8556 8577 8597 8618 8638
110.
329.87 330.26 330.65 331.05 331.44 331.83 332.22 332.62
8659 8679 8700 8721 8741 8762 8783 8804
111.
Circum.
I
Area
Dia.
333.01 333.40 333.80 334.19 334.58 334.97 335.37 335.76
8825 8845 8866 8887 8908 8929 8950 8971
112.
336.15 336.54 336.94 337.33 337.72 338.12 338.51 338.90
8992 9014 9035 9056 9077 9098 9119 9140
113.
339.29 339.69 340.08 340.47 340.86 341.26 341.65 342.04
9161 9183
114.
9225 9246 9268 9289 9310
342.43 }42.83 343.22 343.61 344.01 344.40 344.79 345.18
9331 9353 9374 9396 9417 9439 9460 9481
115.
9503
116.
% % Ys
345.58 345.97 346.36 346.75 347.15 347.54 347.93 348.33
9525 9546 9568 9589 9611 9633 9655
VB
348.72 349.11
Yz
349.90 350.29
Ys
351.Q7 351.47
Ys !4 %
Yz
% % :Va
Ys !4 %
Yz
% % :Va
Ys !4 %
Yz
% ~4
Ys
VB !4 %
Yz
% %
:1
Ys !4 %
Yz
~ ~
% %
I
349.50 350.68
9677 9698 9720 9742 9764 9786 9808 9830
Circum.
Area
351.86 352.25 352.65
~
353.04
% % :Va
353.43 353.82 354.22 354.61
9852 9874 9897 9919 9941 9963 9985 10007
355.00 355.39 355.79 356.18 356.57 356.96 357.36 357.75
10029 10052 10074 10097 10119 10141 10163 10185
358.14 358.54 358.93 359.32 359.71 360.11 360.50 360.89
10207 10230 10252 10275 10297 10320 10342 10365
361.28 361.68 362.07 362.46 362.86 363.25 363.64 364.03
10387 10410 10432 10455
364.43 364.82 365.21 365.60 366.00 366.39 366.78 367.18
10568 10590 106l} 10636 10659 10682 10705 10728
367.57 367.96 368.35 368.75 369.14 369.53 369.92 370.32
10751 10774 10798 10821 10844 10867 10890 10913
Ys
!4
Yz
VB
~ ~
Yz
% % Ys
VB
~ ~
9204
I
Yz
% % Ys
VB
~ ~
Yz
% % Ys
VB !4 %
Yz
% % Ys
117.
VB !4 %
Yz
% % Ys
10477 10500 10522 10545
307
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 118.
Ys ~
% ~
% ~
Ys
119.
Ys
~
% ~'2
% ~
Ys 120.
Ys ~
% ~
% ~
Ys 121.
Ys ~
%
~
% ~
Ys 122.
Ys
~
% ~
%
~.
Ys 123.
Ys ~
% Y2 % ~
Ys
I
Circum.
Area
370.71 371.11 371.49 371.89 372.28 372.67 373.Q7 373.46
10936 10960 10983 11007 11030 11053 11076 11099
373.85 374.24 374.64 375.03 375.42 375.81 376.21 376.60
11122 11146 11169 11193 11216 11240 11263 11287
125.
376.99 377.39 377.78 378.17 378.56 378.96 379.35 379.74
11310 11334 11357 11381 11404 11428 11451 11475
126.
380.13 380.53 380.92 381.31 381.70 382.10 382.49 382.88
11499 11522 11546 11570 11594 11618 11642 11666
127.
383.28 383.67 384.06 384.45 384.85 385.24 385.63 386.02
11690 11714 11738 11762 11786 11810 11834 11858
128.
386.42 386.81 387.20 387.60 387.99 388.38 388.77 389.17
11882 11907 11931 11956 11980 12004 12028 12052
129.
Dia.
I Circum.
~I Ys ~
%
~
% ~
Ys Ys
~
% Y2
% ~
Ys Ys ~
% ~
% ~
Ys
.-
Ys ~
% Y2 % ~
Ys
Ys
~
% Y2 % ~
Ys VB ~
% Y2 % ~
Ys
Area
( continued)
~I Circum~j~_a_
389.56 389.95 390.34 390.74 391.13 391.52 391.92 392.31
12076 12101 12125 12150 12174 12199 12223 12248
130.
392.70 393.09 393.49 393.88 394.27 394.66 395.06 395.45
12272 12297 12321 12346 12370 12395 12419 12444
131.
395.84 396.23 396.63 397.02 397.41 397.81 398.20 398.59
12469 12494 12518 12543 12568 12593 12618 12643
132.
398.98 399.38 399.77 400.16 400.55 400.95 401.34 401.73
12668 12693 12718 12743 12768 12793 12818 12843
133.
402.13 402.52 402.91 403.30 403.70 404.09 404.48 404.87
12868 12893 12919 12944 12970 12995 13020 13045
134.
405.27 405.66 406.05 406.44 406.84 407.23 407.62 408.02
13070 13096 13121 13147 13172 13198 13223 13248
135.
Ys
~
% Y2
YS ~
Ys Ys
~
% Y2 % ~
Ys
Ys
~
% ~
% ~
Ys
Ys ~
% Y2
% ~
Ys
Ys ~
%
~
% ~
Ys VB ~
VB
Y2 % ~
Ys
408.41 408.80 409.19 409.59 409.98 410.37 410.76 411.16
13273 13299 13324 13350 13375 13401 13426 13452
411.55 411.94 412.34 412.73 413.12 413.51 413.91 414.30
13478 13504 13529 13555 13581 13607 13633 13659
414.69 415.08 415.48 415.87 416.26 416.66 417.05 417.44
13685 13711 13737 13763 13789 13815 13841 13867
417.83 418.23 418.62 419.01 419.40 419.80 420.19 420.58
13893 13919 13946 13972 13999 14025 14051 14077
420.97 42l.37 421.76 422.15 422.55 422.94 423.33 423.72
14103 14130 14156 14183 14209 14236 14262 14288
424.12 424.51 424.90 425.29 425.69 426.08 426.47 426.87
14314 14341 14367 14394 14420 14447 14473 14500
308
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 136.
VB
}i
% Y2
%
%;
Ys 137.
VB
}i
% Y2 % %;
Ys 138.
VB
}i
% Y2 % %
Ys
13~.
~il ~4
3/ "8
H %
% Ys 140.
VB
~
~/8
Y2 % %;
Ys H.
Ys
~
% Y2 % % Ys
I Circum. I
Area
427.26 427.65 428.04 428.44 428.83 429.22 429.61 430.01
14527 14553 14580 14607 14633 14660 14687 14714
142.
430.40 430.79 431.19 431.58 431.97 432.36 432.76 433.15
14741 14768 14795 14822 14849 14876
143.
Dia.
VB ~
% H % % Ys
Ys
~
% H %
14903
%;
14930
Ys
I Circum.
Area
Dia.
446.11 446.50 446.89 447.29 447.68 448.07 448.46 448.86
15837 15865 15893 15921 15949 15977 16005 16033
148.
449.25 449.64 450.03 450.43 450.82 451.21 451.61 452.00
16061 16089 16117 16145 16173 16201 16229 16258
149.
452.39 452.78 453.18 453.57 453.96 454.35 454.75 455.14
16286 16314 16342 16371 16399 16428 16456 16485
150.
455.53 -455.93 456.32 456.71 457.10 457.50 457.89 458.28
16513 16542 16570 16599 16627 16656 16684 16713
151.
458.67 459.07 459.46 459.85 460.24 460.64 461.03 461.42
16742 16770 16799 16827 16856 16885 16914 16943
152.
461.82 462.21 462.60 462.99 463.39 463.78 464.17 464.56
16972 17000 17029 17058 17087 17116 17145 17174
153.
VB }i
% Y2 %
%;
Ys
VB
~
% Y2 % %;
Ys
--144.
433.54 433.93 434.33 434.72 435.11
14957 14984
435.50 435.90 436.29
15094 15121 15148
436.68 437.08 437.47 437.86 438.25 438.65 439.04 439.43
15175 15203 15230 15258 15285 15313 15340 15367
145.
439.82 440.22 440.61 441.00 44l.40 441.79 442.18 442.57
15394 15422 15449 15477 15504 15532 15559 15587
146.
442.97 443.36 443.75 444.14 444.54 444.93 445.32 445.72
15615 15642 15670 15697 15725 15753 15781 15809
147.
VB
}i
15012 15039 15067
I
% Y2 % % Ys
VB
}i
% Y2 % %
Ys
Ys }i
%
H %
%;
Ys
VB
}i
% Y2 % % Ys
Ys
~
% Y2 % %
Ys Ys
~
% Y2 % %
Ys VB
}i
% Y2 % %;
Ys
VB
}i
% Y2 % %;
51
( &onl;nued)
Circum.
Area
464.96 465.35 465.74 466.14 466.53 466.92 467.31 467.71
17203 17232 17262 17291 17321 17350 17379 17408
468.10 468.49 468.88 469.28 469.67 470.06 470.46 470.85
17437 17466 17496 17525 17555 17584 17614 17643
471.24 471.63 472.03 472.42 472.81 473.20 473.60 473.99
17672 17702 17731 17761 17790 17820 17849 17879
474.38 474.77 475.17 475.56 475.95 476.35 476.74 477.13
17938 17967 17997 18026 18056 18086 18116
477.52 477.92 478.31 478.70 479.09 479.49 479.88 480.27
18146 18175 18205 18235 18265 18295 18325 18355
480.67 481.06 481.45 481.84 482.24 482.63 483.02 483.41
18385 18415' 18446 18476 18507 18537 18567 18597
17908
I
309
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 154.
VB !-i %
Y2 % % VB 155.
VB X %
Y2
VB % VB 156.
VB !-i %
Y2 % % VB 157.
VB X %
Y2 % % VB
158.
VB X %
Y2 % % VB
159.
VB X %
Y2 % % VB
Circum.
Area
483.81 484.20 484.59 484.99 485.38 485.77 486.16 486.56
i8627 18658 18688 18719 18749 18779 18809 18839
160.
486.95 487.34 437.73 488.13 488.52 488.91 489.30 489.70
18869 18900 18930 18961 18991 19022 19052 19083
161.
490.09 490.48 490.88 491.27 491.66 492.05 492.45 492.84
19113 19144 19174 19205 19235 19266 19297 19328
162.
493.23 493.62 494.02 494.41 494.80 495.20 495.59 495.98
19359 19390 19421 19452 19483 19514 19545 19576
163.
496.37 496.77 497.16 497.55 497.94 498.34 498.73 499.12
19607 19638 19669 19701 19732 19763 19794 19825
164.
499.51 499.91 500.30 500.69 S01.09 S01.48 S01.87 S02.26
19856 19887 19919 19950 19982 20013 20044 20075
165.
Dia.
VB !-i %
Y2 % % :Va VB X %
Y2 % % VB VB !-i %
Y2 % % VB VB X %
Y2 % % VB
VB X %
Y2 % % VB VB X %
Y2 % % VB
I Circum.
I
Area
Dia.
S02.66 S03.05 S03.44 S03.83 S04.23 S04.62 505.01 S05.41
20106 20138 20169 20201 20232 20264 20295 20327
166.
S05.80 506.19 506.58 506.98 S07.37 507.76 508.15 508.55
20358 20390 20421 20453 20484 20516 20548 20580
167.
508.94 S09.33 S09.73 510.12 510.51 510.90 511.30 511.69
20612 20614 20675 20707 20739 20771 20803 20835
168.
512.08 512.47 512.87 513.26 513.65 514.04 514.44 514.83
20867 _ 20899 20931 20964 20996 21028 21060 21092
169.
515.22 515.62 516.01 516.40 516.79 517.19 517.58 517.97
21124 21157 21189 21222 21254 21287 21319 21351
170.
518.36 518.76 519.15 519.54 519.94 520.33 520.72 521.11
21383 21416 21448 21481 21513 21546 21578 21610
171.
Va
X % Y2 % % :Va VB X %
Y2
VB % VB VB X %
Y2 % % VB VB X %
Y2 % % VB VB X %
Y2 % % VB VB X %
Y2 % % VB
I
(continued)
Circum.
I
Area
521.51 521.90 522.29 522.68 523.08 523.47 523.86 524.26
21642 21675 21707 21740 21772 21805 21838 21871
524.65 525.04 525.43 525.83 526.22 526.61 527.00 527.40
21904 21937 21969 22002 22035 22068 22101 22134
527.79 528.18 528.57 528.97 529.36 529.75 530.15 530.54
22167 22200 22233 22266 22299 22332 22366 22399
530.93 531.32 531.72 532.11 532.SO 532.89 533.29 533.68
22432 22465 22499 22532 22566 22599 22632 22665
534.07 534.47 534.86 535.25 535.64 536.04 536.43 536.82
22698 22731 22765 22798 22832 22865 22899 22932
537.21 537.61 538.00 538.39 538.78 539.18 539.57 539.96
22966 22999 23033 23066 23100 23133 23167 23201
310
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 172-
Ys ~
%
Y2
% ~
Ys
173.
Ys ~
%
Y2
% ~
Ys 174.
Ys
~
%
Y2
% ~
Ys 175.
Ys
~
%
Yz % 34 Ys 176.
Ys
~
%
Y2
% ~
Ys
177.
Ys ~
%
Y2
% ~
Ys
I Circum. 540.36 540.75 541.14 541.53 541.93 542.32 542.71 543.10
I
Area 23235 23268 23302 23336 23370
Dia. 178.
Ys ~
%
Y2
%
23404
~
23438 23472
Ys
543.50 543.89 544.28 544.68 545.Q7 545.46 545.85 546.25
23506 23540
546.64 547.03 547.42 547.82 548.21 548.60 549.00 549.39
23779 23813 23848 23882 23917 23951 23985
549.78 550.17 550.57 550.96 551.35 551.74 552.14 552.53
24053 24087 24122 24156 24191 24225 24260 24294
552.92 553.31 553.71 554.10 554.49 554.89 555.28 555.67
24329 24363 24398 24432 24467 24501 24536 24571
182.
556.06 556.46 556.85 557.24 557.63 558.03 558.42 558.81
24606
183.
179.
Ys
~
23575 23609 23643 23677 23711 23745
%
Y2
% ~
Ys 180.
Ys
~
%
Y2
% ~
Ys
24019
24640 24675 24710 24745 24780 24815 24850
181.
Ys
~
%
Y2
% ~
Ys
Ys ~
Vs
Y2
% ~
Ys
Ys
~
%
Y2
% ~
Ys
Circum.
Area
559.21 559.60 559.99 560.38 560.78 561.17 561.56 561.95
24885 24920 24955 24990 25025 25060 25095 25130
184.
562.35 562.74 563.13 563.53 563.92 564.31 564.70 565.10
25165 25200 25236 25271 25307 25342 25377 25412
185.
565.49 565.88 566.27 566.67 567.06 567.45 567.84 568.24
25447 25482 25518 25553 25589 25624 25660 25695
186.
568.63 -569.02 569.42 569.81 570.20 570.59 570.99 571.38
25730 25765 25801 25836 25872 25908 25944 25980
187.
571.77 572.16 572.56 572.95 573.34 573.74 574.13 574.52
26016 26051 26087 26122 26158 26194 26230 26266
188.
574.91 575.31 575.70 576.09 576.48 576.88 577.27 577.66
--
26302 26338 26374 26410 26446 26482 26518 26554
Dia.
Ys
~
%
Y2
% ~
Y8 Ys
~
%
Y2
% ~
Ys Ys ~
%
Yz
% ~
Ys Ys ~
%
Y2
% ~
Ys Ys
~
Vs
Y2
% ~
Ys
189.
Ys ~
%
Y2
I
(continued)
Circum. 578.05 578.45 578.84 579.23 579.63 580.02 580.41 580.80
26590 26626 26663 26699 26736 26772 26808 26844
581.20 581.59 581.98 582.37 582.77 583.16 583.55 583.95
26880 26916 26953 26989 27026 27062 27099 27135
584.34 584.73 585.12 585.52 585.91 586.30 586.59 587.09
27172 27208 27245 27281 27318 27354 27391 27428
587.48 587.87 588.27 588.66 589.05 589.44 589.84 590.23
27465 27501 27538 27574 27611 27648 27685 27722
590.62 591.01 591.41 591.80 592.19 592.58 592.98 593.37
27759 27796 27833 27870 27907 27944 27981 28018
593.76 594.16 594.55 594.94 595.33
28055 28092 28130 28167 28205 28242 28279 28316
%
~5.73
Ys
596.12 596.51
~
Area
311
CIRCUMFERENCES AND AREAS OF CIRCLES
Dia. 190.
Ys
~4
%
Y2 % :Ji Ys 191.
Ys
Ii %
Y2 % :Ji Ys 192.
Ys ~
% Y2 % :Ji Ys 193.
VB
~
% Yz % % Ys 194.
Ys
!4 %
Yz
% :Ji
Ys
195.
Ys
!4 %
Yz
% % Ys
Circum.
I
Area
Dia.
596.90 597.29 597.68 598.08 598.47 598.86 599.25 599.64
28353 28390 28428 28465 28503 28540 28578 28615
196.
600.04 600.44 600.83 601.22 601.62 602.01 602.40 602.79
28652 28689 28727 28764 28802 28839 28877 28915
197.
603.19 603.58 603.97 604.36 604.76 605.15 605.54 605.94
28953 28990 29028 29065 29103 29141 29179 29217
198.
606.33 606.72 607.11 607.51 607.90 608.29 608.58 609.08
29255 29293 29331 29369 29407 29445 29483 29521
199.
609.47 609.86 61026 610.65 61l.05 611.43 611.83 612.29
29559 29597 29636 29674 29713 29751 29789 29827
200.
612.61 613.00 613.40 613.79 614.18 614.57 614.97 615.36
29865 29903 29942 29980 30019 30057
201.
30096 30134
Ys !4 %
Y2 % % Ys
Ys U
% Y2 % :Ji VB
Ys
!4 %
Y2 % :Ji Ys
Ys
!4 % ~2
% :Ji
Ys Ys ~
% Y2 % :Ji Ys
Ys
!4 %
Yz
% % Ys
I Circum. I
Area
Dia.
( continued)
Circum.
I
Area
634.60 635.00 635.40 635.79 636.18 636.57 636.97 637.36
32047 32086 32126 32166 32206 32246 32286 32326
637.74 638.15 638.54 638.93 639.32 639.72 640.11 640.50
32366 32405 32445 32485 32525 32565 32605 32645
Ys
640.88 641.28 641.67 642.07 642.46 642.85 643.24 643.63
32685 32725 32766 32806 32846 32886 32926 32966
VB !4 % Y2 % % Ys
644.03 644.43 644.82 645.21 645.61 646.00 646.39 646.78
33006 33046 33087 33127 33168 33208 33249 33289
647.17 647.57 647.96 648.35 648.75 649.14 649.53 649.93
33329 33369 33410 33450 33491 33531 33572 33613
650.31 650.71 651.10 651.50 651.89 652.28 652.57 653.07
33654 33694 33735 33775 33816 33857 33898 33939
615.75 616.15 616.54 616.93 617.32 617.72 618.11 618.50
30172 30210 30249 30287 30326 30364 30403 30442
202.
618.89 619.29 619.68 620.08 620.47 620.86 621.25 621.64
30481 30519 30558 30596 30635 30674
203.
622.04 622.44 622.83 623.22 623.62 624.01 624.40 624.79
30791 30830 30869 30908 30947 30986 31025 31064
204.
625.18 625.58 625.97 626.36 626.76 627.15 627.54 627.94
31103 31142 31181 31220 31260 31299 31338 31377
205.
628.32 628.72 629.11 629.51 629.90 630.29 630.58 63l.08
31416 31455 31495 31534 31574 31613 31653 31692
206.
63l.46 631.86 632.26 632.65 633.05 633.43 633.83 634.29
31731 31770 31810 31849 31889 31928 31968 32007
207.
Ys !4 %
Y2 % % Ys
Ys
~
% Y2 % % Ys
30713 30752
Ys
!4 %
Yz % :Ji
Ys !4 %
Yz
% % Ys
Ys
!4 %
Yz
% % Ys
312
DAVIT l
I
3"
I I __ -~3" 1~--+---4.\ ~~
I
! ~--
I
CENTER LINE
-4~~:.y-c~
I 4-_ _-4111......
~
FLANGE
1u--~
..0 ..
-tr
--,
-
".
'~,
~
-I
__
.~
EYE BOLT _ _ ,
/DAVITARM ,
1 I,
r-
,/""
..1
I
1
IVSLEEVE
Tt
I
STIFFENIN:'Ai"
n
U BAR-:tj
I
'
1/2 "
PLATE
\
i
-1
i
'\t
I
i
I
~5/8
I
====-
I : !!. . . .
if'
I
SLEEVE
=i
FOR VERTICAL OPENING
FOR HORIZONTAL OPENING
All material carbon steel All welds 3/8" continuous filet weld The davit has been tested against excessive deflection Using davit less room is required than with the use of hinge For frequently used opening, davit is preferred to hinge
FLANGE RATING SIZE
+
\
T
I. 2. 3. 4. 5.
PLATE
_+-+-_1-1/2"
H"D)~ ''"~-or~l~ht,;--4
NOTES:
'-IH+--
'I/~
OAVIT ARM
'\,
"
U'BAR-::Jj hSTIFFENING ..... ,
/' RING
.I'~
-HIt- , - _ .
1\
'::::-;:::
'\ ' l
i
,_'1'2"
EYE BOLT _ _
3"
300-
900 -
12 14 16 18 20 24 12 14 16 18 20 24 12 14 16 18 20 24 12 14 16 18 20 24
NO. OF LIST
1 1 1 1 1 1 1 1 1 1 2 2 1 1 2 2 2 2
DAVIT ARM SLEEVE EYE-BOLT V-BAR
LIST -I 1-1/2"-XH PIPE 2"-XH PIPE 5/8 q, 5/8 q,
RING PLATE HANDLE
5/8 5/8 5/8
STIFFENER
--
q,
LIST -2 2"-XXH PIPE 2-1/2" -STD PIPE
3/4 3/4 3/4 3/4 3/4
1 1 2 2 2 LIST - 3 2"-XXH PIPE 2-1/2"-STD PIPE
q, q,
1" I"
q,
1" I"
q, q,
I"
--
3/8"
q,
3
313
FIXED STAIR Conforms to the requirements of OCCUPATIONAL SAFETY AND HEALTH (OSHA) STANDARDS
Fixed stairs will be provided where operations necessitate regular travel between levels. Fixed stairways shall be designed to carry a load of five times the normal live load anticipated but never less than to carry a moving concentrated load of 1,000 pounds. Minimum width: 22 inches Angle of stairway rise to the horizontal: 30 to 50 degrees. Railings shall be provided on the open sides of all exposed stairways. Handrails shall be provided on at least once side of closed stairways, preferably on the right side descending. Each tread and nosing shall be reasonably slip-resistant. Stairs having treads of less than nine-inch width should have open risers. Open ,rating type treads are desirable for outside stairs. See figure for minimum dimensions. Bolts Y2
1<1
Bolt holes
9/16 1<1
All burrs and sharp edges shall be removed. Dimensions of rises (R) and tread runs (T) tabulated below:
Ansle to Horizontal 30 0 32 0 33 0 35 0 3S o 3S o 40 0 41 0 43 0 45 0 4S o 4S o 49 0
35' OS' 41' lS' 52' 29' OS' 44' 22' 00' 3S' lS' 54'
Riee (in inches) S~
Tread Run (in inches)
~
11 lOy'
7 7~ 7~ 7Y.
10 9y'
10~ 10~
9~ 9~
S S~ S~
9 Sy.
Sy. 9
S~ S~
9~ 9~
S
5
'"
MIDRAIL BAR 2xl/4
HANDRAIL POST ANGLE 2x2.3/8
_
ANGLE 10 HORIZONTAL
314
HINGE
NOTE
LUG-A
WELDED TO BLIND FLANGE
Fit lugs and pin so that pin is loose when cover is bolted up. Weld lugs to flanges with full penetration weld. Th~_~e_ordavit
preferred to hinge, especially for frequently used openings.
A ==
VR2 - (R/2)2
B ==
VR2 -
(R/2+ 1/16+ t)2
C
R + 2% - A
o
R + 2% - B
R = Radius of flange
r = 1.5 times diameter of hole Diameter of hole ::. Pin diameter + 1/16 in.
LUG-B
WELDED TO FLANGE
THICKNESS, t OF LUGS AND DIAMETER OF PINS RATING
FLG. DIAM.
RATING
3/4
3/4
3/4
3/4
3/4
3/4
3/4
3/4
3/4
3/4
3/4
12
14
16
18
20
24
12
14
16
18
20
3/4
3/4
3/4
3/4
24
1 1/2
315
LADDER Conforms to the requirements of STANDARD ANSI A14.3-1974 SAFETY REQUIREMENTS FOR FIXED LADDERS.
OUTSIDE OF SHELL OR INSULATION
SIDE STEP
.>"""'1".......=---'-
THROUGH STEP 24 in. min. 30 in. max.
n
SIDE RAIL (note 5)
P=
RUNG 314 II BAR
NOTES 1. Cage is not required where the length of climb is 20 feet or less above ground level. 2. Horizontally offset landing platform shall be provided at least every 30 ft. of climbing length. Where safety devices are used, rest platforms shall be provided at maximum interwalls of 250 feet. 3. All material: steel conforming to ASTM A 36 4. Instead of the above specified structural shapes any other structural steel of equivalent strength may be used. To avoid damages during shipping or galvanizing, structural angles are widely used for side rail and vertical members of the cage. 5. The recommended minimum size of side rails under normal atmospheric condition 2 1/2 x 3/8 in. flat bar,although 2 x 1/4 bars are frequently used in practice. 6. All burrs and sharp edges shall be removed. 7. Protective Coating: one shop coat primer and one field coat of paint or hot dip galvanizing.
316
MIST
EXTRACTOR
Mist extractors by separating mist, undesirable liquids from vapor, steam, liquids, etc. improve the performance of various process equipments. They are manufactured from metal or plastic mesh and available in any required size and shape.
~II~
detail· A or B
TYPES OF MIST EXTRACTORS
'ANGLE 1Klxl/8
DETAIL - A
DETAIL -
DETAIL - B
c
SUPPORT OF MIST EXTRACTORS
Use 6 I 12.5 beam support in center of mist extractor, when the diameter is greater than 6 ft.
SPECIFICATION THICKNESS OF PAD WIRE MESH
THICKNESS OF WIRE MATERIAL OF WIRE DENSITY Ib./Cu. ft. PRESSURE DROP MA TERIAL CARBON STEEL
GRID
4"
6"
.011 "
.011 "
TYPE 304 S.S. TYPE 304 S.S. 9.0 5.0 0.5" TO 1" WATER GAGE
BEARING BAR
l"x3/16"
CROSS BAR BEARING BAR SPACING CROSS BAR SPACING WEIGHT Ib./sq.ft.
~ if>
lx3/16" y.. if>
3-9/16 4"
3-9/16 4"
5.7
7.4
WIDTH OF ONE SECTION
12"
12"
317
NAME PLATE Pressure vessels built in accordance with the requirements of the Code may be stamped with the official symbol "U" to denote The American Society of Mechanical Engineers' standard. (Code UG-11S and 116) Pressure vessels stamped with the Code-symbol shall be marked with the following: 1. manufacturer's name; preceded with the words: "certified by"; maximum allowable working pressure, (MA WP) psi at temperature, of; maximum design metal temperature at maximum allowable working pressure, psi (MDMT); manufacturer's serial number; (SIN); year built Abbreviations may be used as shown in parenthesis. 2. the appropriate abbreviations indicating the type of construction, service, etc., as tabulated: When inspected by a user's inspector USER Arc or gas welded W Lethal service L Unfired steam boiler US Direct firing OF Fully radiographed and UW-II (a)(S) not applied Rfl Joints A & D fully radiographed; UW-Il(a)(5)(b) applied R12 Spot radiographed RTI When RTl, RT2 or RT3 are not applicable Rf4 Post weld heat treated ill Part of the vessel post weld heat treated PHT Nonstationary Pressure Vessel NPV 1. Symbol "UM" shall be used when the vessel is exemptedfrom inspection [Code U-l (k)]. 2.
For vessels made of5%, 8% and 9% nickel sheets, the use afnameplates is mandatory for shell thickness below ~ in.; name plates are preferred on all thicknesses. Code ULT-1l5(c)
USER
CERTIFIED BY OMEGA TANK CO. MA WP 250 psi II 650'F MDMT 6S0'F It 250 psi S/N-19560 Year built: 1996
W-L
RT 1
NAME PLATE EXAMPLE (The vessel was inspected by user's inspector, arc welded, used in lethal service, fully radiographed and post weld heat treated.) Additional data shall be below the code reauired marking.
HT The name plate shall be affixed directly to the shell. Ifadditional name plate is used on skirts, supports, etc., it shall be marked: "Duplicate." Lettering shall be not less than 5/32 in. high. The Code-symbol and serial number shall be stamped, the other data may be stamped, etched, cast or impressed. Commonly used material for name plate 0.32 in. stainless steel or '/s in carbon steel. The name plate shall be seal welded to uninsulated vessel or mounted on bracket if the vessel is insulated, and located in some conspicuous place; near manways, liquid level control, level gage, about S ft. above ground, etc.
318
PLATFORM Conforms to the requirements of OCCUPATIONAL SAFETY AND HEALTH (OSHA) STANDARDS
3 ft 6
In
ma)(
MIDRAIL BAR 2x1/4
i
/ANGLE 5x3xY.
1/
Platforms shall be fabricated in sections if necessary suitable for shipping and field erection. Platforms fabricated in sections shall
SECTION
be shop fitted, marked and knocked down for shipping. All field connections are to be bolted. Manufacturer shall furnish 10% extra bolts of each sizes for spare. All burrs and sharp edges shall be removed. Paint:
one shop coat primer, except
walking surfaces. Max. spacing of supports 6 ft. Max. spacing of handrail posts 6 ft. Drill one 9/16 ¢J drain hole in checkered
CHANNEL 6x8.2
plate for each 10 sq. ft. area of floor. Bolts 1/2 ¢J Bolt holes 9/16 ¢J
ALTERNATIVE SUPPORTS
319
SKIRT
OPENINGS
1/4 IN. CONTINUOUS
FILLET WELD
VENT HOLES In service of hydrocarbons or other combustible liquids or gases the skirts shall be provided with minimum of two 2 inch vent holes located as high as possible 180 degrees apart. The vent holes shall clear head insulation. For sleeve may be used coupling or pipe.
ACCESS OPENINGS The shape of access openings may be circular or any other shapes. Circular access openings are used most frequently with pipe or bent plate sleeves. The projection of sleeve equals to the thickness of fireproofing or minimum 2 inches. _The projection of sleeves shall be increased when necessary for reinforcing the skirt under certain loading conditions. Diameter (D) = 16 - 24 inches
PIPE OPENINGS The shape of pipe openings are circular with a diameter of 1 inch larger than the diameter of flange. Sleeves should be provided as for access openings. TYPES OF SKIRT ACCESSES
320
VORTEX BREAKER The purpose of vortex breakers is to eliminate the undesirable vortexing of liquids. Cross and flat-plate baffles are frequently used with a wipth of two times the nozzle diameter. For a high degree of effectiveness under severe swirling conditions the width of the baffle should be four times the nozzle diameter. The height above the outlet should be about half the nozzle diameter but may be several inches if required larger clearance for other reasons.
R11'1 ~.-~
~
VORTEXING OF LIQUIDS 0= DIAMETER OF PIPE
c...
GRATING
GRATING BAFFLE FLAT AND CROSS PLATE BAFFLES
Material: 1/4 carbon steel plate or grating with 1 x 1-1/8 bars.
Reference: F. M. Patterson "Vortexing can be prevented" The Oil and Gas Journal, August 4, 1969.
321
PART III. MEASURES AND WEIGHTS 1.
Table of Properties of Pipes, Tubes. '" ....................................... ........ ... 322
2.
Dimensions ............................................................................................ 334 of Heads, Flanges, Long Welding Necks, Welding Fittings, Screwed Couplings.
3.
Weight ................................................................................................... 374 of Shells and Heads, Pipes and Fittings, Flanges, Openings, Packing and Insulation, Plates, Circular Plates, Bolts.
4.
Volume .................................................................................................. 416 of Shells and Heads, Partial Volumes in Horizontal Cylinders, Partial Volumes in Ellipsoidal and Spherical Heads.
5.
Area of Surfaces of Shells and Heads ...................... .............. ............... 425
6.
Conversion Tables ................................................................................ 426 Decimals of an Inch, Decimals ofa Foot, Metric System, Inches to Millimeters, Millimeters to Iriches, Square Feet to Square Meters, Square Meters to Square Feet, Pounds to Kilograms, Kilograms to Pounds, U.S. Gallon to Liters, Liters to U.S. Gallons, Pounds per Square Inches to Kilogram per Centimeter, Kilogram per Centimeter to Pounds per Square Inch, Degrees to Radius, Minutes and Seconds to Decimals of a Degree, Centigrade to Fahrenheit, Fahrenheit to Centigrade.
322
PROPERTIES OF PIPE Schedule numbers and weight designations are in agreement with ANSI B36.1 0 for carbon and alloy steel pipe and ANSI B36.19 for stainless steel pipe. Nom pipe size
1
i
Schedule No. Carbon & alloy steels
10~
.065 .088 .119
.330 .424 .535
.0570 .0451 .0310
.141 .141 .141
.1073 .0955 .0794
.1320 .1041 .0716
40 80
10S 405 80S
.... Sid. X-Stg.
.675 .675 .675
.545 .493 .423
.065 .091 .126
.423 .567 .738
.1010 .0827 .0609
.171 .171 .177
.1427 .1295 .1106
.2333 .1910 .1405
... 40
105 40S
Sid.
.840 .840
.670 .622
.083 .109
.671 .850
.1550 .1316
.220 .220
.1764 .1637
.3568 .3040
80 160
80S ...
X-Slg.
...
. ..
XX·Stg.
.840 .840 .840
.546 .466 .252
.147 .187 .:294
1.087 1.310 1.714
.1013 .0740 .0216
.220 .220 .220
.1433 .1220 .0660
.2340 .1706 .0499
... 40 80
10S 405 80S
Std. X-Stg.
1.050 1.050 1.050
.834 .824 .742
.083 .113 .154
.857 1.130 1.473
.2660 .2301 .1875
.275 .275 .275
.2314 .2168 .1948
.6138 .5330 .4330
160
...
1.050 1.050 XX·SIg. 1.050
.675 .614 .434
.188 .218 .308
1.727 1.940 2.440
.1514 .1280 .0633
.275 .275 .275
.1759 .1607 .1137
.3570 .2961 .1479
.. 40 80
105 40S 80S
.. Std. X.SIg.
1.315 1.315 1.315
1.097 1.049 .957
.109 .133 .179
1.404 1.678 2.171
.4090 .3740 .3112
.344 .344 .344
.2872 .2740 .2520
.9448 .8640 .7190
.. . 160
.. .
.. .
....
1.315 1.315 1.315
.877 .815 .599
.219 .250 .358
2.561 2.850 3.659
.2614 .2261 .1221
.344 .344 .344
.2290 .2134 .1570
.6040 .5217 .2818
1.660 1.660
1.442 1.380
.109 .140
1.806 2.272
.7080 .6471
.434 .434
.3775 .3620
1.633 1.495
1.278 1.160 .896
.191 .250 .382
2.996 3.764 5.214
.5553 .4575 .2732
.434 .434 .434
.3356 .3029 .2331
1.283 1.057 .6305
40 80 160
...
.. . 40 80 160
...
2
.0740 .0568 .0364
.0-49 .068 .095
.410 .364 .302
.. .
1~
.0804 .0705 .0563
.307 .269 .215
.540 .540 .540
.. .
1~
.106 .106 .106
.405 .405 .405
Sid. X.SIg.
.. .
1
.0320 .0246 .0157
Weight per foot lb.
. ...
3
3
.186 .244 .314
Wall thickness in.
105 405 80S
40 80
..
Trans· verse area sq. in.
Inside diam. in.
Std. X.SIg.
...
i
Wt. of Outsidt Inside water surface surface per ft. per ft. per ft. pipe sq. ft. sq. ft. lb.
Outside diam. in.
40S 80S
1
1
Weight Designation
40 80
4 i
Stainless steels
.. . 40 .. .
....
...
XX.Stg.
10S 40S
....
80S
X·SIg.
Std.
. ..
XX-Stg.
1.660 1.660 1.660
lOS 40S
.... Std.
1.900 1.900
1.682 1.610
.109 .145
2.085 2.717
.9630 .8820
.497 .497
.4403 .4213
2.221 2.036
80S
X·Stg.
1.900 1.900 XX·Stg. 1.900
1.500 1.337 1.100
.200 .281 .400
3.631 4.862 6.408
.7648 .6082 .4117
.497 .497 .497
.3927 .3519 .2903
1.767 1.405 .950
2.157 2.067 2.041
.109 .154 .167
2.638 3.652 3.938
1.583 1.452 1.420
.622 .622 .622
.5647 .5401 .5360
3.654 3.355 3.280
...
...
. .. 10S 40S
.... Std. ...
2.375 2.375 2.375
323 PROPERTIES OF PIPE (con't.) Schedule No. NomCarbon Staininal & alloy less pipe steels steels size
2 (CONT.)
80 ...
. .. 80S . ..
.. . 160
... ...
., .
...
...
2~
40 .. 80 160
.. .
... .. . ... ...
40
3
.. .
...
80
.. . .. . 160 ...
...
. ..
10S 40S 80S
... ...
Weight Outside Inside diam. designa - diam. in. in. tion
.. X.Stg. '" .
Wt. of water per ft. pipe lb.
Outside surface per ft. sq. ft.
Inside surface per ft. sq. ft.
Transverse area sq. in.
2.375 2.375 2.375
2.000 1.939 1.875
.188 .218 .250
4.380 5.022 5.673
1.363 1.279 1.196
.622 .622 .l:22
.5237 .5074 .4920
3.142 2.953 2.761
2.375 2.375 2.375
1.150 1.689 1.503
.312 .343 .436
6.883 7.450 9.029
1.041 .767 .769
.622 .622 .622
.4581 .4422 .3929
2.405 2.240 1.714
. Std.
2.875 2.875 2.875
2.635 2.469 2.441
.120 .203 .217
3.53 5.79 6.16
2.360 2.072 2.026
.753 .753 .753
.6900 .6462 .6381
5.453 4.788 4.680
X.Stg.
2.875 2.875 2.875
2.323 2.125 1.771
.276 .375 .552
7.66 10.01 13.69
1.834 1.535 1.067
.753 .753 .753
.6095 .5564 .4627
4.238 3.547 2.464
.
'"
... XX·Stg. .
'"
XX-Stg.
. ...
. ...
3.500 3.500 3.500
3.260 3.250 3.204
.120 .125 .148
4.33 4.52 5.30
3.62 3.60 3.52
.916 .916 .916
.853 .851 .940
8.346 8.300 8.100
. .. 40S
. .. Std.
3.500 3.500 3.500
3.124 3.068 3.018
.188 .2.6 .241
6.65 7.57 8.39
3.34 3.20 3.10
.916 .916 .916
.819 .802 .790
7.700 7.393 7.155
... . .. 80S
. ...
1.500 3.500 3.500
2.992 2.922 2.900
254 .289 .300
8.80 9.91 10.25
3.06 2.91 2.86
.916 .916 .916
.785 .765 .761
7.050 6.700 6.605
3.500 3.500 3.500 3.500
2.875 2.687 2.624 2.300
.312 .406 .438 .600
10.64 13.42 14.32 18.58
2.81 2.46 2.34 1.80
.916 .916 .916 .916
.753 .704 .687 .601
6.492 5.673 5.407 4.155
4.000 4.000
3.760 3.744
.120 .128
4.97 5.38
4.81 4.78
1.047 1.047
.984 .981
11.10 11.01
3.732 3.704 3.624 3.548 3.438 3.364
.134 .148 .188 .226 .281 .318
5.58 6.26 1.11 9.11 11.17 12.51
4.75 4.66 4.48 4.28 4.02 3.85
1.047 1.047 1.047 1.047 1.047 1.047
.978 .971 .950 .929 .900 .880
10.95 10.75 10.32
... ... ... ., . 10S . ..
..
. ..
.
'"
X.Stg.
. ...
. ...
.. XX-Stg.
. ... .,
..
. ...
40
405
Sid.
80
80S
X.Slg.
4.000 4.000 4.000 4.000 4.000 4.000
XX-Slg.
4.00u 4.000 4.000
3.312 3.062 2 728
.344 .469 .636
13.42 17.68 22.85
3.73 3.19 2.53
1.047 1.047 1.047
.867 .802 .716
8.62 7.37 5.84
4.500 4.500 4.500
4.260 4.244 4232
.120 .128 .134
5.61 5.99 6.26
6.18 6.14 611
.1.178 1.178 1.178
1.115 1.111 1.110
14.25 14.15 14.10
4.500 4.500 4.500
4.216 4.110 4.124
.142 .165 .188
6.61 7.64 8.56
6.06 5.92 5.80
1.178 1.178 1.178
1.105 1.093 1.082
13.98 13.6J 13.39
...
. ...
...
4
Weight per foot lb.
...
10S
...
.. .
3i
Wall thickness in.
. . '
...
... ...
. .. . ..
...
105
.. .
..
... .. .
...
.. .
..
.. .
...
9.89 9.28 8.89
324 PROPERTIES OF PIPE (con't.) Schedule No. Nom· inal Carbon Stain· pipe & alloy less size steels steels
o","d'i diam. ""d,
Weight designa diam· tion in.
in.
Wall thick· ness in.
Weight Wt. of per water foot per ft. pipe Ib lb.
4.500
4.090 4026 4.000
.205 .237 .250
9.39 10.79 11 35
5.71 5.51 5.45
1.178 1.178 1.178
1.071 1.055 1.049
13.15 12.73 12.57
4.500 4.500 4.500
3.958 3.938 3.900
.271 .281 .300
12.24 12.67 13.42
5.35 5.27 5.19
1.178 1.178 1.178
1.038 1.031 1.023
12.31 12.17 11.96
4.500 4.500 4.500
3.876 3.826 3.750
.312 .337 .375
14.00 14.98 16.52
5.12 4.98 4.78
1.178 1.17B 1.178
1.013 1.002 .982
11.80 11.50 11.04
4.500 4.500 4.500 4.500
3.624 3.500 3.438 3.152
.438 .500 .531 .674
1900 21.36 2260 27.54
4.47 4.16 4.02 3.38
1.178 1.178 1.178 1.178
.949 .916 .900 .826
10.32 9.62 9.28 7.80
5.295 5.047 4.859 4.813
.134 .258 .352 .375
7.770 14.62 19.59 20.78
9.54 8.66 8.06 7.87
1.456 1.456 1.456 1.456
1.386 1.321 1.272 1.260
22.02 20.01 18.60 18.19
4.500 40
405
Std.
4 ICQNT.J
.. .
...
80
80S
X.Stg.
120
.. .
.. . 160
.. . ... . ..
·. ·.. . XX.Stg .
105 405
Std.
80S
X·Stg.
5.563 5.563 5.563 5.503
XX·Stg .
5.563 5.563 5.563 5.563
4.688 4.563 4.313 4.063
.437 .500 .625 .750
23.95 27.10 3296 38.55
7.47 7.08 6.32 5.62
1.456 1.456 1.456 1.456
1.227 1.195 1.129 1.064
17.26 16.35 14.61 12.97
6625 6.625 6.625
6.3-57 6.287 6.265
.134 .169 .180
9.29 11.56 12.50
13.70 13.45 13.38
1.735 1.735 1.735
1.660 1.650 1.640
31.75 31.00 30.81
6.625 6.625 .6.625
6.249 6.187 6.125
.188 .219 .250
12.93 15.02 17.02
13.31 13.05 12.80
1.735 1.735 1.735
1.639 1.620 1.606
30.70 30.10 29.50
6.625 6.625 6.625 6.625
6.071 6.065 5.875 5.761
.277 .280 .375 .432
18.86 18.97 25.10 28.57
12.55 12.51 11.75 11.29
1.735 1.735 1.735 1.735
1.591 1.587 1.540 1.510
28.95 28.99 27.10 26.07
6.625 6.f\25 6.625 6.625
5.625 5501
.500 .562 .71 R .864
32.79 36.40 45.30 53.16
10.85 10.30 9.16 8.14
1.735 1.735 1.735 1.735
1.475 1.470 1.359 1.280
24.85 23.77 21.15 18.83
13.40 14.26 14.91
23.6 23.6
2.26 2.26 2.26
2.180 2.178 2.175
54.5 54.3 54.1
16.90 18.30 19.64
23.2 23.1 22.9
2.26 2.26
2.161 2.152
53.5 53.1
2.26
2.148
52.7
.. . .,
.
40
·.
5
80 .
'
.
...
.
120 160
...
.. .
. ..
·..
105
. ...
. ..
...
.. . ..
... ...
"
. ...
. .. . ..
·.
40S
Std.
80
80S
X-Stg.
.. . 120 160
... ... ...
... ...
6
·. 40
...
·.
XX-Stg
... .. .
8
4.~00
OutsidJ Inside Trans· surtal:e surface verse per ft. per ft. area sq. ft. sq. ft. sq. in.
lOS
. ...
.. .
....
5.18'1
4.897
.. .
.. .
....
8.625
8.295
.148 .158 .165
.. . .. .
... ...
. ...
...
. ..
. ...
8.625 8.625 8.625
8.249 8.219 8.187
.188 .203 .219
. ...
8.625 8.625
8.329 8.309
23.5
325 PROPERTIES OF PIPE (con't.) Schedule No. NomCarbon Staininal pipe & alloy less steels size steels
.. 20 30
8 ICONT.)
'"
'"
21.43 22.40 24.70
22.7 22.5 22.2
2.26 2.26 2.26
2.136 2.127 2.115
52.2 51.8 51.2
8.625 8.625 8.625
7.981 7.937 7.921
.322 .344 .352
28.55 30.40 31.00
21.6 21.4 21.3
2.26 2.26 2.26
2.090 2.078 2.072
50.0 49.5 49.3
8.625 8.625 8.625
7.875 7.813 7.687
.375 .406 .469
33.10 35.70 40.83
21.1 20.8 20.1
2.26 2.26 2.26
2.062 2.045 2.013
48.7 47.9 46.4
8.625 8.625 8.625
7.625 7.439 7.375
.500 .593 .625
43.39 50.90 53.40
19.8 18.8 18.5
2.26 2.26 2.26
2.006 1.947 1.931
45.6 43.5 42.7
8.625 8.625 8.625 8.625
7.189 7.001 6.875 6.813
.718 .812 .875 .906
60.70 67.80 72.42 74.70
17.6 16.7 16.1 15.8
2.26 2.26 2.26 2.26
1.882 1.833 1.800 1.784
40.6 38.5 37.1 36.4
Std.
. ... ...
.. . 60
... ...
. ... . ...
80 100
80S
120 140
.,
.
..
X-Stg. '"
Inside Transsurface verse area per ft. sq. ft. sq. in.
.238 .250 .277
... ...
'
Outside surface per ft. sq. ft.
8.149 8.125 8.071
405
...
Weight Wt. of per water foot per ft. pipe Ib lb .
8.625 8.625 8.625
. .
"
Wall thickness in.
. .
40 "
I
... ...
Weight Outside Inside designa diamdiam. in. tion in.
.
...
... ...
XX-Stg.
160
"
.
105
"
.
"
.
... ...
'" . . ... ..
10.750 10.420 10.750 10.374 10.750 10.344
.165 .188 .203
18.65 21.12 22.86
36.9 36.7 36.5
2.81 2.81 2.81
2.73 2.72 2.71
85.3 84.5 84.0
10.750 10.310 10.750 10.250 10.750 10.192
.219 .250 .279-
2H'O 28.03 31.20
36.2 35.9 35.3
2.81 2.81 2.81
2.70 2.68 2.66
83.4 82.6 81.6
10.750 10.136 10.750 10.054 10.750 10.020
.307 .348 .365
34.24 38.66 40.48
35.0 34.4 34.1
2.81 2.81 2.81
2.65 2.64 2.62
80.7 79.3 78.9
10.750 10.750 10.750
9.960 9.750 9.687
.395 .500 .531
43.68 54.74 57.98
33.7 32.3 31.9
2.S1 2.81 2.81
2.61 2.55 2.54
77.9 74.7 73.7
10.750 10.750 10.750
9.564 9.314 9.250
.593 .718 .750
64.40 77.00 SO.10
31.1 29.5 29.1
2.81 2.81 2.81
2.50 2.44 2.42
71.8 68.1 67.2
10.750 10.750 10.750 10.750
9.064 8.750 8.625 8.500
.843 1.000 1.063 1.125
89.20 104.20 109.90 116.00
27.9 26.1 25.3 24.6
2.81 2.81 2.81 2.81
2.37 2.29 2.26 2.22
64.5 60.1 58.4 56.7
12.750 12.390 12.750 12344
.180 .203
24.16 27.2
52.2 52.0
3.34 3.34
3.24 3.23
120.6 119.9
12.750 12.312 12.750 12.274 12.750 12.250
.219 .238 .250
29.3 31.8 33.4
51.7 51.5 j13
3.34 3.34 3.34
3.22 3.22 3.12
119.1 118.5 118.0
.
"
'"
.
.
...
20
...
. ...
.
...
. ...
..
.... .
40
405
Std.
60
80S
X-Stg.
...
. ..
...
'"
"
"
30
..
'"
10 "
.
80 100
.
., ..
.. .
... ... ...
160
...
120 140
.. . "
.
'" . . ...
lOS .. .
....
.
...
20
... ..
. .. ..
.
12 .. . "
'"
. ...
'"
.
326 PROPERTIES OF PIPE (con't.) Schedule No. Nom· inal Carbon Stain· pipe & alloy less steels steels size
.. 30
40S
Weight Outside Inside designa diam· diam. tion in. in.
12
.279
37.2
50.7
3.34
3.19
.300
40.0
50.5
3.34
3.18
116.1
...
12.750 12.090
.330
43.8
49.7
3.34
3.16
114.8
12.750 12.062
.344
45.5
49.7
3.34
3.16
114.5
Std.
12.750 12.000
.375
49.6
48.9
3.34
3.14
113.1
12.750 11.938
.406
53.6
48.5
3.34
3.13
111.9
12.750 11.874
.438
57.5
48.2
3.34
3.11
111.0
12.750 11.750
.500
65.4
46.9
3.34
3.08
108.4
12.750 11.626
.562
73.2
46.0
3.34
3.04
106.2
12.750 11.500
.625
80.9
44.9
3.34
3.01
103.8
12.750 11.376
.687
88.6
44.0
3.34
2.98
101.6
12.750 11.064 12.750 11.000
.843
108.0
41.6
3.34
2.90
96.1
.875
110.9
41.1
3.34
2.88
95.0
12.750 10.750 1.000 12.750 10.500 1.125
125.5
39.3
3.)4
2.81
90.8
140.0
37.5
3.34
2.75
86.6
12.750 10.313
1.219
150.1
36.3
3.34
2.70
83.8
10.126 1.312
161.0
34.9
3.34
2.65
80.5 146.0
X.Stg.
80
.,
.
100
.,
.
. ... ....
..
Trans· Inside surface verse area per ft. sq. in. sq. ft.
12.750 12.150
·. . ...
120
Outside surface per ft. sq. ft.
12.750 12.192
60
(CONT.)
Weight Wt. of water per foot per ft. pipe lb IbJ
. ...
40
80S
Wall thick· ness in.
116.9
.,
.
·. . ...
.,
.
. ...
12.750
.,
.
. ...
14.000 13.624 14.000 13.560 14.000 13'.524
.188
28
63.4
3.67
3.57
.220
32
63.0
3.67
3.55
145.0
.238
35
62.5
3.67
3.54
144.0
.250
37
62.1
3.67
3.54
143.0
.312
46
60.8
3.67
3.50
140.5
Std.
14.000 13.500 14.000 13.375 14.000 13.250
.375
55
59.7
3.67
3.47
137.9
.406
58
59.5
3.67
3.45
137.0
....
14.000 13.188 14.000 13.124
.438
63
58.5
3.67
3.44
135.3
14.000 13.062
.469
68
58.1
3.67
3.42
134.0
14.000 13.000 14.000 12.814
.500
72
57.4
3.67
3.40
132.7
.593
85
55.9
3.67
3.35
129.0
14.000 12.750
.625
89
55.3
3.67
3.34
127.7
14.000 12.688 14.000 12.500
.656
94
54.7
3.67
3.32
126.4
80
.750
107
51.2
3.67
3.27
122.7
100
14.000 12.125
.937
131
50.0
3.67
3.17
115.5
120
14.000
1.093
151
47.5
3.67
3.09
109.6 103.9
140 160
.. .
.. 10 20 30
40
14
X.Stg. 60
·.
11.814 14.000 11.500 14.000 11.313
. ...
14.000 11.188
140 160
.' .
1.250
171
45.0
3.67
3.01
1.344
182
43.5
3.67
2.96
100.5
190
42.6
3.67
2.93
98.3
1.406
327 PROPERTIES OF PIPE (con't.) Schedule No. Nom· inal Carbon Stain· pipe & alloy less size steels steels
Weight Outsid e Inside design a diam· diam. tion in. in.
...
. ..
. ...
...
. ..
10
..
. ... ..
20
.. .
... . .. ...
...
. ..
40
...
30
...
16
. ... . .. X.SIg.
...
. ..
60 .. .
... ...
.., . . ...
.. .
...
. ...
80 100
...
. ...
120
. ...
. ...
140.
...
. ..
... ...
.., . ....
...
. ...
...
.,
160 10 20
"
..
. ...
..
Std.
\Veight WI. of per water per ft. foot lb) pipe lb
Ou tsi de surface per fl. sq. ft.
Inside Trans· surface verse per ft. area sq. in. sq. ft.
.188
32
4.09
192.0
4.20
4.06
190.0
.250
40 42
83.3 82.5
4.20
.238
82.1
4.20
4.06
189.0
16.000 15.438 16.000 15.375 16.000 15.31-2
.281
47
81.2
4.20
4.04
.312 344
52 57
80.1
4.20
4.03
187.0 185.6
80.0
4.20
4.01
184.1
16.000 15.250 16.000 15.188 16.000 15.124
.375 .406 .438
63 68 73
79.1 78.6 78.2
4.20
182.6 181.0
4.20
4.00 3.98 3.96
180.0
16.000 15.062 16.000 15.000 16.000 14.938
.469 .500 .531
78 83 88
77.5 76.5 75.8
4.20 4.20 4.20
3.94 3.93 3.91
178.5 176.7 175.2
16.000 14.688 16.000 14.625 16.000 14.500
.656 .687 .750
108 112 122
73.4 72.7 71.5
4.20 4.20 4.20
3.85 3.83 3.80
169.4 168.0 165.1
16.000 14.314 16.000 13.938 16.000 13.564
.843 1.031 1.218
137 165 193
69.7 66.0 62.6
4.20 4.20 4.20
3.75 3.65 3.55
160.9 152.6 144.5
16.000 13.124 16.000 13.000 16.000 12.814
1.438 1.500 1.593
224 23~
4.20 4.20 4.20
3.44 3.40 335
135.3 132.7
245
58.6 57.4 55.9
18.000 17.500 18.000 17.375 18.000 17.250
.250 .312 .375
47 59 71
104.6 102.5 101.2
4.71 4.71 4.71
4.58 4.55 4.51
Ul.0 237.1 233.7
18.000 17.124 18.000 17.000 18.000 16.876
.438 .500 .562
82 93 105
99.5 98.2 97.2
4.71 4.71 4.71
4.48 4.45 4.42
229.5 227.0 224.0
16.000 15.624 16.000 15.524 16.000 15.500
4.20
1~9.Q
30
... X.SIg
40
... ...
...
. ... ., .. ..
18.000 16.813 18.000 16.750 18.000 16.500
.594 .625 .750
110 116 138
96.1 95.8 92.5
4.71 4.71 4.71
4.40 4.39 4.32
222.0
. ..
...
. ... . ... . ...
18.000 16.375 18.000 16.126 18.000 15.688
.812 .937 1.156
149 171 208
91.2 88.5 83.7
4.71 4.71 4.71
4.29 4.22 4.11
210.6 204.2 193.3
.. , .
. ...
18.000 18.000 18.000 18.000
15.250
...
1.375 1.562 1.687 1.781
244 275 294 309
79.2 75.3 72.7 71.0
4.71 4.71 4.71 4.71
3.99 3.89 3.83 3.78
182.7 173.8 168.0 163.7
. ... 60
..
18
Sid.
Wall thick· ness in.
... 80 100
.. ...
120
140 ... 160
. .. ...
'0' •
. .. .
14.876 14.625 14.438
220.5
213.8
328 PROPERTIES OF PIPE (con't.) Schedule No. Nominal Carbon Stainpipe & alloy less size steels steels
10 .. . 20
.. . 30 .. .
20
'"
· .. .. '
· .. ... .
.... . ... Std. X-Stg.
"
· ..
.. .
...
. ... . ...
60 .. .
· ..
. ...
40
.. . 80 100 120 140
· .. " " "
'"
'"
22
Weight Outside Inside designa diam- diam. in. in. tion
. . .
. .0. ,.0 .
..0. . ...
. .
.... · ...
Weight WI. of water per foot per flpipe lb lb.
Outside surface per ft. sq. ft.
TransInside surface verse area per flsq. ft. sq. in.
20.000 19.500 20.000 19.374 20.000 19.250
.250 .313 .375
53 66 79
130.0 128.1 126.0
5.24 5.24 5.24
5.11 5.08 5.04
299.0 295.0 291.1
20.000 19.124 20.000 19.000 20.000 18.875
.438 .500 .562
92 105 117
125.1 122.8 121.1
5.24 5.24 5.24
5.01 4.97 4.94
28S.0 283.5 279.8
20.000 20.000 20.000 20.000
18.814 18.750 18.376 18.250
.593 .625 .812 .875
123 129 167 179
120.4 119.5 114.9 113.2
5.24 5.24 5.24 5.24
4.93 4.91 4.81 4.78
278.0 276.1 265.2 261.6
20.000 20.000 20.000 20.000
18.188 17.938 17.438 17.000
.906 1.031 1.281 1.500
20.000 16.500 20.000 16.313 20.000 16.064
1.750 1.S44 1.968
185 209 256 297 342 357 379
112.7 109.4 103.4 9S.3 92.6 90.5 87.9
5.24 5.24 5.24 5.24 5.24 5.24 5.24
4.76 4.80 4.56 4.45 4.32 4.27 4.21
259.S 252.7 238.8 227.0 213.8 209.0 202.7
160
. '"
.. .
.. ..
.. .
'"
.
·.
22.000 21.500 22.000 21.376 22.000 21.250
.250 .312 .375
58 72 87
157.4 155.6 153.7
5.76 5.76 5.76
5.63 5.60 5.56
363.1 358.9 354.7
.. .
'"
.
.. , .
22.000 21.126 22.000 2LOOO 22.000 20.876
.437 .500 .562
103 115 129
152.0 150.2 148.4
5.76 5.76 5.76
5.53 5.50 5.47
350.5 346.4 342.3
22.000 20.750 22.000 20.624 22.000 20.500
.625 .688 .750
143 157 170
146.6 144.8 143.1
5.76 5.76 5.76
5.43 5.40 5.37
338.2 334.1 330.1
24.000 23.500 24.000 23.376 24.000 23.250
.250 .312 .375
63 79 95
189.0 186.9 183.8
6.28 6.28 6.28
6.15 6.12 6.09
435.0 430.0 424.6
24.000 23.125 24.000 23.000 24.000 22.876
.437 .500 .562
110 125 141
181.8 181.0 178.5
6.28 6.28 6.28
6.05 6.02 5.99
420.0 416.0 411.0
24.000 22.750 24.000 22.626 24.000 22.500
.625 .687 .750
156 171 186
175.9 174.2 172.1
6.28 6.28 6.28
5.96 5.92 5.89
406.5 402.1 397.6
.968 1.031 1.218 1.531
238 253 297 367
165.8 163.6 158.2 149.3
6.28 6.28 6.28 6.28
5.78 5.74 5.65 5.48
382.3 378.0 365.2 344.3
.. .
.. . .. . 10
.. .
.... '" .
0"
•
·...
,0 ••
.... . ...
... .
....
'"
. Std.
20
X-Stg.
30
24
Wall thickness in.
40
'"
.
'"
.
60
...
SO 100
·.
'"
.
....
'"
.
....
24.000 24.000 24.000 24.000
22.064 21.938 21.564 20.938
329 PROPERTIES OF PIPE (con't.) Schedule No. Nominal Carbon Stainpipe & alloy less steels size steels
24 iCONT.)
120 140 .. . 160
.. .
.. . .. .
26
... .. . .. .
.. .
.. . .. .
30
Weight Outside Inside designa diam- diam. lion in. in.
... .
....
. , ..
....
... . '0' •
....
....
Weight WI. of Outsid~ Inside Transper water surface surface verse foot per ft. per ft. per ft. area lb. pipe lb sq. ft. sq. ft. sq. in.
20.376 19.876 19.625 19.314
1.812 2.062 2.187 2.343
429 484 510 542
141.4 134.4 130.9 127.0
6.28 6.28 6.28 6.28
5.33 5.20 5.14 5.06
326.1 310.3 302.0 293.1
.250 .312 .375
67 84 103
221.4 219.2 217.1
6.81 6.81 6.81
6.68 6.64 6.61
510.7 505.8 500.7
'0' •
....
... .
.....
... . ... .
....
26.000 25.500 26_000 25.376 26.000 25.250
... .... ....
26.000 25.126 26.000 25.000 26.000 24.876
.437 .500 .562
119 136 153
215.0 212.8 210.7
6.81 6.81 6.81
6.58 6.54 6.51
495.8 490.9 486.0
26.000 24.750 26.000 24.624 26.000 24.500
.625 .688 .750
169 186 202
208.6 206.4 204.4
6.81 6.81 6.81
0.48 6.45 6.41
481.1 476.2 471.4
30.000 29.376 30.000 29.250 30.000 29.125
.312 .375 .437
99 119 138
293.7 291.2 288.7
7_85 7.85 7.85
7.69 7.66 7.62
677.8 672.0 666.2
30.000 29.000 30.000 28.875 30.00C 28.750
.500 .562 .625
158 177 196
286.2 283.7 281.3
7.85 7.85 7.85
7.59 7.56 7.53
660.5 654.8 649.2
•
0'
•
... . •
0'
•
.0
••
.. , .
....
'0' •
....
10
,0' •
....
.. . .. .
.. , .
....
... .
....
20
....
.... ...
10
24.000 24.000 24.000 24.000
Wall thickness in.
w w
ANSI B 36.10
DIMENSIONS OF PIPE
o
1. All Dimensions are in inches 2. The Nominal Wall Thicknesses shown are subject to a 12.5% Mill Tolerance 3. Not included in standard ANSI B 36.10 Nominal Outside Pipe Diameter Size
V.
v..
%
-~
% 1
0.405 0.540 0.675
--0.8-40 1.050 1.315
- - ---
Iv..
1.660 1~ 1.900 2 2.375 --- --2.875 2~ 3 3.500 3~ 4.000 --- --4 4.500 5.563 5 6 6.625 - - --8 8.625 10 10.750 12 12.750 - - --14 14.000 16 16.000 18 18.000 - - --20 20.000 24 24.000 303 30.000
NOMINAL WALL THICKNESS Sched. 10
Schad. 20
Sched. 30
Std. Weight
Sched. 40
-----------------------
---
------------------
0.068 0.088 0.091
0.068 0.088 0.091 -0.109 0.113 0.133
--
-. ..
-------
0.250 0.250 0.250 -- ,_.... 0.250 0.250 0.312
-------.----.-----.
--
0.109 0.113 0.133 -0.140 0.145 0.154 -0.203 0.216 0.226 --
0.312 0.312 0.312
0.375 0.375 0.438
0.237 0.258 0.280 -_._-0.322 0.365 0.375 -----0.375 0.375 0.375
------
------
------
0.375 0.375 0.500
0.500 0.562 0.625
0.375 0.375 0.375 3
--
-0.250 0.250 0.250
-0.277 0.307 0.330
~-.--
-------
0.140 0.145 0.154 -0.203 0.216 0.226 -0.237 0.258 0.280
-0.322 0.365 0.406 ---- ._--
0.438 0.500 0.562 --.---0.593 0.687
--
Schad. 60
..
--.
--
---
-------------
--0.406 0.500 0.562 ---_ .. 0.593 0.656 0.750 ---0.812 0.968
--
Extra Strong
Sched. 80
0.095 0.119 0.126
0.095 0.119 0.126
--
--
0.147 0.154 0.179
0.147 0.154 0.179 -0.191 0.200 0.218 --0.276 0.300 0.318 --0.337 0.375 0.432 ---0.500 0.593 0.687
-0.191 0.200 0.218
-0.276 0.300 0.318
-0.337 0.375 0.432 -.-~-
-
0.500 0.500 0.500 .-_ .. __ ... --0.500 0.500 0.500 ~---
0.500 0.500 0.500 3
-------
0.750 0.843 0.937 ----.~
1.031 1.218
--
Sched. 100
Sched. 120
.-------------------
---------
--
-.-----0.438 0.500 0.562
--
0.593 0.718 0.843 --0.937 1.031 1.156 -1.281 1.531
--
------
0.718 0.843 1.000 ----1.093 ,1.218 1.375 --1.500 1.812 -
--
Sched. 140
--
--
--
--
----------------
Sched. 160
.---0.187 0.218 0.250 ~--
0.250 0.281 0.343 --0.375 0.438
--
--
0.531 0.625 0.718
XX Strong
.--
--
--
0.294 0.308 0.358 -0.382 0.400 0.436 --
0.552 0.600 0.636 3 -0.674 0.750 0.864
~-
------
0.812 1.000 1.125 -1.250 1.438 1.562
--
0.906 1.125 1.312 ---1.406 1.593 1.781
0.875
--
--
1.750 2.062
1.968 2.343
--
.-
Nomina Pipe Size
--. -----.---
V.
v..
¥a
-~
% 1 --
Iv..
1~
2
-2V2 3 3~
-4 5 6
-8 10 12
-14
16 18 -20 24
30
331
332
PROPERTIES OF STEEL TUBING
Internal Area Sq. In.
Sq. Ft. External Surface Per Ft. Length
Sq. Ft. Internal Surface Per Ft. Length
Theoretical Weight Per Ft. Length
ID Tubing Inches
.125 .110 .105 .095 .085
.1104 .1288 .1353 .1486 .1626
.1636 .1636 .1636 .1636 .1636
.0982 .1060 .1086 .1139 .1191
.668 .605 .583 .538 .490
5/8 5/8 5/8 5/8 5/8
.075 .065 .060 .055 .050
.1772 .1924 .2003 .2083 .2165
.1636 .1636 .1636 .1636 .1636
.1244 .1296 .1322 .1348 .1374
3/4 3/4 3/4 3/4 3/4 3/4
.150 .135 .125 .1 IO .105 .095
.1590 .1810 .1964 .2206 .2290 .2463
.1963 .1963 .1963 .1963 .1963 .1963
3/4 3/4 3/4 3/4 3/4 3/4
.085 .075 .065 .060 .055 .050
.2642 .2827 .3019 .3117 .3217 .3318
7/8 7/8 7/8 7/8 7/8 7/8
.150 .135 .125 .IIQ .105 .095
7/8 7/8 7/8 7/8 7/8 7/8
D of Tubing Inches
Wall Thickness Inches
5/8 5/8 5/8 5/8 5/8
Constant C·
OD
-ID-
Metal Area (Transver.;c Metal Area) Sq. In.
.375 .405 .415 .435 .455
172 201 211 232 254
1.667 1.543 1.506 1.437 1.374
.1964 .1780 .1715 .1582 .1442
.441 .389 .362 .335 .307
.475 .495 .505 .515 .525
276 300 312 325 338
1.316 1.263 1.238 1.214 1.190
.1296 .1144 .1065 .0985 .0903
.1178 .1257 .1309 .1388 .1414 .1466
.961 .887 .834 .752 .723 .665
.450 .480 .500 .530 .540 .560
248 282 306 344 357 384
1.667 1.563 1.500 1.415 1.389 1.339
.2STT
.1963 .1963 .1963 .1963 .1963 .1963
.1518 .1571 .1623 .1649 .1676 .1702
.604 .541 .476 .442 .408 .374
.580 .600 .620 .630 .640 .650
412 441 471 486 502 518
1.293 1.250 1.210 1.190 1.172 1.154
.1776 .1590 .1399 .1301 .1201 .1100
.2597 .2875 .3068 .3370 .3473 .3685
.2291 .2291 .2291 .2291 .2291 .2291
.1505 .1584 .1636 .1715 .1741 .1793
1.I61 1.067 1.001 .899 .863 .791
.575 .605 .625 .655 .665 .685
405 448 478 526 542 575
1.522 1.446 1.400 1.336 1.316 1.277
.3416 .3138 .2945 .2p44 .2540 .2328
.085 .075 .065 .060 .055 .050
.3904 .4128 .4359 .4477 .4596 .4717
.2291 .2291 .2291 .2291 .2291 .2291
.1846 .1898 .1950
.705 .725 .745 .755 .765 .775
609
.2003 .2029
.717 .641 .562 .522 .482 .441
680 698 717 736
1.241 1.207 1.174 1.159 1.144 1.129
.2110 .1885 .1654 .1536 .1417 .1296
I
.ISO
I I I I
.135 .125 .110 .105 .095
.3848 .4185 .4418 .4778 .4902 .5153
.2618 .2618 .2618 .2618 .2618 .2618
.1833 .1911 .1964 .2042 .2068 .2121
1.362 1.247 1.168 1.046 1.004 .918
.700 .730 .750 .780 .790 .810
600 653 689 745 764 804
1.429 1.370 1.333 1.282 1.266 1.235
.4006 .3669 .3436 .3076 .2952 .2701
I I I I I I
.085 .075 .065 .060 .055 .050
.5411 .5675 .5945 .6082 .6221 .6362
.2618 .2618 .2618 .2618 .2618 .2618
.2173 .2225 .2278 .2304 .2330 .2356
.831 .741 .649 .602 .555 .507
.830 .850 .870 .880 .890 .900
844 885 927 949 970 992
1.205 1.176 1.149 r.136 1.124 1.111
.2443 .2179 .1909 .1772 .1633 .1492
= pounds
per tube per hour
o
I
• Liquid velocity in feet/second
.1~77
644
.2608 .2454 .2212 .2128 .1955
C x specific gravity of liquid Specific gravity of water at 60 deg. F
= 1.0
Courtesy of HEAT EXCHANGE INSTITUTE
333
PROPERTIES OF TUBING Area Metal Sq. Fe Sq. Ft. Weight Weight Weight (TransExternal Internal per Fe per Ft. per Ft. 0.0. Thick- Internal Surface Surface Length Length Length 1.0. 0 0 verse of BWG ness Area per Ft. per Ft. Adm. Copper Steel Tubing Constant _ _ Metal Tubing Gage Inches Sq. In. Length Length Lbs. Lbs. Lbs. Inches C" [ 0 Area) --~-~-------------~----~-----------------
5/8 5/8 5/8 5/8 5/8 5/8
10 II 12 13 14 15
.134 .120 .109 .095 .083 .072
.[001 .1164 .1301 .1486 .1655 .1817
.1636 .1636 .1636 .1636 .1636 .1636
.0935 .1008 .1066 .1139 .1202 .1259
.766 .705 .655 .586 .524 .464
.801 .738 .685 .613 .548 .485
.703 .647 .601 .538 .480 .425
.357 .385 .407 .435 .459 .481
156 182 203 232 258 283
l.751 1.623 1.536 1.437 1.362 1.299
5/8 5/8 5/8 5/8 5/8 5/8 3/4 3/4 3/4 3/4 3/4 3/4
16 17 18 19 20 22
.065 .058 .049 .042 .035 .028
.1924 .2035 .2181 .2299 .2419 .2543
.1636 .1636 .1636 .1636 .1636 .1636
.1296.424 .1333 .383 .1380 .329 .1416 .285 .1453 .240 .1490 .195
.443 .400 .344 .298 .251 .204
.389 .351 .30 I .262 .221 .179
.495 .509 .527 .541 .555 .569
300 317 340 359 377 397
1.263.1144 1.228 .1033 1.186 .0887 1.155 .0769 1.126 .0649 1.098 .0525
10 11 12 13 14 15
.134 .120 .109 .095 .083 .072
.1825 .2043 .2223 .2463 .2679 .2884
.1963 .1963 .1963 .1963 .1963 .1963
.1262 .1335 .1393 .1466 .1529 .1587
1.005 .920 .851 .758 .674 .594
.882 .807 .746 .665 .591 .521
.482 .510 .532 .560 .584 .606
285 JI9 347 384 418 450
1.556 1.471 1.410 1.339 1.284 1.238
.961 .880 .813 .724 .644 .568
.2067 .1904 .1767 .1582 .1413 .1251
.2593 .2375 .2195 .1955 .1739 .1534
1-.:...-...-------------------------------·-------------3/4 16 .065 .3019 .1963 .1623 .518 .542 .476 .620 471 1.210 .1399 3/4 17 .058 .3157 .1963 .1660 .467 .489 .429 .634 492 1.183 .1261 3/4 18 .049 .3339 .1963 .1707 .400 .418 .367 .652 521 1.150 .1079 3/4 19 .042 .3484 .1963 .1744 .346 .362 .318 .666 543 .1.126 .0934 3/4 20 .035 .3632 .1963 .1780 .291 .305 .267 .680 566 1.103 .0786 3/4 22 .028 .3783 .1963 .1817 .235 .246 .216 .694 590 1.081 .0635 1......:...:...-...-------------....:...:.;...;.;;.-...:..;:..-=------------------·-.:..:..:...:- - - - - - - - - - - - - 1.442 .3119 7/8 10 .134 .2894 .2291 .15891.156 1.2091.060 451 .607 1.378 .2846 494 7/8 11 .120 .3167 .2291 .1662 1.055 1.103 .968 .635 1.332 .2623 7/8 12 .109 .3390 .2291 .1720 .972 1.017 .892 529 .657 1.277 .2328 7/8 13 .095 .3685 .2291 .1793 .863 .902 .791 575 .685 1.234 .2065 7/8 14.083.3948.2291 .1856.765 .-800.702 616 .709 1.197 .1816 7/8 15 .072 .4197 .2291 .1914 .673 .704 .617 655 .731 1.174 .1654 7/8 16 .065 .4359 .2291 .1950 .613 .641 .562 .745 680 l.l53 .1489 .759 7/8 17 .058 .4525 .2291 .1987 .552 .577 .506 706 1.126 .1272 IS .049 .4742 .2291 .2034 .471 .493 .432 .777 7/S 740 1.106 .1099 766 7/8 19 .042 .4914 .2291 .2071 .407 .426 .374 .791 •. 087 .0924 794 7/S 20 .035 .5090 .2291 .2107 .342 .358 .314 .805 1.068 .0745 822 22 .028 .5268 .2291 .2144 .276 .289 .253 .819 7/8 1 1 I I I I I
1 I
1 I I
10 II 12 13 14 15
.134 .4208 .120.4536 .109 .4803 .095 .5153 .083 .5463 .072 .5755
.261S .2618 .2618 .261S .2618 .2618
.1916 1.351 .19901.229 .2047 1.131 .2121 1.001 .2183 .886 .2241 .778
16 17 18 19 20 22
.065 .058 .049 .042 .035 .028
.2618 .2618 .2618 .2618 .2618 .2618
.2278 .2314 .2361 .2398 .2435 .2471
.5945 .6138 .6390 .6590 .6793 .6999
"Liquid velocity in feetl second
=
.740 .665 .567 .490 .411 .331
pounds per tube per hour C x specific gravity of liquid
Specific gravity of water at 60 deg. F
Courtesy of
.708 .636 .542 .468 .393 .317
1.413 1.239 1.2861.128 1.182 1.037 1.047 .918 .927 .813 .814 .714
= 1.0
HEAT EXCHANGE INSTITUTE
.649 .584 .498 .430 .361 .291
.732 .760 .782 .810 .834 .856
656 707 749 804 852 898
1.366 1.316 1.279 1.235 1.199 1.168
.3646 .3318 .3051 .2701 .2391 .2099
.870 .S84 .902 .916 .930 .944
927 957 997 1028 1059 1092
1.149 1.131 1.109 1.092 1.075 1.059
.1909 .1716 .1464 .1264 .1061 .0855
Weights of other materials - Multiply carbon steel weights by the following factors: 90-10 Cu. Ni. Alloy 706 - 1.140 70-30 Cu. Ni. Alloy 715 • 1.140 70-30 Ni. Cu. Alloy 400 - 1.126 TP304 Stainless Steel· 1.013
334
HEADS For vessels of small and medium diameters ellipsoidal heads are used most commonly, while large diameter vessels are usually built with hemispherical or flanged and dished heads. Heads may be of seamless or welded construction. STRAIGHT FLANGE Formed heads butt-welded to the shell need not have straight flange when the head is not thicker than the shell according to the Code Par. UG-32 & 33, but in practice heads except hemisphericals are used with straight flanges. The usual length of straight flanges: 2 inches for ellipsoidal, I 1/2 inches for flanged and dished and 0 inches for hemispherical heads. Formed heads thicker than the shell and butt-welded to it shall have straight flange.
On the following pages the data of the most commonly used heads are listed. The dimensions offlanged and dished heads meet the requirements of ASME Code. WEIGHT OF HEADS See tables beginning on page 374 VOLUME OF HEADS See page 4116 SURF ACE OF HEADS See page 425
335
DIMENSIONS
~.1
D= inside diameter of hemispherical and ellipsoidal heads, outside diameter of ASME flanged & dished heads.
D HEMISPHERICAL
I..
h = inside depth of dish of F & D heads
"
L(R) = inside radius of dish of ASME flanged & dished heads as used in formulas for internal or external pressure.
.1
D ELLIPSOIDAL
ET
M= factor used in formulas for internal pressure.
~r
I.
L(R)7 D ASME FLANGED & DISHED
.I
r
=
inside knuckle radius of ASME flanged & dished heads.
t
=
wall thickness, nominal or minimum. ALL DIMENSIONS IN INCHES
WALL THICKNESS
DIAM
ETER D
14
16
18
20 '
22
L (R) r h M L (R) r h
M L (R) r h M L (R) r h
M L (R) r h
M L (R)
24
HEADS
SYMBOLS USED IN THE TABLES
14
,-
OF
r
h M
Ys
Y2
%
~
VB
1
lYs
1~
12 1.125 2.625 1.56 15 1.125 2.750 1.65 18 1.125 2.875 1.75 18 1.250 3.500 1.69 21 1.375 3.688 1.72 24 1.500 3.875 1.75
12 1.500 2.750 1.46 15 1.500 2.875 1.54 16 1.500 3.313 1.56 18 1.500 3.563 1.62 20 1.500 3.813 1.65 24 1.500 3.813 1.75
12 1.875 2.938 1.39 14 1.875 3.188 1.44 15 1.875 3.563 1.46 18 1.875 3.750 1.52 20 1.875 4.000 1.56 24 1.875 4.000 1.65
14 2.250 3.375 1.36 15 2.250 3.750 1.39 18 2.250 3.875 1.46 20 2.250 4.188 1.50 24 2.250 4.188 1.58
18 2.625 3.625 l.41 18 2.625 4.063 1.41 20 2.625 4.313 1.44 24 2.625 4.375 1.50
18 3.000 4.250 1.36 20 3.000 4.500 1.39 24 3.000 4.563 1.46
20 3.375 4.688 1.36 24 3.375 4.813 1.41
24 3.750 5.000 l.39
336 DIMENSIONS
OF
HEADS
ALL DIMENSIONS IN INCHES DlAM
WALL THICKNESS
ETER D
26
28
L(R). r h M L (R) r h
M
30
L (R) r h
32
L (R) r h
M
M
34
L(R) r h
36
L (R) r h
38
L (R) r h
M
M
M
40
42
L (R) r
h M L (R) r
h
M
48
54
L (R) r h M L (R) r h
M
60
L (R) r
h M
VB
Y2
%
24 1.625 4.500 1.72 26 1.750 4.813 1.72 30 1.875 4.875 1.75 30 2.000 5.563 1.72
24 1.625 4.438 1.72 26 1.750 4.750 1.72 30 1.875 4.813 1.75 30 2.000 5.500 1.72
24 1.875 4.500 1.65 26 1.875 4.750 1.69 30 1.875 4.813 1.75 30 2.000 5.375 1.72
34 2.125 5.563 1.75 36 2.250 5.938 1.75 36 2.375 6.500 1.72 40 2.500 6.625 1.69 40 2.625 7.188 1.72 42 3.000 8.000 1.69 54 3.250 8.938 1.77 60 3.625 10.000 1.77
34 30 2.125 2.125 5.500 6.000 1.75 1.69 36 36 2.250 2.250 5.875 5.813 1.75 1.75 36 36 2.375 2.375 6.438 6.375 1.72 1.72 40 36 2.500 2.500 6.563 6.938 1.69 1.69 40 40 2.625 2.625 7.125 7.063 1.72 1.72 42 42 3.000 3.000 8.750 8.688 1.69 1.69 48 48 3.250 3.250 9.750 9.750 1.72 1.72 60 54 3.625 3.625 9.875 10.688 1.77 1.72
%
Ys
1
178
I%;
1%
24 24 24 24 24 24 2.250 2.625 3.000 3.375 3.750 4.125 4.688 4.875 5.000 5.188 5.375 5.625 1.50 1.46 1.39 1.41 1.56 1.36 24 24 24 24 24 26 2.250 2.625 3.000 3.375 3.750 4.125 4.938 5.375 5.563 5.688 5.875 6.063 1.46 1.39 1.36 1.50 1.41 1.60 30 30 30 30 30 30 2.250 2.625 3.000 3.375 3.750 4.125 5.000 5.125 5.375 5.500 5.750 5.938 1.60 1.65 1.54 1.50 1.46 1.44 30 30 30 30 30 30 2.250 2.625 3.000 3.375 3.750 4.125 5.500 5.625 5.813 6.000 6.188 6.375 1.60 1.54 1.50 1.44 1.65 1.50 30 30 30 30 30 30 2.250 2.625 3.000 3.375 3.750 4.125 6.063 6.188 6.313 6.438 6.625 6.813 1.46 1.44 1.60 1.65 1.54 1.54 36 36 36 36 36 36 2.250 2.625 3.000 3.375 3.750 4.125 5.750 5.938 6.125 6.313 6.500 6.688 1.69 1.52 1.52 1.75 1.62 1.58 36 36 36 36 36 36 -2.375 2.625 3.000 3.375 3.750 4.125 6.375 6.438 6.563 6.750 6.938 7.125 1.69 1.48 1.52 1.72 1.62 1.60 36 36 36 36 36 36 2.500 2.625 3.000 3.375 3.750 4.125 7.000 7.000 7.125 7.313 7.438 7.625 1.48 1.69 1.52 1.69 1.62 1.58 40 40 40 36 36 36 2.625 2.625 3.000 3.375 3.750 4.125 7.000 7.000 7.125 7.125 8.000 8.125 1.72 1.48 1.72 1.65 1.52 1.56 42 42 42 42 42 42· 3.000 3.000 3.000 3.375 3.750 4.125 8.625 8.563 8.500 8.625 8.813 9.000 1.69 1.58 1.54 1.69 1.69 1.62 48 48 48 48 48 48 3.250 3.250 3.250 3.375 3.750 4.125 9.625 9.500 9.375 9.438 9.625 9.750 1.72 1.72 1.65 1.60 1.72 1.69 54 54 54 54 54 54 3.625 3.625 3.625 3.625 3.750 4.125 10.625 10.563 10.500 10.438 10.438 10.563 1.69 1.65 1.72 1.72 1.72 1.72
337 DIMENSIONS
OF
HEADS
ALL DIMENSIONS IN INCHES
WALL THICKNESS
DIAM
ETER D
lYz
1%
l~
30 4.500 6.125 1.39 30 4.500 6.563 1.39
30 4.875 6.375 1.36 30 4.875 6.750 1.36
30 5.250 6.938 1.34
1%
2
2~
2Yz
2~
3
L(R)
26
r
28
r
30
L (R) r h M
32
L (R) r h M
34
L (R) r h M
36
L (R) r h M
38
L (R) r h M
40
L (R) r h M
h M L (R)
42
h M
L (R) r h
M
48
L(R) r h M
54
L (R) r h M
60
L(R) r h M
30 30 30 4.500 4.875 5.250 7.000 7.188 7.375 1.39 l.36 1.34 36 36 36 36 4.500 4.875 5.250 5.625 6.875 7.063 7.313 7.500 1.46 1.44 1.41 1.39 36 36 36 36 36 4.500 4.875 5.250 5.625 6.000 7.313 7.500 7.813 7.875 8.063 1.46 1.44 1.41 1.39 1.36 36 36 36 36 36 4.500 4.875 5.250 5.625 6.000 7.813 8.000 8.125 8.313 8.500 1.46 1.44 1.41 1.39 1.36 36 36 36 36 36 4.500 4.875 5.250 5.625 6.000 8.313 8.438 8.625 8.813 8.938 1.46 1.44 1.41 1.39 1.36 42 42 42 42 42 42 42 4.500 4.875 5.250 5.625 6.000 6.750 7.500 9.188 9.250 9.438 9.563 9.750 10.125 10.500 1.52 1.48 1.46 1.44 1.41 1.34 1.36 48 48 48 48 48 48 48 48 4.500 4.875 5.250 5.625 6.000 6.750 7.500 8.250 9.875 10.063 10.188 10.375 10.563 10.875 11.250 11.625 1.56 l.54 1.48 1.50 1.46 1.36 1.41 1.39 54 54 54 54 54 54 54 54 54 4.500 4.875 5.250 5.625 6.000 6.750 7.500 8.250 9.000 10.688 10.875 11.000 11.188 11.313 11.688 12.000 12.375 12.750 l.62 1.58 1.54 1.52 1.50 1.46 1.39 1.41 1.36
338 DIMENSIONS
OF
HEADS
ALL DIMENSIONS IN INCHES
WALL THICK.NESS
DIAM ETER
%
D
66
L (R) r h
72
L (R) r h
M
M
78
L (R) r h
M
84
L (R) r h
M
90
L (R) r h
M L (R)
96
r
h M L (R) r
102
h
108
L (R) r h
M
M L (R)
114
r
h
M L (R) r
120
h
126
L (R) r h
M
M
132
L (R) r h M
66 4.000 11.000 l.77 72 4.375 12.000 1.77 78 4.750 13.000 l.77 84 5.125 14.000 1.77 90 5.500 15.125 1.77 96 5.875 16.125 1.77 96 6.125 17.938 1. 75 102 6.500 18.938 1.75
Y2
66 4.000 10.938 1.77 72 4.375 11.938 1.77 72 4.750 13.813 1.72 84 5.125 13.938 1.77 84 5.500 15.813 1.72 90 5.875 16.875 1.72 96 6.125 17.875 1.75 102 6.500 18.875 1.75 108 6.875 19.875 1.75 114 7.250 20.875 1.75 120 7.625 21.875 1.75
%
60 4.000 1l.750 1.72 72 4.375 11.875 1.77 72 4.750 13.750 1.72 84 5.125 13.875 1.77 84 5.500 15.750 1.72 90 5.875 16.813 1.72 96 6.125 17.750 1.75 102 6.500 18.750 1.75 108 6.875 19.813 1.75 114 7.250 20.813 1.75 120 7.625 21.813 1.75 126 8.000 22.875 1.75
%
60 4.000 11.625 l.72 72 4.375 11.875 1.77 72 4.750 13.688 1.72 84 5.125 13.813 1.77 84 5.500 15.688 1.72 90 5.875 16.750 l.72 96 _6.125 17.688 1.75 102 6.500 18.750 1.75 108 6.875 19.750 1.75 114 7.250 20.750 1.75 120 7.625 21.750 1.75 126 8.000 22.813 1.75
VB
60 4.000 11.563 1.72 66 4.375 12.625 1.72 72 4.750 13.563 1.72 84 5.125 13.750 1.77 84 5.500 15.625 1.72 90 5.875 16.625 1.72 Y6
6.125 17.625 1.75 102 6.500 18.688 1.75 108 6.875 19.685 1.75 114 7.250 20.688 1.75 120 7.625 21.688 l.75 120 8.000 23.688 1.72
1 60 4.000 1l.500 1.72 66 4.375 12.500 1.72 72 4.750 13.500 1.72 84 5.125 13.688 1.77 84 5.500 15.563 1.72 90 5.875 16.563 1.72 96 6.125 17.563 1.75 102 6.500 18.563 1.75 108 6.875 19.625 1.75 114 7.250 20.625 1.75 120 7.625 21.625 1.75 120 8.000 23.563 1.72
lYs 60 4.000 11.438 l.72 66 4.375 12.438 1.72 72 4.750 13.438 1.72 78 5.125 14.438 1.72 84 5.500 15.500 1.72 90 5.875 16.500 1.72 90 6.125 18.500 1.72 96 6.500 19.438 1.72 108 6.875 19.563 1.75 108 7.250 21.500 l.72 120 7.625 21.563 1.75 120 8.000 23.500 l.72
1~
J%
60 4.000 1l.375 l.72 66 4.375 12.375 1.72 72 4.750 13.375 1.72 78 5.125 14.375 1.72 84 5.500 15.438 1.72 90 5.875 16.438 l.72 90 6.125 18.375 1.72 96 6.500 19.375 1.72 108 6.875 19.500 1.75 108 7.250 21.438 1.72 120 7.625 21.500 1.75 120 8.000 23.438 l.72
60 4.125 11.375 l.72 66 4.375 12.313 1.72 72 4.750 13.313 1.72 78 5.125 14.313 1.72 84 5.500 15.313 1.72
84 5.875 17.313 1.72 90 6.125 18.250 1.72 96 6.500 19.313 1.72 108 6.875 19.438 1.75 108 7.250 21.375 l.72 114 7.625 22.313 1.72 120 8.000 23.750 1.72
339 DIMENSIONS
OF
HEADS
ALL DIMENSIONS IN INCHES
WALL THICKNESS
DIAM
ETER
iY2 1%
D
I%;
1%
2
2~
2~
2.~
3
66
60 60 60 60 60 60 60 60 L(R) 60 4.500 4.875 5.250 5.625 6.000 6.750 7.500 8.250 9.000 r h 11.500 11.688 11.813 12.000 12.125 12.438 12.813 13.125 13.500 M 1.58 1.54 1.65 1.50 1.46 1.58 1.41 1.39 1.62
72
66 66 66 66 66 66 66 66 L (R) 66 4.500 4.875 5.250 5.625 6.000 6.750 7.500 8.250 9.000 r 12.313 12.500 12.625 12.750 12.938 13.250 13.563 13.938 14.313 h 1.60 1.44 M 1.54 1.65 1.72 1.50 1.46 1.58 1.69
78
72 72 72 72 72 72 72 72 L (R) 72 4.875 5.250 5.625 6.000 6.750 , 7.500 8.250 9.000 4.75 r 13.250 13.250 13.438 13.563 13.750 14.063 14.375 14.750 15.063 h M l.65 1.62 1.56 1.52 1.48 1.46 1.72 1.69 1.72
84
78 78 78 78 78 78 78 78 78 L (R) 5.250 5.625 6.000 6.750 7.500 8.250 9.000 5.125 5.125 r 14.250 14.188 14.250 14.375 14.500 14.875 15.188 15.500 15.875 h 1.72 M 1.60 1.48 1.69 1.56 1.72 1.65 1.72 1.52
90
~4 ~4 M4 ~4 84 84 84 84 84 L(R) 5.500 5.500 5.500 5.625 6.000 6.750 7.500 8.250 9.000 r h 15.250 15.188 15.125 15.188 15.313 15.625 16.000 16.313 16.625 M l.58 1.52 1.69 1.62 1.54 1.72 1.72 1.72 1.72
L (R)
96
r
h M L (R)
102
108
r
h M L (R) r h M L (R)
114
120
r
h M L(R) r h
M L (R)
126
r
h M L(R)
132
r
h M
84 5.875 17.250 1.69 90 6.125 18.125 1.72 96 6.500 19.250 1.72 108 6.875 19.313 1.75 108 7.250 21.313 1.72 114 7.625 22.250 l.72 120 8.000 23.313 1.72
84 5.875 17.125 1.69 90 6.125 18.125 1.72 96 6.500 19.125 1.72 102 6.875 20.125 1.72 108 7.250 21.250 1.72 114 7.625 22.188 1.72 120 8.000 23.250 1.72
84 5.875 17.063 1.69 90 6.125 18.063 1.72 96 6.500 19.063 1.72 102 6.875 20.063 1.72 108 7.250 2l.188 1.72 114 7.625 22.125 1.72 120 8.000 23.125 1.72
84 5.875 17.000 1.69 90 6.125 18.000 1.72 96 6.500 19.000 1.72 102 6.875 20.000 1.72 108 7.250 2l.063 1.72 114 7.625 22.063 1.72 120 8.000 23.063 1.72
84 6.000 17.063 1.69 90 6.125 17.938 1.72 96 6.500 18.938 1.72 102 6.875 19.938 1.72 108 7.250 20.938 1.72 114 7.625 21.938 1.72 120 8.000 23.000 1.72
84 6.750 17.313 1.62 90 6.750 18.125 1.65 96 6.750 18.938 1.69 102 6.875 19.813 1.72 108 7.250 20.813 l.72 114 7.625 21.813 1.72 120 8.000 22.875 1.72
84 7.500 17.625 l.58 90 7.50 18.375 1.62 96 7.500 19.188 1.65 102 7.500 20.000 1.69 108 7.500 20.813 1.72 114 7.625 21.625 1.72 120 8.000 22.750 1.72
84 8.250 17.875 1.54 90 8.250 18.688 1.58 96 8.250 19.500 1.60 102 8.250 20.312 1.62 108 8.250 21.125 1.65 114 8.250 21.938 1.69 120 8.250 22.750 1.72
84 9.000 18.188 1.52 90 9.000 19.000 1.54 96 9.000 19.813 1.56 102 9.000 20.563 1.60 108 9.000 21.438 1.62 114 9.000 22.188 1.65 120 9.000 23.000 l.65
340 DIMENSIONS
OF
HEADS
ALL DIMENSIONS IN INCHES
WALL THICKNESS
DIAM
ETER
138
144 DIAM
SEE PAGE
138
144
lyg
1
l;i
1% lY2
132 132 L (R) 132 132 132 132 132 132 8.375 8.375 8.375 8.375 8.375 8.375 8.375 8.375 r 23.938 23.875 23.813 23.750 23.688 23.625 23.563 23.500 h 1.75 1.75 1.75 l.75 M 1.75 1.75 1.75 l.75 L (R) 132 132 132 132 132 132 132 132 r 8.750 8.750 8.750 8.750 8.750 8.750 8.750 8.750 h 25.875 25.813 25.750 25.625 25.563 25.500 25.438 25.313 M l.72 l.72 1.72 l.72 l.72 l.72 l.72 1.72
ETER D
Y8
%
%
D
325
WALL THICKNESS
1%
1%
1%
2~
2
2Y2 2%
3
-
L (R) 132 130 130 130 130 132 132 130 r 8.375 8.375 8.375 8.375 8.375 8.375 8.375 9.000 23.438 23.375 23.313 23.500 23.375 23.250 23.125 23.250 h 1.69 M 1.75 1.72 1.72 1.75 1.75 l.72 l.72 132 132 132 132 L (R) 132 132 132 132 r 8.750 8.750 8.750 8.750 8.750 8.750 8.750 9.000 25.250 25.188 25.125 25.063 24.938 24.813 24.625 l4.625 h l.72 1.72 1.72 1.72 1.72 M 1.72 1.72 1.72
TOLERANCES WALL THICKNESS (APPROXIMATION) MINIMUM REQ'D. THICKNESS
* OTHER TYPES
HEMISPHERICAL
UP TO 150" I.D. inc!.
OVER 150" J.D.
To 1" 1" To 2" 2" To 3"
excl. " "
0.1875 0.3750 0.6250
0.0625 0.1250 0.2500
0.1250 0.1250 0.2500
3" To 3.5" 3.5" To 4" 4" To 4.5"
" "
0.7500 1.1250 1.5000
0.3750 0.500 0.6250
0.3750 0.5000 0.6250
4.5" To 5" 5" To 5.5" 5.5" & Over
" "
1.7500 2.0000 2.0000
0.7500 0.8750 1.0000
0.7500 0.8750 1.0000
"
* Specify minimum thickness (if required) when ordering. INSIDE DEPTH OF DISH (h) 48" O.D. and under plus 0.5" minus 0" Over 48" O.D. to 96" O.D. incl. plus 0.75", minus 0" Over 96" O.D. plus 1 ", minus 0" OUT OF ROUNDNESS Within the limits permitted by the Code.
341
FLANGES FLANGE FACING FINISH In pressure vessel construction only gasket seats of flanges, studded openings, etc. require special finish beyond that afforded by turning, grinding or milling. . The surface finish for flange facing shall have certain roughness regulated by Standard ANSI B16.5. The roughness is repetitive deviation from the nominal surface having specified depth and width. Raised faced flange shall have serrated finish having 24 to 40 grooves per inch. The cutting tool shall have an approximate 0.06 in. or larger radius resulting 500 microinch approximate roughness IANSI B16.5, 6.3.4.1.1 The side wall surface of gasket groove of ring joint flange shall not exceed 63 microinch roughness. IANSI B16.5-6.3.4.3./ Other finishes may be furnished by agreement between user and manufacturer. The finish of contact faces shall be judged by visual comparison with Standard ANSI B46-1. The center part of blind flanges need not to be finished within a diameter which equals or less than the bore minus one inch of the joining flange. IANSI B16.5-6.3.31 Surface symbol used to designate roughness r is placed either on the line indicating the surface or on a leader pointing to the surface as shown below. The numbers: 500 and 63 indicate the height of roughness; letter "c" the direction of surface pattern: "concentric-serrated" .
CONCENTRIC SERRATED FINISH
SYMBOL USED IN PAST PRACTICE
342
I SO lb. FLANGES STANDARD ANSI B16.5 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/16 in. raised face is included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified. 7. Flanges for pipe sizes 22, 26, 28 and 30 are not covered by ANSI BI6.S. SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING. Diameter of Bore
Nominal Pipe Size
A
Length Through Hub
c
B
D
SLIp· ON
J~
aW?tW4@J .H=tI I
~
I.
I .1
Ua
BLIND
Diameter of Hub at Point of Welding
Diameter of Hub at Base
Outside Diameter of Flange
Thickness of Flange
E
G
H
J
.62 .82 1.05
.88 1.09 1.36
1~ 2~6 2~6
.84 1.05 1.32
1~,
3Y2
1 V2
3%
11~6
4~
1.38 1.61 2.07
1.70 1.95 2.44
2~ 2~
1.66 1.90 2.38
2~6 2~6 3~6
5 6
3Y.r
2.47 3.07 3.55
2.94 3.57 4.07
2.88 3.50 4.00
4~
4 5 6
4.03 5.05 6.07
4.57 5.66 6.72
4.50 5.56 6.63
5~ 6~6 7~6
9 10 11
8
8.72 10.88 12.88
91~6
13Y2 16 19
1 V.
12
7.98 10.02 12.00
14 16 18
13.25 15.25 17.25
21 23V2 25
1%
20
Y.r % 1
,Yo. 1Y.r 2
2Y.r 3
10
22 24 26
28 30
2V2 2~ 2~ 21~6
lV. 1~6 1~ 1~6
Hi6 1~6
3~6 41~6
4%
7 7VJ 8V2
4
1~
4
11~6
4V2
2~6
14.14 16.16 18.18
5 5 5Y2
2V2 2 1!ti6
14.00 16.00 18.00
19.25 21.25 23.25
20.20 22.22 24.25
5Y.
2~ 3~ 3~
20.00 22.00 24.00
22
To be specified
26.25 28.25 30.25
3~
26.00 28.00 30.00
28V2
34~
30~ 32~
36V2
51~6
6
5 5 1..i6 5~
2~
3 7ti6 3V2
8.63 10.75 12.75
12
14% 15~
18 19~
24~
26Y.
27V2 29Y2 32
38~
¥a I¥.6
1~6 1~6 1~6
1 1~ 1~
1~ 1~6 11~6
11~6
1 ¥.
343
150 lb. LONG WELDING NECK H
I- I'
K
I
~,
Il~
I. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105 . Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/16 in. raised face is included in dimensions J and M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order.
~,
~~
~ ~
J
~
~r-N-
~ ~
~
~~ ~
~
Ll~
SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Lel!gth of Bolts No. of Holes
Diam. of Bolts
-Bolt Circle
K 1~
l' Yi6
4 4
2
A
2Y2 2Y.
4 4 4
3% AY. 5 5Y2
A
67i6
8 8 8
7~6
8Y2
10%
12% 15
8 12 12
Y2 Y2 Y2
2~
2)1
23A 3Va
2~
Y2 Y2
% % %
4 8
~ Raised Face
0/. %
L
M
Diameter Nominal of Pipe Bore Size
N ~
%
3Y.
2
1
3Y2 3Y.
2~
3l7. 3Yz
2~
4%
3~
1~ 1~
3
5Y2
3)1
6 7
3~
% % %
11%
31.
---
Length
2~
7Y2 8Y2 9Y2
Y.
Ring Joint
Outside Diameter
3~
'" 4Y.
20/. 3~
2
9 d)
3%
.~
4~
CIl
Q)
2~
3
3~
4~
4%
3~
.s.
3~
4~
4
4Yz 4J1
5Y2 6Y2
<; s:::
4
7%
0
6
4~
9~
4
14~
4.~ 4~
17
4~
5~ 5~
12
0.
·s 12
c: CIl
'"
11)
E
14~
~
5
8 10 12
12 16 16
1 1
18%
5~
5~
21~
1~
22%
5Yz 6
6 6).1
16 18 20
1Y.
25
6Y.
6~
1~ 1~
27~
22
27~
20 20 20
29Y2
6Y2 7
7 7J1
26~
20 22 24
29~ 31 ~ 33~
24 28 28
1~ 1~ 1~
31% 34 36
7 7
---.
28Y2 30Yz 32Y2
26 28 30
16~
18Y2
21 23
7~
14
16 18 10-14
344
eEl
300 lb. FLANGES STANDARD ANSI B16.5 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/16 in. raised face is included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified. 7. Flanges for pipe sizes 22, 26, 28 and 30 are not covered by ANSI BI6.5.
SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING. Diameter of Bore
Nominal Pipe Size
Length Through Hub
nt:ln~l
~~
1,1.
WELDING NECK
H
~.
,~ 9--;t ¥
:
~~
I
I
U6
SLIP· ON J
a~HII I. I~ : I I ~. BLIND
Diameter of Hub at Point of Welding
Diameter of Hub at Base
Outside Diameter of Flange
Thickness of Flange
A
B
C
D
E
G
H
J
.62 .82 1.05
.88 1.09 1.36
2116 2JA 27i6
VI 1 1116
.84 1.05 1.32
1 Y2 1 V. 2Y.
33A 4%
~6
4V.
% ' 116
1114 1Y2 2
1.38 1.61 2.07
1.70 1.95 2.44
2'116 2 3,4
1116 1¥!6 HI6
1.66 1.90 2.38
2Y2 2 3,4 3t16
5JA 6Y. 6Y2
3A '¥!6
V.
2Y2 3 3Y2
2.47 3.07 3.55
2.94 3.57 4.07
3 3Y. 3¥!6
1 Y2 1'116 1~
2.88 3.50 4.00
3 15
7Y2 8JA 9
1 1 Y. 1 ¥!6
4 5 6
4.03 5.05 6.07
4.57 5.66 6.72
3¥a 3Ye 3V.
1 V. 2 2116
4.50 5.56 6.63
10 11 12Y2
lJA l¥a 17i6
8 10 12
7.98 10.02 12.00
8.72 10.88 12.88
4¥a 4% 5Y.
27i6 2Y. 2V.
8.63 10.75 12.75
15 17Y2 20Y2
1 V. 2
14 16 18
13.25 15.25 17.25
14.14 16.16 18.18
5% 6JA
3 3JA 3Y2
14.00 16.00 18.00
19 21
23 25Y2 28
2Y. 2JA 2¥a
20 22 24
19.25 21.25 23.25
20.20 22.22 24.25
6¥a 6Y2 6%
3~
4Y1,
20.00 22.00 24.00
23Y. 25JA 27%
30Y2 33 36
2Y2 2Y.
26 28 30
To be spedfled
26.25 28.25 30.25
7JA
7JA
7~
7~
8~
28¥a 30Y2
38~ 40~
8JA
26JA 28 JA 30JA
32~6
43
3Y. 3¥a 3%
Y2
1
¥..
2~6
5~
4
i
116
4% 5JA 5~
7 8Y. 10JA 12% 14~ 16~
IV.
2~
345
300 lb. LONG WELDING NECK 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/16 in. raised face is included in dimensions J and M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order. SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No.
of Holes
Diam. of Bolts
Bolt Circle
K
Pia 11 Yl6 2 2!12
2'% 3%
U. Raised Face
Ring Joint
Outside Diameter !Nominal Diameter Length of Pipe Bore Size
L
4 4 4
3 3~
2V.
4
3~ 4~
23A
4~
3~6
N
3X
4
2Y2
a a
43A
31~6
5
a
5V.
5
5V2
8
60/. 7lA
40/. 5lA
6~6 7~6
a a
7V.
5~
5!/2
4V.
M
51A
9
2Y2 3 3Y2
53A
4 5 6
a!/2
12
9lA 10 5/.
5~
ay.
10%
12
6!4
123A 15
13
16 16
15IA
7
lOlA 120/.
10
173A
7~
143A
12
16lA laV2
20 20
21
24
20IA 22!/2
7~ 8~
2H4
8X
163A 19 21
14 16 18
23
24
9
23Y.
25lA 27lA
24 24
27 29IA
93A
32
29Y2
2a
34Y2
31 !/2
28 28
37
333A
39lA
10 IOY2 IlIA
7
10~
27%
11 l1Y2
29!/2 31 !/2
121A
333A
12
8
10·14
20 22 24
26 28 30
346
400 lb. FLANGES STANDARD ANSI B16.5
1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified. 7. Flanges for pipe sizes 22, 26, 28 and 30 are not covered by ANSI B16.5. SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING.
A ~ ~
1
1¥.4 1~
2 2~
3 3~
4
5 6 8 10
B
.88 1.09 1.36 1.70 1.95 2.44 2.94 3.57 4.07 4.57 5.66 6.72
14 16 18
8.72 10.88 12.88 14.14 16.1.6 18.18
20 22 24
20.20 22.22 24.25
26
26.25 28.25 30.25
12
28 30
J
a
a
BLIND
Diameter of Hub at Base
D
E
G
2~
%
2Y-.
1 1!t1,
.84 1.05 1.32
1%
C
2~,
2% 2~
lVa
v..
3Y,
1 1 ~, 1 y,
3
11~,
2%
v..
3¥,
p~
3Y2
2
4
2Vi
4!t1,
4% 4% 5% 5 "V, 6 6~
6% 6~
2Y-. 2 1!t1, 2 "V,
3Y, 3~6
3 1!tl6 3%
4
4 v..
6%
4Y2
7Y, 8Y,
7%
8%
8Y, 8%
l
a.~H II I I~ ~ I I ~ Diameter of Hub at Point of Welding
Length Through Hub
Diameter of "'Bore
Nominal Pipe Size
SLIp· ON
1.66 1.90 2.38 2.88 3.50 4.00 4.50 5.56 6.63 8.63 10.75 12.75 14.00 16.00 18.00 20.00 22.00 24.00 26~ 28~,
30;1,
1 Y2
2Y, 2Y2 2~
3;1, 3 1;1,
4% 5Y-.
Outside Diameter Thickness of of Flange Flange
H
J
3~
0/16 %
4% 4% 5Y-. 6Y, 6Y2 7Y2 8Y-. 9
5~
10
7
11 12Y2
8Va
1!t1, 1~6
% 1
1 y, 1 v..
1% 1% 1 Y2
1% 1%
12%
15 17Y2
14~
20Y2
2Y-.
16~
23 25Y2 28
2%
lOY-.
19
21 23Y,
2Y, 2Y2 2Y,
30Y2
2~
25Y-.
33
27%
2%
36
3
28% 301~, 32 1;1,
3~ 3~
4
347
400 lb. LONG WELDING NECK
"I ·Il~
H
I" I
K
~ -
I. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in thickness J but is included in length M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order.
~~
~~
I"-
~ ~
~~
l"-
~r-N-
I
I' ~
~
~
~
LL-
SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No.
of Holes
Diam. of Bolts
Bolt Circle
K
1% 11~6
2 2~
2¥. 3Y. 4Y.
5 5Y2 6~6
70/16 8Y2 lOY.
12lA 15 16~
18Y2
21 23 25~ 27~
29Y2 31 Y2
33lA
4 4 4 4 4 8 8 8 8 8 8 12 12 16 16 20 20 24 24 24 24
1% 1% 1 Y2 1% llA
28 28 28
Y2 Y.
% Y.
lA % lA lA ~
% ¥. % 1 1Y.
%," Raised Face
Ring Joint
Diameter Nominal Outside of Diameter Lenath Pipe Bore Size
L
3 v..
3
3Y2 3%
3lA 4
_3 4
4Y2
4Y.
4~
5 5¥. 6%
4~
4~
4lA 5
5 5~
7~
2 3.4 30/16 310/16 4%
5Y2
5lA
5~
7¥.
5~
5~
5~
2% 3~
9~
10% 13 15~
1~
17lA
1~
20Y.. 22Y2 24~
27
3Y2
~
~
6~
8Y.
9
9 9Y4 10
8Y. 8Y2
29~
10
32
10~
11 Y.
1~
34Y2
11 Y2
1¥. 2
37
12~
39~
13
12 12 3.4
IOY2
13Y2
1 1
2Y2
7
7lA
¥.4
2Y.
6
7
9~
N
3~
5lA 6 6% 7)12 8 8Y. 8~
M
10~
12% 14lA 16lA 19 21 23Ye 27Y.
v..
1~
2
9
2~
3 cu
3~
rJl
4
,::: 0
Q..
12
'0. -; s::
's 0
s:: rJl
~
0
S 10-14
~
5
6 8 10 12 14 16 18
t/.l
20 22 24 26 28 30
348
600 lb. FLANGES STANDARD ANSI B16.5
I. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. S. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified. 7. Flanges for pipe sizes 22, 26, 28 and 30 are not covered by ANSI BI6.5.
WELDING NECK
SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING.
Nominal Pipe Size
A ~
B
1~
.88 1.09 1.36 1.70 1.95
2
2.44
o/.t 1
1Y
14 16 18
2.94 3.57 4.07 4.57 5.66 6.72 8.72 10.88 12.88 14.14 16.16 18.18
20 22 24
20.20 22.22 24.25
26 28 30
26.25 28.25 30.25
3 3~
4 5 6 8 10
12
Diameter Diameter of Hub of at Point Hub of at Welding Base
Length Through Hub
Diameter of Bore
C
D
2~6
2Y
%
2~6
1 1 !li6
2%
1 Y.
2~
2% 3Ye
3Y-. 3¥a 4 4Y2
lY-.
1~6
10/. 1'¥!6 1'0/16 2Y.
2¥a
Outside Diameter Thickness of of Flange Flange
E
G
H
.84 1.05 1.32 1.66 1.90 2.38 2.88 3.50 4.00 4.50 5.56 6.63
1 Y2 1% 2Y.
4% 4%
6
10~
7~6 8~
1 Y2
13 14
1 ¥.
8.63
10~
16Y2
10.75 12.75
13Y2
20 22
3~
30/16
51A 6Y. 6Y2
3'0/16
7Y2
2Y2 2~
4%
5Y-.
J
8Y-. 9
~6
% '!li6 '¥!6
¥. 1 1 Y. 1Y-. 1¥a 1~
4%
2%
5Y-.
3
6
3¥a
6Y.
3%
6Y2 7
3'!li6 4¥!6
17
23~
2~
7Y-.
4%
14.00 16.00 18.00
19Y2 21 Y2
27
3
29Y-.
3Y-.
7Y2
5
7~
5Y-.
3Y2
34y-'
3~
5Y2
24 26Y-. 28Y-.
32
8
20.00 22.00 24.00
37
4
29~6
40
31% 33'0/16
421A 44Y2
15~
2¥!6 2Y2 2%
349
600 lb. LONG WELDING NECK
,- I~
H K
I
~
Il~
1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in thickness J but is included in length M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order.
~~~
~
I'-
~-N~ ~
'__-i
J
~
~
~
M
~~
LL~
SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No. of Holes
Diam. of Bolts
Bolt Circle
K 1 :V. l' Y16 2
14Raised Face
Ring Joint
4 4 4 4 4 8
Y2
8Y2
8 8 8 8 8 12
* * ¥a ¥. 1 1
10% 12* 15
12 16 20
1 Y. l'A 1 v..
16 'A
20 20 20 24 24 24
l¥a 1 Y2 1%
13* 17 19'A 20t. 23* 25*
1% 1* l¥a
30% 33
11 Ya 12 13
12Y2
28 28 28
l¥a 2 2
36 38 40 'A
13 'A 13 3,4 14
14 'A
2Y2
2¥. 3% 4Y. 5 5Y2 6~6 7~6
18 Y2
21 23 25'A 27 v.. 29Y2
31 Y2 33*
0/. % % ~
%
Diameter Nominal Outside of Diameter Length Pipe Bore Size
L
M
3 v..
3
3Y2
3Y2
3Y2
3~
-3~
"2Y.
3¥a
4 4 v.. 4/{
4 4X
2Y2
4Y2 5
3~6 31~6
5 5Y2 5M 6Y2 6M
S'A
40/.
7M
7*
20/. 3 v..
4Y2 5
5¥. 60/. 7'A 8Y2 10Y2 11 Y2
28Y2
4~
Y2
:y..
2*
I Iv.. l~
9
2 Q)
5~
S'A
.~
6 6* 7
6
0..
8~
13Y2
8% 9!4
9 9YJ 10 v.. 11
15* 17 19Y2 21 Y2
11~
24
13'A 13~
14Y2
til
Q)
·a
7Y2
8* 10*
8Y2
10 10M
N
28 v..
12
~
·s= 0
= til
('is
Q)
S ('is
CI:l
12-20
2Y2 3 3Y2 4 5 6 8 10 12 14 16 18 20 22 24 26 28 30
350
900 lb. FLANGES STANDARD ANSI B 16. S 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, aHoy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. S. BoIt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified. 7. Flanges for pipe sizes 26, 28 and 30 are not covered by ANSI B16.5. SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING.
Nominal Pipe Size
A
~
% 1
1Y-. 1~
Length Through Hub
Diameter of Bore
B
C
D
.88 1.09 1.36
2%
1~
2~ 2~
1%
1.70 1.95 2.44
2¥. 3~
1% 1%
4
1~ 2~
2.94 3.57 4.57
4Va
2Y2
4~
2~
6 8
5.66 6.72 8.72
5 5Y2 6%
3% 4
10 12 14
10.88 12.88 14.14
7~ 7~
4%
16 18 20 24
16.16 18.18 20.20 24.25
26 28 30
26.25 28.25 30.25
2 2~
3 4
5
4
8% 8Y2 9
2V.
3Y. 4~
5V.
Diameter of Hub at Base
E
G
H
.84 1.05 1.32
1~ 1~
5V.
2~,
5%
lV.
2~ 2~
6~
1 Y.
1.66 1.90 2.38
4V.
Outside Diameter Thickness of of Flange Flange
J
4~
% 1
7
1~
8~
1 Y2 1%
2.88 3.50 4.50
4~
6~
11 Y2
1~ 1~
5.56 6.63 8.63
7~ 9~
13~
2
15
2~ 2~
10.75 12.75 14.00
5
11 ~
9% 9~
18Y2
14~
21~
2~
16Y2
24
17~
25~
3Y. 3%
16.00 18.00 20.00 24.00
20
27~
3~
22~ 24~
31
4
33~
29Y2
41
4~ 5~
11 ~ 11 ~
26%
30~ 32~
42~
281~
46
5Y2 5%
12~
30~
35
48~
5~
9~
11 Y2
5~
Diameter of Hub at Point of Welding
6 6~
8
351
900 lb. LONG WELDING NECK
I ·Il~
H
,- /-
K
~'\
1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in thickness J but is included in length M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order.
~-j
~ ~ ~ ~ ~ ~r-N-
J
tJ
~~
~
LL~
SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No. of Holes
Diam. of Bolts
Bolt Circle
K
1% 1'!ti6 2 2Y2 2% 3% 4Y.
5 6~ 7~
8Y2
10% 12~
15 161A 18Y2 21 23 27lA 29Y2
31 Y2 33~
4 4 4 4 4 8 8 8 8 8 12 12 16 20 20 20 20 20 20 20 20 20
~ ~
¥. 1
% %
1
¥.
3lA 3Y2 4 4% 4%
~.
Raised Face
4lA 41Y, 5 5
Ring Joint
Diameter Nominal Outside of Diameter Length Pipe Bore Size
L
5Y2
41A -4 )12 5 5 5)12
6Y2 7Y2 7Y2
5~
5~
4Y.
6~
6lA 6
9lA
6~
7
4% 5 6lA
11 12Y2 15Y2
7Y2 7 3,4
7~
7Y2
8~
9
11~
9){ 10
9)12 lOY.
14Y2 16Y2
10~
11 ){
17~
11 ){
11~
12~
13 )12 141A
20 221A
5JA
1 Y. l1A 1 Y. 1% 1% 1% 1Y2 1% 1¥. 2 2Y2
29Y2 35Y2
13Y2 17 Y.
2~
37Y2
40lA
17Y2
3 3
18~
18lA
19Y2 20
18Y2 21 22 24lA 27
42~
18~
7~
17~
M
N
Y2 % 2!t\6
2YI 2~
9 0)
,~ rJJ
0)
12
'0.. C;
'8= 0 =
91A
24Y2 29Y2
0..
til
CIl 0)
a
12·20
JJ
1 1Y-t l,Y2 2 2Y2 3 4 5
6 8 10 12 14 16 18 20 24 26 28 30
352 eEl
1500 lb. FLANGES STANDARD ANSI B16.S 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, aHoy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified.
SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING.
Nominal Pipe Size
A ~
y.. 1 1~ 1~
2
...II
0
B
C
.88 1.09 1.36
2% 2% 2¥.
1.70 1.95 2.44
2~
~
I.
I
F: ~:
.~ e!~
a
1.lt~
SLIP· ON
JJ
a~.4~ II I I~ ~ I I ~ BLIND
Diameter of Hub at Base
D
E
G
H
1~
.84 1.05 1.32
lYl 1%
4% 5Ya
2~6
5~
1 1 Y.
2Y2
6~
lYa
2% 4Ya
7 8Yl
1 Y2
4¥.
1% ·1%
3~
1% 1%
4
2~
2.94 3.57 4.57
4Ya 4%
2~
4~
3~6
5.66 6.72 8.72
6Y.
4Y.
6% 8%
41~6
10.88 12.88
10 11 Y. 11 %
1.66 1.90 2.38
Outside Diameter Thickness of of Flange Flange
~
2Yl 3 4
~
WELDING NECK
Diameter of Hub at Point of Welding
Length Through Hub
Diameter of Bore
£:~~
I.
J ~
1~
~
~
Q,
>...a ."
II
2Yl
2.88 3.50 4.50
9% 10Yl
1%
5~
6%
12~
2Ya
5.56 6.63 8.63
7% 9 llYl
14%
2¥.
15Y2
3~
19
3%
10.75 12.75 14.00
14Yl 17% 19Y1
23 26Yl
4~
29Y2
5~
21%
32Yl 36 38% 46
5% 6% 7 8
1~
~
5 6 8 10 12 14 16 18 20 24
'u II
...
Q,
II
...a
~
-----
--
12~
12~
14 16
5% 6~
7Ya
------
16.00 18.00 20.00 24.00
23Y2 25~
30
4¥.
353
1500 lb. LONG WELDING NECK 1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in thickness J but is included in length M. 4. The length of bolts do not include the height of crown. S. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order. SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No. of Holes
Diam. of Bolts
Bolt Circle
K
%Raised Face
Ring Joint
Outside Diameter Nominal Diameter Length of Pipe Bore Size
L
M
N
4 4 4
4Yi 5 6~
8 8 8
1 1Y. 1~
7V2
6!4
6~
4¥.
2~
8
7
7
5~
9Y2
7~
7~
6~
3 4
8
1Y2 1~ 1%
11Y2 12Y2 15Y2
9~
9~
lOY.
10 Y2 .]2
1 ¥a 2
19 22Y2 25
12~
12
15
16 16
18Y2 21 23 27~
v..
1
12 12
16~
¥.
4 4 8
16 16 16 16
5
9
5Y2 ¥.
2~
5~
27~
30Y2 32~
39
11
J1
1~
2
12
5 6 8
14~
13 ~ 15 Yi
16
17
17Y2 19 Y2 21 Y, 24 J1
18Y2 20)1 22 )1
23Y2
25~
30
13~
1
10 12 14 21~ 25~
12-20
16 18
20 24
354
2500 lb. FLANGES STANDARD ANSI B 16. S
1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in dimensions C, D and J. 4. The lengths of stud bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Flanges bored to dimensions shown unless otherwise specified.
WELDING NECK
~~~'l~ ~I.~~I:====~==:::~--~ SLIP· ON
SEE FACING PAGE FOR DIMENSION K AND DATA ON BOLTING.
Nominal Pipe Size
A
~
y.. 1
ly.. 1~
2
Length Through Hub
Diameter of Bore
... tJ ;; -£... ~
Q.
B
C
.88 1.09 1.36
2% 3Y. 3Y2
1.70 1.95 2.44
3% 4% 5
2~6
2.94 3.57 4.57
5% 6% 7Y2
3Y. 3%
5.66 6.72 8.72
9 10% 12Y2
10.88 12.88
16V2
D
.
BLIND
Diameter of Hub at Point of Welding
Diameter of Hub at Base
E
G
.84 1.05 1.32
Outside Diameter Thickness of of Flange Flange
H
J
11~6
5~
1~6
2
5Y2
l~
2~
6~
1%
1.66 1.90 2.38
2%
7~
3~
8
3%
9~
1V2 1% 2
4V2 5~
10Y2 12
4~
2.88 3.50 4.50
6Y2
14
5Y. 6· 7
5.56 6.63 8.63
8 12
16V2 19 21%
5
14% 17%
26Y2 30
7~
1~6
11~6
1%
2% 2%
>.
2~
3 4
5 6 8 10 12
.a 'tJ tJ
cc 'utJ
...
Q.
tJ
.a ~
18~
9 10
10.75 12.75
9~
2~
2% 3 3% 4~
6V2
355
2500 lb. LONG WELDING NECK
I_lt~
H
I"
K
'" ~" ~~
1. All dimensions are in inches. 2. Material most commonly used, forged steel SA 105. Available also in stainless steel, alloy steel and non-ferrous metal. 3. The 1/4 in. raised face is not included in thickness J but is included in length M. 4. The length of bolts do not include the height of crown. 5. Bolt holes are 1/8 in. larger than bolt diameters. 6. Dimensions, M (length of welding necks) are based on data of major manufacturers. Long welding necks with necks longer than listed are available on special order.
~,,~~ ~
~t-N-
~
~
~
J
"
~~ ~
~
~
LL~
SEE FACING PAGE FOR DIMENSION J. Outside Diameter of Raised Face
Length of Bolts No. of Holes
Diam. of Bolts
Bolt Circle
K
H'.
14," Raised Face
Ring Joint
Diameter Nominal Outside of Diameter Length Pipe Bore Size
L
M
N
3Y2 3*
5~
5~
~
5~
5~
~
4~
%
5*
5~
2~
4 4 8
1 1 Y. 1
5Y. 5* 6*
6~
6Y2
7
7~
2~ 3~
7~
7Y2
3*
4Y. 5
8
7*
8
8~
9
9
9~
6~6
8
1 Y. 1 v.. 1 Y2
7~6
lOY.
8 8 12
'* 2 2
12* 14Y2 17v..
12 13'14 15 v..
12* 14 ~ 16
12* lS
12 12
2Y2 2*
21 v.. 24¥e
19 Y2 21 ~
22 ~
l'Yi6 2 2~
2¥. 3%
4 4 4
* *
8
10*
1ov..
10~
9
1 CI)
.~
V>
CI)
4Y2 5 v.. 6Y2
0..
'S,. ~
12
's'" 0
'"
1¥.t 1~
2 2~
3
4
V>
CIS
8Y2
20~
8 9
CI)
E CIS
v..
CIl
12 14* 17¥e
12-20
5 6 8
10 12
356
RING JOINT FLANGES
r~=t
APPROXIMA TE DISTANCE BETWEEN FLANGES
t.~
Nominal Pipe Size
X
150
Pressure Rating lb.
300
400
Va
Va
Va
Va
-
U2
U2
U2
%2 5/ /32 5/ / ~2
~{2 ~{~
1
/32
1~
~{2 ~{2 5/ /32
/32
~'32 J{6
"!{2
U6
?{2
J{6 ?{2
1X 2 2/-2 3
1500
900
2500
Distance, inches 5/ /32 5/ -32 5/ /32 5/ .I 32
%
600
5/
/32 5/
~{2 ~{2
1/
S/
/32
~{6 ~{6
~32 ~2
K6
5/ 732
5/ /32
~32
~2
6 8 10 12 14 16 18 20 22 24
5/ /32
/32
K2
5/ /32
K2
?{2
~2
J{6
~2
5/ /32
?{z ?{z
!{2
K6
732
Va
7/ /31
~/
/)2
I/.
/a
Va Va Va
~2
~2 ~2
~{2
!{2
~2 ~
~2 ~ ~
X
~{6
K6 K6
~2 ~2
-
-
!{2
}\6
J{6
%2
K~ ~
s/
716
~2 ~6 ~6
~2 ~2
3{6
~l2 ~l2
K6
$/
J{6 -
Va Va Va Va
5/ 732
/32 7/
Va
U2
3{6 J/ /16 3/ ;16
~{2
K2
732
Va Va Va Va Va Va
Va Va
K2
~~2
$/
~32 ~32
5/ /32
$/
732 5/ 732
~~2 ~32
U2
4 5
7/
-
-
-
%
RING NUMBERS Nominal Pipe Size
..QJ .c• /a /a QJ «I
=.-
Q.,U
150 300,400,600 900 1500 2500 Nominal Pipe Size
QJ
.. .c• /aQJ /a«I
=-
~u
150 300,400,600 900 1500 2500
3.4
11A 1Y2 2 2Y2 3 3Y2 .. ... R15 R17 R19 R22 R25 R29 R33 Rll R13 R16 R1B R20 R23 R2& R3l R34 .. . ,. ... .. .. . ... . .. R3l .. R12 R14 R16 - .- R1B r-R20 R24 R27 R35 ... R13 R16 RIB R21 R23 R26 R2B R32 ...
Vi
1
. .
.
.
4
R3& R37 R37 R39 R3B
5
6
8
10
12
14
16
18
20
24
R40 R41 R41 R44 R42
R43 R45 R45 R46 R47
R4B R49 R49 R50 R51
R52 R53 R53 R54 R55
R5& R57 R57 R58 R60
R59 R&l R62 R63
R64 R65 R66 R67
R&8 R69 R70 R71
R72 R73 R74 R75
R76 R77 R78 R79
... ..
,
. .. ... ...
357 A
~
~ '" a: r
~
t-
w
r
C
~t-
R
,,'
STUDDING OUTLETS All dimensions are in inches. Material most commonly used, forged steel SA-105.
150lb SIZE lliICK (BORE) B T 1/2 3/4 1 11/4 11/2 2 21/2 3 31/2 4 5 6 8 10 12 14 16 18 20 24
1.50 1.50 1.50 1.50 1.50 1.75 1.75 1.75 1.75 1.75 2.00 2.00 2.00 2.25 2.25 2.56 2.56 2.75 2.75 3.00
aD A 3.50 3.88 4.25 4.62 5.00 6.00 7.00 7.50 8.50 9.00 10.00 11.00 13.50 16.00 19.00 21.00 23.50 25.00 27.50 32.00
RF STUD STUDS aD CIRCLE NO. SIZE TPI R C J M I 1.38 1.69 2.00 2.50 2.88 3.62 4.12 5.00 5.50 6.19 7.31 8.50 10.62 12.75 15.00 16.25 18.50 21.00 23.00 27.25
2.38 2.75 3.12 3.50 3.88 4.75 5.50 6.00 7.00 7.50 8.50 9.50 11.75 14.25 17.00 18.75 21.25 22.75 25.00 29.50
4 4 4 4 4 4 4 4 8 8 8 8 8 12 12 12 16 16 20 20
1/2 1/2 1/2 1/2 1/2 5/8 5/8 5/8 5/8 5/8 3/4 3/4 3/4 7/8 7/8 1 1 11/8 11/8 11/4
13 13 13 13 13 11 11 11 11 11 10 10 10 9 9 8 8 8 8 8
TAP HOLE DEPlli DEPlli E F 0.75 0.75 0.75 0.75 0.75 0.94 0.94 0.94 0.94 0.94 1.12 1.12 1.12 1.31 1.31 1.50 1.50 1.69 1.69 1.88
1.25 1.25 1.25 1.25 1.25 1.50 1.50 1.50 1.50 1.50 1.75 1.75 1.75 2.00 2.00 2.31 2.31 2.50 2.50 2.75
300lb SIZE lliICK (BORE) B T 1/2 3/4 1 11/4 11/2 2 21/2 3 31/2 4 5 6 8 10 12 14 16 18 20 24
1.50 1.75 1.75 1.75 2.00 1.75 2.00 2.00 2.00 2.00 2.00 2.00 2.25 2.56 2.75 2.75 3.00 3.00 3.00 3.44
aD A 3.75 4.62 4.88 5.25 6.12 6.50 7.50 8.25 9.00 10.00 11.00 12.50 15.00 17.50 20.50 23.00 25.50 28.00 30.50 36.00
RF STUD STUDS aD CIRCLE NO. SIZE TPI R C J M I 1.38 1.69 2.00 2.50 2.88 3.62 4.12 5.00 5.50 6.19 7.31 8.50 10.62 12.75 15.00 16.25 18.50 21.00 23.00 27.25
2.62 3.25 3.50 3.88 4.50 5.00 5.88 6.62 7.25 7.88 9.25 10.62 13.00 15.25 17.75 20.25 22.50 24.75 27.00 32.00
4 4 4 4 4 8 8 8 8 8 8 12 12 16 16 20 20 24 24 24
1/2 5/8 5/8 5/8 3/4 5/8 3/4 3/4 3/4 3/4 3/4 3/4 7/8 1 11/8 11/8 11/4 11/4 11/4 11/2
13 11 11 11 10 11 10 10 10 10 10 10 9 8 8 8 8 8 8 8
TAP HOLE DEPlli DEPlli E F 0.75 0.94 0.94 0.94 1.12 0.94 1.12 1.12 1.12 1.12 1.12 1.12 1.31 1.50 1.69 1.69 1.88 1.88 1.88 2.25
1.25 1.50 1.50 1.50 1.75 1.50 1.75 1.75 1.75 1.75 1.75 1.75 2.00 2.31 2.50 2.50 2.75 2.75 2.75 3.19
359
~ 1:
a:
it....
A
~w
C
r
STUDDING OUTLETS
A
"
It I-
All dimensions are in inches. Material most commonly used, forged steel SA-lOS.
1500lb SIZE rnICK (BORE) T B 1(2 3/4 1 11/4 11/2 2 21(2 3 4 5 6 8 10 12 14 16 18 20 24
2.19 2.19 2.44 2.44 2.75 2.44 2.75 2.94 3.19 3.62 3.44 3.88 4.31 4.56 5.00 5.50 5.94 6.38 7.31
OD A 4.75 5.12 5.88 6.25 7.00 8.50 9.62 10.50 12.25 14.75 15.50 19.00 23.00 26.50 29.50 32.50 36.00 38.75 46.00
RF STUD STUDS OD CIRCLE NO. SIZE TPI J I C M R 1.38 1.69 2.00 2.50 2.88 3.62 4.12 5.00 6.19 7.31 8.50 10.62 12.75 15.00 16.25 18.50 21.00 23.00 27.25
3.25 3.50 4.00 4.38 4.88 6.50 7.50 8.00 9.50 11.50 12.50 15.50 19.00 22.50 25.00 27.75 30.50 32.75 39.00
4 4 4 4 4 8 8 8 8 8 12 12 12 16 16 16 16 16 16
3/4 3/4 7/8 7/8 1 7/8 1 11/8 11/4 11(2 13/8 15/8 17/8 2 21/4 21(2 23/4 3 31(2
10 10 9 9 8 9 8 8 8 8 8 8 8 8 8 8 8 8 8
HOLE TAP DEP1H DEP1H E F 1.12 1.12 1.31 1.31 1.50 1.31 1.50 1.69 1.88 2.25 2.06 2.44 2.81 3.00 3.38 3.75 4.12 4.50 5.25
1.75 1.75 2.00 2.00 2.31 2.00 2.31 2.50 2.75 3.19 3.00 3.44 3.88 4.12 4.56 5.06 5.50 5.94 6.88
2500lb SIZE rnICK (BORE) B T 1(2 3/4 1 11/4 11(2 2 21(2 3 4 5 6 8 10 12
2.19 2.19 2.44 2.75 2.94 2.75 2.94 3.19 3.62 4.12 4.56 4.56 5.50 5.94
OD A 5.25 5.50 6.25 7.25 8.00 9.25 10.50 12.00 14.00 16.50 19.00 21.75 26.50 30.00
. STUDS RF STUD OD CIRCLE NO. SIZE TPI R C J M I 1.38 1.69 2.00 2.50 2.88 3.62 4.12 5.00 6.19 7.31 8.50 10.62 12.75 15.00
3.50 3.75 4.25 5.12 5.75 6.75 7.75 9.00 10.75 12.75 14.50 17.25 21.25 24.38
The studding outlets tabulated comply with the requirements of ASME Code Sect. VIII. Div. 1. The tabulated dimensions of thickness, T are the minimums
4 4 4 4 4 8 8 8 8 8 8 12 12 12
3/4 3/4 7/8 1 11/8 1 11/8 11/4 11(2 13/4 2 2 21(2 23/4
10 10 9 8 8 8 8 8 8 8 8 8 8 8
TAP HOLE DEP1H DEP1H F E 1.12 1.12 1.31 1.50 1.69 1.50 1.69 1.88 2.25 2.62 3.00 3.00 3.75 4.12
1.75 1.75 2.00 2.31 2.50 2.31 2.50 2.75 3.19 3.69 4.12 4.12 5.06 5.50
required. The outlets are available also in stainless and other alloy steels. Air test holes are optional.
360 NOTES
361
ua .-
A ---I
90° Long Radius Elbow
~:""""::...:...,...,I;Z-..;.;';;';';';~~~
WELDING FITTINGS 1.
ANSI B 16.9 All dimensions are in inches.
2.
Welding fitting material conforms to SA 234 grade WPB.
3. 4.
Sizes 22, 26 and 30 in. are not covered by ANSI B 16.9 .
5.
90° Long Radius Reducing Elbow _
For wall thicknesses see page 322. Dimension F} applies to standard and X-STG. caps. Dimension F2 applies to heavier weight caps.
Nominal Pipe Size
Dimensions Outside
Diameter
0.840 1.050
1fA,,,
~UJ~
c
D
F/s
....
B
A
7h6
Pl1I6
E
1 ....
1Y2 ....
1315
lY2
7/s
23!t6
1
1%
1~
lY2
1.660
Fls
1
2%
lY4
2 11I6
l~
lY2
1.900
2V4
Ills
3V4
1~
27116
1~
1~
2.375
3
Pis
4 1I6
2
3
3 1I6
lY2
1~
2~
2.875
3~
1~
3
5 !t6
2Y2
15
3 !t6
lYz
2
3
3.500
4Y2
2
6Y4
3
4%
2
2Y2
4.000
5V4
2Y4
7Y4
3~
5Y2
2~
3
4
4.500
6
21;2
8Y4
4
6V4
2Yz
3
5
5.563
7~
31/8
10 5!t6
5
7%
3
3Yz
6
6.625
9
3%
12 15/16
6
95h6
3~
4
8
8.625
12
5
I 65!t6
8
12 5/16
4
5
15
1
614
20 k
10
I 5 /s
5
6
12
18 3/8
6
7
IV4
.--,,~
45° Long Radius Elbow 2
~.7 . ~.
lffTYili ~AJ-A-' 1800 Long Radius Elbow
10 90° Short Radius Elbow
180° Short Radius Return
Cap
10.750
3
3
3
12
12.750
18
1h
24 3/8
14
14.000
21
8%
28
14
21
6~
1h
16
16.000
24
10
32
16
24
7
8
18
18.000
27
llY4
36
18
27
8
9
20
20.000
30
12~
40
20
30
9
10
22
22.000
33
13Y2
44
10
10
24
24.000
36
15
48
1O~
12
26
26.000
39
16
52
1O~
... .
30
30.000
45
18~
ffi
24 30
36
45
lOY2 ... .
362
WELDING FITTINGS 1. 2. 3. 4.
~ r-t--
ANSI B 16.9 All dimensions are in inches Welding fitting material conforms to SA 234 grade WPB. Sizes 22,26 and 30 in. are not covered by ANSI B 16.9. For wall thicknesses see page 322.
Nominal Pipe Size
Yz
Yz 3/S
%
%
Yz 1
1 %
Yz
114
}li4
1 %
Yz
lYz
IY2 114 1 %
Y2
2
2
lYz 114 1 %
2Yz
2Yz 2
lYz Pi4
3
1 3
2Yz 2
lYz 114
3Y2
3Yz 3
2Yz 2
lYz 4
4
3Yz 3
2Yz 2
lYz
Outside Diameter .840 .675 l.050 .840 1.315 l.050 .840 l.660 1.315 1.050 .840 l.900 1.660 1.315 1.050 .840 2.375 l.900 l.660 1.315 1.050 2.875 2.375 l.900 l.660 1.315 3.500 2.875 2.375 l.900 l.660 4.000 3.500 2.875 2.375 1.900 4.500 4.000 3.500 2.875 2.375 l.900
+
[G.~J
Dimensions Outlet
f
G
I
Tee G
H
J
1 1 Jl/s 11/S
1 1 11/s 11/s
· ... · ... , ...
lYz lYz lYz
lYz lYz lYz
· ... 2 2
P/s P/s P/s P/s 214 214 214 214 214
P/s P/s P/s P/s 214 214 214 214 214
....
2Yz
....
2Yz 2Yz 2Yz 2Yz 2Yz 3 3 3 3 3 3% 3% 3% 33/8 ]3/8 3% 3% 3% 3% 3% 41/8 41/8 4 1/s 4 1/s 4 1/s 4 1/s
23/8 21/8 2 1% 3 2% 25/s
2Yz
214 V/8 314 3 27/8 2% 3% 35/8
3Yz
31;4 31/8 4 1/s 4 37/s 3%
3Yz
33/s
,
lYz
2 2 2
· ... 2Yz 2Yz 2Y2 2Y2 3 3 3 3
· , ..
3Yz 3Yz 3Yz 3Yz .... 3Yz 3Yz 3Yz 3Yz .... 4 4 4 4
.... 4 4 4 4 4
I
~
f---t-
lG-~GJ Reducing Tee
[J]
S
Concentric Reducer
LJl '---
----
Eccentric Reducer
363
F'---t_.l ,
WELDING FITTINGS
f
G
[c.-J
ANSI B 16.9 All dimensions are in inches Welding fitting material confonns to SA 234 grade WPB. Sizes 22, 26 and 30 in. are not covered by ANSI B 16.9. For wall thicknesses see page 322.
1.
2 3. 4.
Nominal Pipe Size
I
Tee
5
,
!
?
~.--t-
6
lc-~cJ Reducing Tee
8
I
I
I
[Jl
10
-'-'--
12
-
-
.--..I
Concentric Reducer
eJl '-'-
14
16
-.-.
18
Eccentric Reducer
Outlet 5 4 312 3 212 2 6 5 4 312 3 212 8 6 5 4 312 10 8 6 5 4 12 10 8 6 5 14 12 10 8 6 16 14 12 10 8 6 18 16 14
Dimensions Outside G Diameter 47/8 5.563 47/8 4.500 47/8 4.000 47/s 3.500 47/8 2.875 47/8 2.375 55/8 6.625 55/8 5.563 55/8 4.500 55/8 4.000 55/8 3.500 55/8 2.875 7 8.625 7 6.625 7 5.563 7 4.500 7 4.000 10.750 8.625 6.625 5.563 4.500 12.750 10.750 8.62.5 6.625 5.563 14.000 12.750 10.750 8.625 6.625 16.000 14.000 12.750 10.750 8.625 6.625 18.000 16.000 14.000
8Yz 8Yz 8Yz 812 812 10 10 10 10 10 11 11 11 11 11 12 12 12 12 12 12 13Y2 1312 1312
H
J
47/8 45/8 4'h 43/8 4Y4 4 1/8 55/8 53/8 51/8 5 47/8
....
4~
5 5 5 5 5
.... 5Y2 512 5Y2 512 512
7 65/8 63/8 6 1/8 6
....
812 8 75/8 712 7Y4 10 9Y2 9 8 5/8 8Y2 11
....
10 5/8 10 1/8
13 13 13 13
9~
93/8 12 12 11 5/8 111/8 10~
10 1/8 1312 13 13
6 6 6 6 7 7 7 7
.... 8 8 8 8
...
.... 14 14 14 14 14
.... 15 15
364
WELDING FITTINGS 1.
2 3. 4.
rL,
ANSI B 16.9 All dimensions are in inches Welding fitting material conforms to SA 234 grade WPB. Sizes 22, 26 and 30 in. are not covered by ANSIB 16.9. For wall thicknesses see page 322.
Nominal Pipe Size
r'---L.--
Outside Diameter
I
Tee
G
H
J
15 15 15
18
12 10 8
12.750 10.750 8.625
13'lS 13'lS 13'lS
12 5/8 12'/8 11%
20
20 18 16 14 12 10 8
20.000 18.000 16.000 14.000 12.750 10.750 8.625
15 15 15 15 15 15 15
15 14Y:z 14 14 13 5/8 13'/8 12%
.'
22 20 18 16 14 12 10
22.000 20.000 18.000 16.000 14.000 12.750 10.750
16'lS
.,
16'lS 16'lS 16Y:z 16Y:z 16Y:z
16'lS 16 15Y:z 15 15 14 5/8 14'/8
24 22 20 18 16 14 12 10
24.000 22.000 20.000 18.000 16.000 14.000 12.750 10.750
17 17 17 17 17 17 17 17
17 17 17 16Y:z 16 16 15 5/8 15'/8
30 24 22 20 18 16
30.000 24.000 22.000 20.000 18.000 16.000
22 22 22 22 22 22
22 21
22
24
30
+
[G+-J
Dimensions Outlet
t
G
16Y2
2OY2
20 19'1S 19
..
20 20 20 20 20 20
I
--+-
,•
,
H
I
lG--GJ
Reducing Tee
..
20 20 20 20
.... .. ,.
.... 20 20 20 20 20 20 20
E3
Concentric Reducer
.. 24 24 24
.,
...
[I]
ell '---'-'
,
.... Eccentric Reducer
365
at
FACE-TO-FACE DIMENSIONS OF FLANGED STEEL
GATE VALVES (WEDGE AND DOUBLE DISC) Pr.ssur., lit. per Sq. In. Nominal Sill, Inch.s
150
1
-
1~
1~
2
.,
2~
300
-
-
9~
1~
2 2)12
.-
11~
11~
13
14
14
llY.
-,:t
4 5 6 8 10 12 1400 1600 1800 2000 2400
9 10 10)12 11~
13 14 15 16 17 18 20
16 18 19)12
I
23~
18
26~
19~
30
30 33 36 39 45
32~ 35~ 38~
41 )12 48)12
PrlSsur., Lb. per Sq. In.
Nominal
150
Inches
-
9~
13
llYa 12 15 15Ya 16)12
-
1~
9~
8
Siz',
1
8~
8~
~
8)12 9
7 7)12
3~
.,... ·S
8~
7)12
._~~_l 400
-
--
Dim.nsion A, Inches
1
5~
1~
1)12
6 7
2
7~
8
.,
1500
I
2500
Dimlmion A, Inches
I
10 11 12 14)12
10 11 12 14~
17~
16~
16~
20
15 18 22 24 29 33 38 40)12 44)12
12Y. 13~
15Ya
18~
22~
21 )12 26)12
31~
27~
36
26)12
32~
40~
39 44)12 49)12 54)12
50 56
60~
48 52 61
65~ 76~
-
-
-
I HOminal Size, Inches
8~
8~
1
9
9
1~
9~
9~
1)12
~~.~~~. 900- ...
_-1~_~=r2s00-
Dimension A, Inches
10 11 12
10 12Ve 11 13Ya 12 15~ 14Y. 17Ya -16Ys 20~ ~---- 1 - - - ' _ 18Ys 23. 21 Y. 26Ya 26Y. 31% 36)12 28
2 14Y. 9Y. llY. 11Y. lOY. 2~ 16Y. 13Y. 13Ve ._-1--' 3 11~ 15Y. 14Y. 14Y. 4 12Y. 18Ve 16Y. 17Ve 22Y. 15Y. 5 18Y. 20Ya 16)12 19Y. 22Y. --~-- - -24Y. --"40j~ 29Y. - 33Y. 17Y. 8 23Y. 26Y. .-'--33Y. -- 39Ye 50Ya 18Y. 26Y. 31---"-Ya _ 1 0 _ ------- - - - - -_ .... _45Y. 38Y. 56Ya 20Ye 30Y. I 33Y. 1~_ ---_ .. _- - 14 40Ya 50~ 30Y. 32Y. 35Y. f---- - - -.-..... 16 44Ya 5SYe 33Y. 3SY. 39Y. ----"- t-48)12 18 61Ye 36Y. 38Y. I--43Y. -- - - - ----------- - . - - -=--
2~ 8 3 8~ 4 9~ Q, >010)12 S to11 6 CI' c: 8 12 &i2 10 13~ 14)12 12 14 IS~ 16)12 16 18- - - 1----.... 17~-t--39~1-41 ~ -- 47~ 20 "8~ -20)12 24 4Sv.-T48Ya 55Y.
c:
'0
I
900
3 4 5 6 8 10 12 14 16 18 20 24
17 20 22 26 31 33 35 39 43 47 '55 600
Pr.ssur., Lb. per Sq. In.
Nominal Sil., InchIS
9
-
3
CI
600
DimlllSion A, Inches
.....
w
400
--~.
_.
-
-~---
20 24
52)12
66Ye
61~
nY.
-
-
366
~m
I
FACE·TO·F ACE DIMENSIONS OF FLANGED STEEL
GLOBE AND ANGLE VALVES
J,-
~2XA...j
~
\
-t
.~
-A-
Raised Face Class,lb Nominal SiZI, InchlS
V, ~
1 lY. ,V, 2 2V, 3 3V, 4 5 6 8
300
150
400
600
Dimension 2 x A, Inchls
-
-
-
-
10V, 11 V, 12V, 13Y. 14
8 8V, 9V, 10V, 11 V, 14 16 19V,
-
-
v,
7V, 8V,
~
9V, 11 V, 13 14
7V, 8V, 9 9V, 11 V, 13 14
-
-
9
-
17 20 22 26
16 18 19V, 23V,
15~
17V, 22
Nominal Sin, InchlS
Lb. Sq. In. - -900 PrlsSun,15~ 2500_ JIll'
Dimlnslon 2 x A, Inchls
1 lY. ,V, 2 2V, 3 4 5 6 8 10 12 14
9 10 11 12 14V, 16V, 15 18 22 24 29 33 38 40V,
9 10 11 12 14V, 16V, 18V, 21 V, 26V, 27~ 32~
39 44V, 49V,
lOY. 10~
12Y. 13~
15Y. 17~
20 22~
26V, 31Y. 36 40Y. 50 56
-
Ring- Type Joint Nominal Siz., Inch.s
V,
PrISS,":'! Lb. per Sq. In.
f---
300
150
I
400
I
600
Dimension 2 x A, Inches
-
I
6K, 6K,c _ 6K, 7V, 7V, 7V, 8V, 8V, 1 8V, -lY. 9 9 _._- - .9 ,V, 9V, 9V, 9V, 7 2 8Yi 11Y. 11Y. 1lY. - - - - - ->-2V, 9 12Y. 13Y. 13Y. 3 13Y. 14Y. 14Ya 4 12 104Y. 16Y. 17Y. ----5 14Yi"--- -16Y. 20Y. - - - -c------ -1lBY. 16V, 6 lBY. 19Y. 22Y. 8 20 22Ya 23Y. 26Y. 10 25 25Y. 26Y. 31 Y. 12 2B 2BY. 30Y. 33Y. 14 31 Yi16 36V, -
-~
-
~--
-
-
Nominal Size, Inches
Pr.ssure, lb. per Sq. In. f---
900 __ 1.~_~-=-r=.2500
WL
Dimension 2 x A, Inches
-
V,
- - -~ - - - f - -9- . -
1 lY. ,V,
10 11 12 104Y. 16Y. 15Y. lBY. 22Y. 204Y. 29Y. 33Y. 3ay. 40Ye
2 2V, 3 4 5 6 8 10 12 14
I
9 10 11 12 14Y. 16Y. lBY. 21 Y. 26Ya 2B 33Y. 39Y. o4SY. SOY.
10% __'2Y. 13Ye 15Y. 17Ye 20Y. - -23 --26Ye--_ .. 31~
36V, 40Ye 50Ye 56Ye
-
367
m
I
-~-~-
FACE..TO-FACE DIMENSIONS OF FLANGED STEEL
SWING CHECK VALVES
00
•
~A~
Raised Face Pressure, lit. per III- In.
Nominal
Siz.,
150
400
600
Dimltlsion A. Inches
Inches 2 2)4
300
Nominal Sin, Inches
8 8)4
10)4
11)4
11)4
)4
11)4
13
13
~
14
14
Pressure, lit. per Sq. In.
2500
1500
900
Dimension A, Inches
-
-
lOY.
9
9
10~
1
10
10
12Y.
1~
11
11
13~
1)4
12 14)4
12 14)4
lSY.
16)4
16)1
20
9)4
12)4
3Yt
10)4
13~
4
11)4
14
S
13
lS~
6
14
17)4
19}1
22
21
23Yt
26
lSVz
22~
26Vz
31
3 4
15
24Yt
lS
26)4
28
30
33
S
22
21Vz 26)1
6
24
27~
36
8
29
32~
40~
10
33
50
12
38 40)4
39 44)1
3
8 10 12
-
-
-
16
17
-
-
2 2)4
14
17~
31~
56
-
49Vz
Ring Type Joint Pressure, Lb. per Sq. In.
Nominal SiZt,
150
Inches
300
I
400
I
600
Dimension A, Inches
-
6U.
6U.
Vz
7Vz
7Y2
~
)4
4 13l.
~
1
SY. 5)4
1~
6
1Vz
9)1 7._- r--10-- f - - - -1--. - llY. llY. sVz r-llY. --
2 --2Vz 3
9 10
4
12
5
13Vz
6
9 9)4
NomiMI Size, Inches
1----
2500
-
-
lOY.
9
9
10~
8Vz
1
10
10
12Y.
9 --9)1
9
1~
11
11
13Va
1)1
12
12
lS~
14Y.
14Y.
17Va
16Y.
16Y.
20~
lSY.
lSY.
23
13Y.
13Y.
13Y. - .- - - t -14Y. 14Y. 16Y.
14Y.
3
17Y. --lay. 16Y. 20Y. ----- t--- '-- r - - - 19% lSY. 22Y. f-- --
14Vz ---=--S 20 23% 26Y. - - - - - - 1 -21- Y. - - -1---10 26Y. 25 25Y. 31 Y. -- ._- I-- - - - 1------- t - - . - - 12 30Y. 33Y. 2S . - 28Y. ..--14 31)1 -~
-
1500 Dimension A, Inches
8Vz
2 2)1
12Y.
Press...e, lb. per Sq. In.
900
-
-
4
lSY.
21%
26Va
5
22Y.
26Y.
31~
6
24Y.
8
36Vz - - - e-------=-- f - 28 40Va 29Y. 33Y. f------
10
33Y.
39Y.
50Va
12
3SY.
4SY.
S6Va
14
40Va
SO~
-
Reference: Face-to-Face and End-to-End Dimensions of Ferrous Valves American National Standard ANSI 816.10-1973
368
g
SCREWED COUPLINGS
Full Coupling
1. All dimensions are in inches. 2. Material forged carbon steel conforms to the requirements of Specification SA-lOS. 3. Threads comply with ANSI Standard B2.11968.
111 I-A-J
Half Coupling Half Coupling
Full Coupling
Nominal Pipe Size
6000lb
3000lb
6000lb
3000lb
Length Diameter Length DiameteI Length B A A A B
Diameter Length B A
DiameteJ B
1/8
1 1/4
3/4
1 1/4
7/8
5/8
3/4
5/8
7/8
1/4
1 3/8
3/4
1 3/8
1
11/16
3/4
11/16
I
3/8
1 1/2
7/8
1 1/2
1 1/4
3/4
7/8
3/4
I 1/4
1/2
1 7/8
I 1/8
1 7/8
1 1/2
15/16
1 1/8
15/16
I 1/2
3/4
2
I 3/8
2
1 3/4
1
1 3/8
1
1 3/4
1
2 3/8
1 3/4
2 3/8
2 1/4
13/16
1 3/4
13/16
2 1/4
1 1/4
2 5/8
2 1/4
2 5/8
2 1/2
1 5/16
2 1/4
1 5/16
2 1/2
1 1/2
3 1/8
2 1/2
3 1/8
3
1 9/16
2 1/2
19/16
3
2
33/8
3
33/8
3 5/8
1 11/H
3
I 11/16 3 5/8
2 1/2
3 5/8
3 5/8
3 5/8
4 1/4
1 13/16
3 5/8
1 13/16 4 1/4
3
4 1/4
4 1/4
4 1/4
5
2 1/8
4 1/4
2 1/8
5
3 1/2
4 1/2
43/4
4 1/2
53/4
2 1/4
43/4
2 1 /4
53/4
4
43/4
5 1/2
43&4
6 1/4
23/8
5 1/2
23/8
6 1/4
369
SYMBOLS FOR PII~E FITTINGS American Standard: ANSI Z32.2.3 Flanged Bushing
Screwed
Bell and Spigot
-D-.
'E----i-
--3
Cap Cross Reducing Straight Size
Crossover Elbow
45- Degree
.~
~
Welded
..-
Soldered
$
~
~ ~ 'T. I
.~
+ +*+ + t
fJ\i
Y'E
(
t
(
t
90 - Degree
~
r rC r
Turned Down
G-t
G--+
G-E
~
G-&
Turned Up
&t
@--+-
~
&*
e-e-
C*
~
Base
Double Branch
L. ~ '4 +-r T
Long Radius
F'
~
Reducing
~
~
Side Outlet (Outlet Down) Side Outlet (Outlet Up)
~
r
r
~ ~ ~
1
370
SYMBOLS FOR PIPE FITTINGS
Flanged
Screwed
Bell and Spigot
Welded
le
Street
Soldered
Joint Connecting Pipe Expansion
-+-
~
-€-
"*-
-e-
t::::::=I-
-E:3-
-:£:::f
-a::::JE7
Lateral
r y r
~
Orifice Plate
-1:1-
Reducing Flange
-iD--
Plugs Bull Plug
-to
Pipe Plug
t
C> ----t<:J
(
-IC>t- -
--t:>+-
~
~
~
-i~
~
~
~
€t::::.e-
-+-+-
-++-
-3---E-
*--*-
-e----&
Tee Straight Size
~
~
~
't'
xL
~
(Outlet Up)
t-0-iI-
+-0-+
7--0--t-
*07(
-e0-e-
(Outlet Down)
+-e-t
+-e-t
~
~
-e-e-e-
Double Sweep
~
~
Reducer Concentric Eccentric
Sleeve
Reducing
rL L
~ ~ ~
371
SYMBOLS FOR PIPE FITTINGS
Flanged
Screwed
Single Sweep
*T t
Side Outlet (Outlet Down)
....L
Side Outlet (Outlet Up) Union Valves Angle Valve Check, also Angle Check
Bell and Spigot
~
~
~ ~
~
-+t--
Welded
~
--4-
? ? ?
Soldered
-eje-
? ?
Gate, also Angle Gate (Elevation) Ball Valve Gate, also Angle Gate (Plan)
~
r-
iC«Jr
-te::J-
G::l-
(3:::J-
Globe, also Angle Globe (Elevation)
l?- lr-
F
~
Globe (Plan)
@:]-
~
(3:::J3-
Automatic Valve By-Pass GovernorOperated Reducing
(* ~
(3::::)(-
00-
~
-t-11
Check Valve (Straight Way)
-I'J-
~
~
~
~
Cock
-II{11-
~Q~
--3QE-
~Q~
-BQe-
372
-
SYMBOLS FOR PIPE FITTINGS
Diaphragm Valve
Flanged
Screwed
~
-Jr
,.-, Float Valve Gate Valve Motor-Operated Globe Valve Motor-Operated Hose Valve, also Hose Globe Angle, also Hose Angle Gate Globe Lockshield Valve
I Cl
Bell and Spigot
:-21
-t*J-
-ckl-
-[>
-(>
-*-
~
--IXr
-{XJ-
~
~
~
~
-[>¢J
--t>¢J
-I>¢J
--(>::l::l
Welded
Soldered
r-ll~
~
r-~
~
~
~
-E{>
-J!~
~
-€t,)r"'...&
~
k
--tt.- -Jr-
Plu, Valve
~
-c-:J-
.~~
Quick Opening or Butterfly Valve
~
~
~
~
~
~
~
-€1*9-
Safety Valve
~
374
WEIGHTS
1.
The tables on the following pages show the weights of different vessel components made of steel.
2.
All weights are calculated with the theoretical weight of steel: 1 cubic inch = 0.28333 pounds.
3.
To obtain the actual weight of a vessel, add 6% to the total weight. This will cover the overweights of material which comes from the manufacturing tolerances and the weight of the weldings.
4.
The weights of shells shown in the tables refer to one lineal foot of shell-length. The weights tabulated in columns headed by "I.S." and "O.S." are the weights of shell when the given diameter signifies inside or outside diameter.
5.
The weights of the heads include: A. For ellipsodial heads: 2 inch straight flange or the wall thickness, whichever is greater. B. For ASME flanged and dished heads: lY2 inch straight flange. C. For hemispherical heads: 0 inch straight flange.
6.
The weights of pipe fittings made by different manufacturers show in many cases considerable deviations, which reflect manufacturing differences. The weights of pipe fittings shown in these tables refer to the products of Ladish Company.
7.
All dimensions in inches. All weights in pounds.
375
WEIGHT OF SHELLS & HEADS WALL THICKNESS
1/4"
DIAM. VESSEL
5/16" HEAD
SHELL
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
20 28 36 46 56
41 48 54 61 68
39 46 52 59 66
28 35 41 51 58
19 24 29 35 43
26 35 46 58 71
41 47 55 62 70
68 81 95 110 126
74 81 88 94 101
72 79 86 92 99
69 78 87 100 114
51 58 69
85 101 119 138 158
100 113 128 139 156
80 89 98 110 120
143 161 180 201 222
108 114 121 128 134
106 112 119 126 133
129 144 160 177 195
123 138 150
179 202 226 256 279
11 1 127 143 159 175
165 215 270 330 398
131 168 210 257 309
245 320 404 498 602
141 161 182 202 222
139 159 179 199 219
214 285 351 434 520
163 210 263 322 386
307 400 506 624 755
96
193 209 225 241 257
191 207 223 239 255
453 543 624 723 820
365 421 492 556 637
717 840 974 1118 1272
243 263 283 303 324
239 259 279 299 319
598 695 806 925 1050
456 532 614 702 796
897 1052 1220 1399 1592
102 108 114 120 126
273 289 305 321 337
271 287 303 319 335
922 1031 1150 1255 1445
710 801 883 984 1075
1435 1608 1792 1985 2188
344 364 385 405 425
339 359 379 399 419
1180 1320 1468 1622 1820
896 1001 1104 1230 1344
1796 2013 2242 2484 2738
132 138 144
353 369 385
351 367 383
1590 1730 1880
1186 1286 1406
2401 2624 2856
446 466 486
439 459 480
1990 2160 2350
1482 1607 1758
3004 3282 3573
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
ELLIP F.&D. HEMIS
HEAD
I.S.
O.S.
33 38 44 49 54
31 36 42 49 52
22 28 33 41 47
14 19 23 28 35
60 65 70 76 81
58 63 68 74 79
55 62 70 78 89
86 92 97 102 108
84 90 95 100 106
113 129 145 161 177
78
87 100 III
376
WEIGHT OF SHELLS & HEADS WALL THICKNESS
3/8"
DIAM. VESSEL
SHELL I.S.
12
O.S.
50 58 66 74 82
47 55 63 71 79
90 98 106 114 122
87 95 103
7/16"
HEAD
SHELL
ELUP F.&D. HEMIS
HEAD ELUP F.&D. HEMIS
I.S.
O.S.
58 67 77 86 95
54 63 73 82 91
41 49 61 71 85
26 33 41 52 61
37 50 65 82 100
33
22
42 50 61 70
28
35 42 52
32 43 55 70 85
119
82 94 105 121 137
61 70 82 94 105
103 122 143 166 190
105 114 123 133 142
101 110 119 129 138
97 109 122 141 160
71 82 97 109 122
121 143 168 194 223
130 138 146 154 162
127 135 143 151 159
154 173 192 213 234
121 134 147 165 180
216 243 272 303 336
151 161 170 179 189
148 157 166 176 185
180 191 224 248 273
141 156 172 192 210
253 285 319 355 393
170 194 218 242 266
167 191 215 239 263
257 331 415 508 610
196 252 316 386 463
370 482 609 751 907
198 226 254 282 310
194 222 250 278 306
300 386 484 592 711
229 295 368 450 540
433 564 712 877 1060
96
290 314 338 362 386
287 311 335 359 383
718 836 965 1110 1260
547 638 737 842 955
1079 1265 1466 1682 1912
338 366 394 422 450
334 362 391 419 447
842 983 1136 1298 1473
639 745 860 983 1115
1260 1478 1713 1965 2234
102 108 114 120 126
410 434 458 482 506
407 431 455 479 503
1419 1582 1760 1950 2170
1075 1202 1335 1476 1624
2158 2418 2694 2984 3288
478 506 534 562 591
475 503 531 559 587
1658 1854 2061 2249 2530
1254 1402 1558 1722 1894
2521 2825 3146 3484 3840
132 138 144
530 554 579
527 551 576
2490 2595 2820
1779 1928 2110
3608 3942 4292
619 647 675
615 643 671
2790 3025 3300
2075 2264 2461
4213 4604 5011
14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78
84 90
III
377
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
9/16"
1/2"
DIAM.
HEAD
SHELL
HEAD
SHELL
ELLIP F.&D. HEMIS
ELLIP F.&D. HEMIS
I.S.
O.S.
47 56 70 81 97
30 38 47 59 70
43 58 75 94 115
76 88 100 112 124
69 81 93 105 117
52 63 78 91 109
35 44 54 67 78
49 65 85 106 131
114 125 136 146 157
110 125 140 161 182
81 94 110 125 140
139 165 193 223 255
136 148 160 172 184
129 141 153 165 177
124 143 162 181 205
91 107 124 140 157
157 186 218 252 288
174 184 195 206 217
168 178 189 200 211
206 230 256 283 313
161 178 196 220 240
290 327 366 407 450
196 208 220 232 244
189 201 213 225 237
231 259 288 319 352
181 200 220 247 270
327 369 413 459 508
227 259 291 323 355
221 253 285 317 349
343 442 553 677 813
261 337 421 514 617
496 646 815 1005 1214
256 292 328 364 400
249 285 321 357 393
386 497 622 762 915
294 379 473 578 694
560 728 919 1133 1368
96
387 419 451 483 515
381 413 445 477 509
962 1124 1298 1484 1683
730 852 983 1124 1274
1443 1692 1960 2248 2557
436 472 508 544 580
429 465 501 537 573
821 1083 1264 958 1460 1106 1669 1264 1894 1433
1626 1906 2209 2533 2880
102 108 114 120 126
547 579 611 647 676
541 573 605 638 670
1894 2119 2355 2571 2890
1433 2884 1602 3232 1780 3599 1968 3986 2165 4393
617 653 689 725 761
610 646 682 718 754
2131 1612 2384 1802 2650 2002 2892 2214 3234 2435
3249 3640 4054 4489 4947
132 138 144
708 740 777
702 734 766
3340 3460 3760
2372 2588 2813
797 833 869
790 826 862
3660 2668 3897 2911 4240 3165
5427 5930 6454
12 14
I.S.
O.S.
67 88 99 110
61 72 82 93 104
120 131 142 152 163
78
16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
4820 5266 5732
378
WEIGHT OF SHELLS & HEADS WALL THICKNESS
5/8"
DIAM.
VESSEL
SHELL
1.5.
12
O.S.
11/16"
HEAD
SHELL
ELUP F.&D. HEMIS
I.S.
0.5.
HEAD ELUP F.&D. HEMIS
16
III
20
124 137
76 89 103 116 129
151 164 177 191 204
143 156 169 183 196
138 161 180 201 228
101 121 138 156 175
176 208 243 281 322
166 181 196 211 225
156 171 186 201 215
154 177 198 221 251
113 133 151 171 195
194 230 269 311 355
218 231 244 258 271
210 223 236 250 263
257 288 326 355 391
201 223 245 275 300
365 411 460 512 566
240 255 269 284 299
230 245 259 274 289
283 317 353 390 430
221 245 270 302 330
403 454 508 565 625
284 324 364 404 444
276 316 356 396 436
428 552 691 846 1017
327 421 526 643 772
623 811 1024 1261 1523
313 357 401 445 489
303 347 391 435 479
471 607 760 931 1118
360 458 579 707 849
688 895 1129 1390 1677
96
484 524 564 604 644
476 516 556 596 636
1203 1405 1622 1855 2104
912 1065 1229 1405 1592
1810 2121 2458 2818 3204
533 577 621 665 710
523 567 611 655 700
1323 1545 1784 2D41 2315
1003 1171 1352 1545 1751
1994 2337 2707 3104 3529
102 108 114 120 126
685 725 765 805 848
677 717 757 797 837
2368 1791 2648 2003 2944 2225 3213 2460 3578 2706
3614 4049 4509 4993 5502
754 798 842 886 930
744 788 832 876 920
2605 2913 3239 3535 3910
1970 2203 2448 2706 2977
3980 4459 4965 5498 6058
132 138 144
885 925 965
877 917 957
3980 2965 4325 3234 4720 3516
6036 6595 7178
974 1018 1062
964 1008 1052
4317 4703 5185
3261 3557 3868
6646 7261 7902
14 18
22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
84 97
58 70 87 101 121
40 50 61 74 86
55 73 95 119 146
93 108 122 137 152
83 98 112 127 142
64 79 95 113 133
44 55 67 83 97
61 81 105 132 162
379
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
13/16"
3/4"
DIAM.
HEAD
SHELL I.S.
O.S.
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
HEAD ELLIP F.&D. HEMIS
102 118 134 150 166
90 106 122 138 154
70 88 104 126 145
48 60 74 92 108
67 90 116 145 177
1 11 128 146 163 180
97 114 132 149 166
76 95 113 136 157
53 67 82 100 117
73 98 126 158 193
182 198 214 230 246
170 186 202 218 234
171 193 216 241 274
126 145 165 187 216
213 252 295 340 389
198 215 233 250 267
184 201 219 236 253
185 209 234 261 304
137 160 182 412 234
232 275 321 370 423
262 278 294 310 326
250 266 282 298 314
309 345 393 425 469
241 267 294 330 361
442 497 556 618 684
285 302 319 337 354
271 288 305 323 340
335 378 425 470 508
261 289 323 357 391
480 541 605 672 743
342 390 438 486 534
330 378 426 474 522
514 662 829 1015 1220
393 505 631 772 926
753. 979 1234 1520 1835
371 423 475 527 579
357 409 461 513 565
567 729 911 1107 1337
425 547 683 836 1003
818 1063 1340 1650 1991
96
582 630 678 726 775
570 618 666 714 763
1443 1685 1947 2226 2525
1095 1277 1475 1685 1911
2179 2554 2958 3391 3855
631 683 735 788 840
617 669 721 774 826
1564 1835 2120 2433 2757
1186 1384 1597 1825 2070
2365 2771 3209 3679 4181
102 108 114 120 126
823 871 919 967 1015
811 859 907 955 1003
2842 3178 3533 3856 4243
2150 2403 2671 2952 3248
4348 4870 5422 6004 6616
892 944 996 1048 1100
878 930 982 1034 1086
3103 3457 3854 4204 4614
2329 2603 2893 3198 3518
4716 5282 5881 6511 7174
132 138 144
1063 1111 1159
1051 1099 1147
4655 5082 5650
3558 3881 4219
7257 7928 8628
1152 1204 1256
1138 1190 1242
5059 5522 6067
3854 4205 4571
7869 8596 9356
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
380
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
12 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90 96
HEAD
SHELL I.S.
14
1 5/16"
7/8"
DIAM.
O.S.
HEAD
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
ELLIP F.&D. HEMIS
120 139 157 176 195
104 123 141 160 179
82 103 122 147 170
59 74 90 107 127
80 106 137 171 209
130 150 170 190 210
III
131 151 171 191
90 110 135 157 185
67 83 101 123 144
86 115 148 1-85 226
213 232 251 270 288
197 216 235 254 272
199 225 252 288 327
147 175 199 225 252
251 297 347 401 458
230 250 270 290 310
211 231 251 271 291
213 241 271 310 351
167 194 220 249 282
271 320 374 431 493
307 326 344 363 382
291 310 328 347 366
366 412 458 506 558
281 312 352 385 421
519 584 653 726 803
330 350 370 390 410
311 331 351 371 391
393 442 491 543 597
314 347 387 422 462
558 628 702 780 863
400 456 512 568 624
384 440 496 552 608
611 789 982 1200 1440
458 589 736 900 1080
883 1148 1447 1780 2149
430 491 551 611 671
411 471 531 591 651
654 836 1051 1285 1543
507 643 802 979 1174
949 1233 1554 1911 2306
680 736 792 849 905
664 720 776 833 889
1702 1986 2293 2620 2970
1278 1491 1720 1966 2229
2551 2989 3461 3968 4509
731 791 851 911 971
711 771 832 892 952
1823 2128 2456 2807 3182
1387 1616 1864 2129 2412
2738 3207 3714 4257 4837
5085 5695 6340 7019 7734
1031 1091 1151 1212 1272
1012 1072 1132 1192 1252
3580 4002 4447 4852 5341
2712 3036 3366 3720 4091
5454 6109 6800 7529 8294
4150 8482 4528 9266 4923 10084
1332 1392 1452
1312 1372 1432
5853 6389 6948
4480 9097 4886 9937 5310 10813
102 108 114 120 126
945 961 1017 1001 1073 1057 1129 1113 1185 1169
3341 2508 3735 2804 4150 3115 4528 3444 4985 3789
132 138 144
1241 1297 1353
5463 5963 6485
1225 1281 1337
381
WEIGHT OF SHELLS & HEADS WALL THICKNESS 1"
DIAM. VESSEL
12
HEAD
SHELL I.S.
O.S.
1-1/16" HEAD
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
ELLIP F.&D. HEMIS
139 160 182 203 224
117 138 160 181 202
98 118 144 168 200
76 93 113 139 162
93 124 159 198 242
148 171 193 216 239
124 147 169 192 215
104 125 153 178 212
83 102 122 150 175
100 132 170 212 259
246 267 289 310 331
223 245 266 287 308
228 257 288 330 374
187 214 242 273 313
290 343 400 462 528
262 284 307 330 352
238 260 283 306 328
242 277 31 1 350 397
202 231 261 294 338
310 366 427 493 563
353 374 396 417 438
330 351 372 393 415
421 471 523 579 637
347 383 421 460 502
598 673 752 835 923
375 398 420 443 466
351 374 396 419 442
448 500 562 614 677
373 412 452 495 539
638 801 890 984
459 523 587 651 715
436 500 564 628 692
698 897 1121 1371 1646
556 698 869 1059 1268
1015 1318 1661 2043 2465
489 557 625 693 761
465 533 601 669 737
741 953 1191 1457 1749
597 749 931 1134 1357
1082 1404 1769 2175 2624
96
779 844 908 972 1036
756 821 885 949 1013
1945 2270 2620 2994 3394
1496 1741 2008 2292 2596
2926 3427 3967 4547 5166
829 805 897 874 965 942 1033 1010 110 1 1078
2067 2412 2783 3181 3606
1590 1851 2134 2435 2758
3114 3647 4221 4838 5496
102 108 114 120 126
1100 1164 1228 1292 1356
1077 1141 1205 1269 1333
3819 4268 4743 5175 5697
2917 3258 3617 3996 4393
5825 6523 7261 8039 8856
1169 1237 1306 1374 1442
1146 1214 1282 1350 1418
4057 3099 4535 "3462 5038 3843 5498 4246 6053 4667
6197 6939 7724 8550 9419
132 138 144
1420 1484 1549
1397 1461 1526
6243 6815 7411
4809 9712 5243 10609 5697 11544
1510 1578 1646
1486 1554 1623
6633 7241 7874
14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
7~7
5108 10329 5571 11282 6053 12276
382
WEIGHT OF SHELLS & HEADS WALL THICKNESS
1-1/8"
DIAM. VESSEL
12
HEAD
SHELL I.S.
O.S.
1-3/16" SHELL
ELLIP F.&D. HEMIS
LS.
O.S.
HEAD ELLIP F.&D. HEMIS
158 182 206 230 254
131 155 179 203 227
110 133 163 189 225
90 110 132 162 189
106 141 181 226 276
167 192 218 243 268
137 162 188 213 238
116 143 172 203 237
97 120 143 171 200
113 150 193 240 293
278 302 326 350 374
251 275 299 323 347
256 298 333 371 421
217 248 281 315 362
330 390 454 524 598
294 319 345 370 395
264 289 315 340 365
279 318 352 391 444
230 266 301 337 382
351 414 482 555 634
398 422 446 470 494
371 395 419 443 467
474 530 601 651 717
400 442 484 530 576
678 762 851 946 1045
421 466 471 497 522
391 416 441 467 492
500 560 634 687 756
423 466 517 565 615
718 807 902 1001 1106
518 591 663 735 807
491 563 635 707 779
785 1009 1261 1543 1852
639 800 994 1209 1446
1149 1491 1877 2308 2783
548 624 700 776 852
518 594 670 746 822
828 1065 1331 1628 1954
674 852 1049 1276 1526
1216 1577 1986 2441 2943
96
879 951 1023 1095 1167
852 924 996 1068 1140
2189 2554 2947 3368 3818
1684 1960 2260 2579 2920
3303 3867 4476 5129 5827
929 1005 1081 1157 1233
899 975 1051 1127 1203
2310 2695 3108 3555 4030
1788 2082 2398 2736 3097
3492 4089 4732 5422 6159
102 108 114 120 126
1239 1312 1384 1456 1528
1212 1284 1356 1428 1500
4296 4802 5336 5822 6409
3282 3666 4070 4496 4942
6569 7356 8187 9062 9982
1309 1385 1461 1537 1613
1279 1355 1431 1507 1583
4535 5069 5632 6145 6765
3480 6942 7772 7773 4314 8651 4764 9576 5236 10547
132 138 144
1600 1672 1744
1573 1645 1717
7024 7667 8338
5410 10947 5899 11956 6408 13010
1690 1766 1842
1660 1736 1812
7414 8093 8801
5731 11566 6248 12632 6786 13744
14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 -S4 90
383
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
1-5/16"
1-1/4"
DIAM.
LS.
O.S.
SHELL
HEAD
SHELL
ELUP F.&D. HEMIS
LS.
O.S.
HEAD ELUP F.&D. HEMIS
177 204 230 257 284
144 171 197 224 251
122 154 181 217 250
105 129 154 181 210
120 160 204 254 310
187 215 243 271 299
150 178 206 234 262
129 161 193 228 267
112 138 165 193 225
127 169 216 269 327
311 337 364 391 417
278 304 331 358 384
292 331 371 412 467
242 284 322 360 402
371 438 510 587 670
327 355 383 411 439
290 318 346 374 402
307 347 390 439 497
258 303 343 384 428
392 462 538 619 707
444 471 497 524 551
411 438 464 491 518
526 589 667 724 796
446 490 551 601 654
759 853 952 1057 1168
467 495 523 552 580
430 486 515 543
559 625 700 768 844
474 521 585 638 694
800 899 1003 1113 1230
578 658 738 818 898
545 625 705 785 865
872 1121 1401 1714 2057
710 904 1104 1343 1606
1284 1665 2095 2575 3104
608 692 776 860 944
571 655 739 823 907
924 1187 1482 1812 2173
753 958 1169 1421 3374
1352 1752 2205 2709 3265
96
979 1059 1139 1219 1299
945 1025 1105 1185 1265
2432 1893 2837 2204 3275 2537 3742 2894 4242 3274
3683 4311 4988 5715 6491
1029 1113 1197 1281 1365
991 1075 1159 1243 1328
2567 2994 3455 3947 4473
1988 2314 2664 3039 3438
3873 4533 5245 6009 6824
102 108 114 120 126
1379 1459 1539 1619 1700
1346 1426 1506 1586 1666
4774 3678 5336 4106 5929 4558 6469 5032 7121 5530
7317 8192 9116 10090 11113
1449 1533 1617 1701 1786
1418 1496 1580 1664 1748
5032 5623 6248 6815 7501
3862 7692 4311 8611 4786 9582 5283 10606 5807 11681
132 138 144
1780 1860 1940
1746 1826 1906
7804 6051 8519 6596 9264 7165
12186 13308 14480
1870 1954 2038
1832 1916 2000
8220 8971 9755
6354 12808 6926 13986 7524 15217
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
45~
384
WEIGHT OF SHELLS & HEADS WALL THICKNESS
1-3/8"
DIAM.
VESSEL
SHELL I.S.
O.S.
1-7/16" HEAD
SHELL
ELUP F.&D. HEMIS
I.S.
O.S.
HEAD ELLIP F.&D. HEMIS
196 225 255 284 313
156 185 215 244 273
142 169 206 239 285
119 148 176 206 239
135 178 228 283 345
206 237 267 298 329
162 193 223 254 285
151 180 220 255 303
126 155 184 220 253
143 188 240 298 363
343 372 402 431 460
303 332 362 391 421
322 364 408 466 527
275 323 364 408 454
412 486 566 651 743
360 390 421 452 482
316 346 377 408 438
342 386 432 493 558
292 337 380 426 481
434 511 594 684 780
490 519 548 578 607
450 479 508 538 567
593 662 734 812 892
502 553 620 676 734
841 945 1054 1170 1293
513 544 575 605 636
469 500 531 561 592
627 699 775 857 941
532 585 648 707 768
882 991 1106 1228 1355
637 725 813 901 989
597 685 773 861 949
977 1253 1563 1910 2289
796 1012 1234 1500 1768
1420 1841 2315 2844 3427
667 759 851 943 1035
623 715 807 899 991
1030 1320 1646 2061 2407
840 1057 1301 1568 1861
1489 1929 2426 2979 3590
96
1078 1166 1254 1342 1430
1038 1126 1214 1302 1390
2703 3152 3635 4152 4704
2083 2424 2791 3184 3602
4065 4757 5503 6303 7159
1128 1220 1312 1404 1496
1083 1175 1267 1360 1452
2841 3312 3819 4360 4938
2177 2534 2917 3328 3766
4257 4981 5761 6599 7493
102 108 114 120 126
1518 1606 1694 1783 1871
1478 1566 1654 1743 1831
5291 5911 6567 7162 7882
4046 8068 4517 9032 5014 10050 5535 11122 6084 12249
1588 1680 1772 1865 1957
1544 1636 1728 1820 1912
5553 6203 6890 7513 8267
4230 8445 4722 9453 5241 10518 5786 11640 6360 12818
132 138 144
1959 1919 8636 6656 13430 2047 2007 9424 7256 14666 2135 2095 10246 7882 15955
2049 2141 2233
2004 9113 2097 9881 2189 10742
6959 14054 7586 15346 8240 16695
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
385 WEIGHT OF SHELLS & HEADS WALL THICKNESS 1-1/2"
DIAM. VESSEL
12
HEAD
SHELL I.S.
O.S.
1-9/16"
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
HEAD ELLIP F.&D. HEMIS
216 248 280 312 344
168 200 232 264 296
162 192 234 271 321
134 162 192 234 271
150 198 252 313 381
227 260 294 327 361
174 207 241 274 308
173 204 248 287 340
144 174 206 249 287
158 208 265 328 399
376 408 440 472 504
328 360 392 424 456
363 409 457 521 589
310 352 397 444 508
455 536 623 717 817
394 427 461 494 527
341 374 408 441 474
384 432 483 550 621
329 745 415 470 536
476 561 652 750 855
536 568 600 633 665
488 520 552 585 617
661 738 817 903 991
562 618 676 738 802
924 1038 1158 1285 1418
561 594 628 661 694
508 541 575 608 641
696 777 860 950 1042
592 652 712 777 844
966 1085 1210 1343 1482
697 793 889 985 1082
649 745 841 937 1034
1084 1388 1729 2111 2526
885 1103 1368 1636 1954
1558 2018 2537 3115 3753
728 828 928 1028 1129
675 775 875 975 1075
1140 1457 1815 2212 2647
931 1110 1436 1716 2049
1628 2107 2649 3251 3916
96
1178 1274 1370 1466 1562
1130 1226 1322 1418 1514
2980 3472 4003 4569 5173
2272 2644 3044 3472 3930
4449 5205 6021 6895 7829
1229 1329 1420 1529 1629
1175 1275 1376 1476 1576
3122 3635 4189 4781 5411
2382 2770 3171 3617 4093
4643 5431 6281 7192 8166
102 108 114 120 126
1658 1754 1851 1947 2043
1610 1706 1803 1899 1995
5815 6496 7213 7864 8652
4414 8823 4928 9875 5468 10987 6038 12158 6636 13389
1729 1829 1930 2030 2130
1676 1776 1876 1976 2076
6081 6792 7540 8219 9041
4598 5133 5696 6290 6913
9201 10298 11457 12678 13960
132 138 144
2139 2235 2331
2091 9590 2187 10339 2283 11239
7262 14678 7916 16027 8599 17436
2230 2330 2430
2176 10020 2276 10738 2376 11741
14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
7564 15304 8246 16710 8957 18188
386
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
12 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72
78 84 90 96
HEAD
SHELL I.S.
14
1-11/16"
1-5/8"
DIAM.
O.S.
HEAD
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
ELLIP F.&D. HEMIS
236 271 305 340 375
180 215 249 284 319
184 217 263 304 359
153 186 220 265 304
166 218 277 344 417
247 283 319 355 391
186 222 258 294 330
195 230 277 321 379
163 198 235 280 315
174 228 290 359 436
410 444 479 514 548
354 388 423 458 492
405 455 509 578 653
348 393 443 495 564
498 586 681 783 892
427 463 499 535 571
366 402 438 474 570
427 480 535 608 686
361 415 466 521 585
520 611 710 817 930
583 618 653 687 722
527 562 597 631 666
732 815 903 997 1094
623 685 748 817 886
1009 1132 1263 1401 1546
608 644 680 716 752
547 583 619 655 691
770 856 948 1045 1147
647 711 785 857 930
1051 1180 1316 1459 1610
757 861 965 1069 1174
701 805 909 1013 1117
1195 1527 1900 2314 2768
978 1216 1505 1797 2144
1698 2197 2761 3388 4080
788 896 1004 1112 1221
727 835 943 1051 1159
1253 1015 1598 1275 1987 1562 2418 1880 2891 2226
1768 2288 2873 3526 4245
1278 1382 1486 1590 1694
1221 1325 1430 1534 1638
3264 2492 3799 2897 4375 3298 4994 3762 5650 4257
4836 5657 6542 7490 8504
1329 1437 1545 1653 1761
1267 1376 1484 1592 1700
3408 2603 3965 3008 4565 3443 5207 3926 5892 4441
5031 5884 6803 7789 8842
6348 4782 9581 7088 5338 10723 7867 5924 11928 8575 6541 13198 9431 7190 14533
1869 1978 2086 2194 2302
1808 1916 2024 2133 2241
6618 7388 8198 8935 9825
4966 5567 6177 6819 7493
9961 11148 12401 13720 15107
2263 10450 7867 15931 2367 11138 8576 17394 2471 12243 9316 18921
2410 2518 2626
2349 10851 8198 16560 2457 11669 8936 18079 2565 12749 9705 19666
102 108 114 120 126
1798 1742 1903 1846 2007 1950 2111 2054 2215 2159
132 138 144
2319 2423 2527
387
WEIGHT OF SHELLS & HEADS WALL THICKNESS
1-3/4"
DIAM. VESSEL
SHELL I.S.
O.S.
1-13/16" HEAD
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
HEAD ELLIP F.&D. HEMIS
257 294 332 369 407
192 229 267 304 342
206 243 294 338 399
172 211 249 296 327
182 238 303 375 455
267 306 344 383 422
197 236 274 313 352
218 257 314 356 420
182 223 264 311 345
190 249 316 391 473
444 481 519 556 593
379 416 454 491 528
450 504 562 639 719
374 437 490 547 607
542 637 740 850 969
461 499 538 577 615
391 429 468 507 545
473 530 590 670 754
394 460 515 575 638
564 663 770 885 1007
631 668 706 743 780
566 603 641 678 715
807 898 993 1094 1200
671 737 823 897 973
1094 1228 1369 1518 1675
654 693 732 770 809
584 623 662 700 739
845 940 1040 1144 1254
704 772 862 939 1018
1138 1276 1423 1577 1740
818 930 1042 1154 1267
753 865 977 1089 1201
1311 1670 2074 2523 3015
1053 1332 1620 1963 2308
1839 2378' 2986 3664 4410
848 964 1080 1196 1313
778 894 1010 1126 1243
1370 1743 2163 2630 3141
1101 1392 1691 2047 2407
1910 2469 3100 3802 4576
1379 1491 1603 1715 1827
1313 1426 1538 1650 1762
3552 2715 4132 3119 4756 3588 5421 4091 6134 4626
5226 6111 7065 8089 9181
1429 1545 1661 1777 1893
1359 1475 1591 1707 1823
3700 4301 4948 5639 6379
2829 3299 3737 4237 4792
5422 6339 7328 8389 9521
102 108 114 120 126
1940 1874 6888 5150 10343 2052 1986 7688 5796 11574 2164 2099 8529 6430 12874 2276 2211 9295 7098 14243 2388 2323 10220 7797 15681
2010 2126 2242 2358 2474
1940 7162 2056 7991 2172 8865 2288 9659 2404 10618
5334 6003 6660 7351 8076
10725 12001 13348 14767 16257
132 138 144
2500 2435 11252 8530 17189 2612 2547 12201 9296 18766 2725 2659 13256 10094 20412
2590 2707 2823
2520 11650 8535 17820 2637 12673 96~8 19453 2753 13768 10455 21159
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90 96
388
WEIGHT OF SHELLS & HEADS WALL THICKNESS
1-7/8"
DIAM.
VESSEL
HEAD
SHELL I.S.
O.S.
1-15/16"
SHELL
ELLIP F.&D. HEMIS
208 249 291 332 374
243 285 343 394 462
201 247 293 342 382
206 270 342 423 512
414 482 540 602 668
587 689 800 929 1046
495 536 578 619 661
415 456 498 539 581
521 583 648 737 825
435 498 558 622 699
610 716 830 953 1085
883 981 1086 1194 1309
736 808 902 981 1063
1181 1325 1477 1637 1805
702 743 785 826 867
622 663 705 746 787
923 1025 1134 1246 1365
770 845 932 1014 1099
1225 1374 1531 1697 1871
804 924 1044 1164 1284
1429 1817 2253 2737 3268
1150 1981 1452 - 2561 1762 3214 2132 3941 2506 4743
909 1033 1157 1282 1406
829 953 1077 1202 1326
1489 1892 2344 2846 3397
1200 1501 1835 2203 2607
2054 2653 3329 4081 4910
96
1480 1600 1720 1840 1960
1405 1525 1645 1765 1885
3846 4470 5141 5858 6624
2944 3380 3886 4383 4958
5618 6568 7592 8690 9862
1530 1654 1778 1902 2027
1450 1574 1698 1822 1947
3995 4642 5357 6080 6873
3040 5816 3512 6798 4015 7857 4552 8992 5123 10204
102 108 114 120 126
2081 2201 2321 2441 2561
2005 7436 2126 8295 2246 9201 2366 10024 2486 11017
5518 6210 6890 7604 8355
11108 12429 13823 15292 16834
2151 2275 2399 2523 2647
2071 7714 2195 8603 2319 9540 2443 10358 2567 11420
132 138 144
2681 2802 2922
2606 12058 9140 18451 2726 13146 9960 20142 2846 14280 10816 21907
2772 2896 3020
2692 12460 9444 19084 2816 13623 10291 20832 2940 14756 11176 22657
16 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
231 271 326 375 441
191 235 278 327 363
478 518 558 598 638
403 443 483 523 563
497 556 619 701 789
679 719 759 799 839
604 644 684 724 764
879 999 1119 1239 1360
ELLIP F.&D. HEMIS
288 329 371 412 454
18
203 243 283 323 363
O.S.
198 259 329 407 493
12 14
278 318 358 398 438
I.S.
HEAD
--
5722 6417 7120 7858 8633
11492 12858 14299 15818 17413
389
WEIGHT OF SHELLS & HEADS WALL THICKNESS
VESSEL
2 1/4"
2"
• DIAM. SHELL I.S.
O.S.
HEAD
SHELL
ELLIP F.&D. HEMIS
I.S.
O.S.
HEAD ELLIP F.&D. HEMIS
299 342 384 427 470
214 257 299 342 385
256 300 361 414 484
210 259 307 358 400
215 281 356 439 531
342 391 439 487 535
216 282 330 379 427
307 358 362 425 495
248 296 349 406 467
251 326 411 506 612
513 555 598 641 683
428 470 513 556 598
546 610 678 767 862
456 514 576 642 730
633 742 861 988 1124
583 631 679 727 775
475 523 571 619 667
578 648 723 801 904
533 603 678 757 840
726 851 986 1130 1285
726 769 812 854 897
641 684 727 769 812
963 1068 1181 1298 1421
804 882 962 1047 1134
1269 823 1423 871 1586 919 1757 967 1937 1015
715 763 811 859 907
1014 1130 1277 1380 1515
927 1019 1115 1216 1321
1449 1623 1834 2001 2205
940 1068 1196 1325 1453
855 983 1239 1367
1550 1968 2436 2956 3526
1250 1550 1909 2274 2708
2126 2745· 3444 4221 5078
1063 1208 1352 1496 1640
955 1100 1244 1388 1532
1655 2115 2632 3204 3833
1438 1802 2181 2632 3085
2419 3125 3922 4808 5787
96
1581 1709 1837 1965 2094
1496 1624 1752 1880 2008
4145 4814 5573 6302 7122
3140 6013 3645 7028 4145 8122 4722 9295 5288 10546
1784 1929 2073 2217 2361
1676 1821 1965 2109 2253
4519 . 3618 6854 5260 4146 8012 6058 4760 9194 6913 5364 10528 7823 6058 11952
102 108 114 120 126
2222 2350 2478 2606 2734
2137 7992 2265 8911 2393 9880 2521 10692 2649 11824
11877 13287 14776 16345 17992
2505 2650 2794 2938 3082
2397 8790 6737 2542 9814 7513 2686 10893 8332 2830 11874 9193 2974 13059 10096
132 138 144
2863 2991 3119
2777 12862 9748 19718 2906 14100 10623 21523 3034 15232 11536 23408
3226 3371 3514
3118 14301 11041 22291 3263 15597 12029 24343 3407 16952 13059 26424
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90
IIII
5937 6624 7349 8112 8911
13466 15073 16767 18554 20328
390
WEIGHT OF PIPES AND FITTINGS NOM. NOM. PIPE WALL PIPE DESIGNATION 1 ft. THK. SIZE ~
ELBOW
,, 90° L.R.
90° S.R.
RETURN 45° L.R.
6
180° L.R.
"
180° S.R.
ft
.. TEE
0.4 0.5 0.4
Y2
STD XSTG SCH.160 XXSTG
.109 .147 .187 .294
0.9 1.1 1.3 1.7
0.2 0.3
0.1 0.2
%
STD XSTG SCH.160 XXSTG
.113 .154 .218 .308
1.1 1.5 1.9 2.4
0.2 0.3
0.1 0.2
0.4 0.7
1
STD XSTG SCH.160 XXSTG
.133 .179 .250 .358
1.7 2.2 2.8 3.7
0.4 0.5 0.6 0.8
0.3 0.3 0.3 0.4
0.8 1.0 1.2 1.5
.140 .191 .250 .382
2.3 3.0 3.8 5.2
0.6 0.9 1.0 1.4
0.4 0.7 0.9
0.4 0.5 0.5 0.8
1.3 1.8 2.0 2.7
0.8
l~
STD XSTG SCH.160 XXSTG
1.4 1.8
1.3 1.6 2.0 2.5
lY2
STD XSTG SCH.160 XXSTG
.145 .200 .281 .400
2.7 3.6 4.9 6.4
0.9 1.2 1.4 1.9
0.6 0.8 1.2 1.0
0.4 0.7 1.0 1.1
1.9 2.4 3.3 4.0
1.1 1.5 2.4 2.7
2.0 2.3 3.0 3.4
2
STD XSTG SCH.160 XXSTG
.154 .218 .343 .436
3.7 5.0 7.5 9.0
1.6 2.2 3.3 3.5
1.0 1.5 2.2 2.3
0.8 1.2 1.6 2.0
3.2 4.4 6.0 7.5
2.0 3.0 4.0 5.0
3.5 4.0 5.0 6.3
2Y2
STD XSTG SCH.160 XXSTG
.203 .276 .375 .552
5.8 7.7 10.0 13.7
3.3 4.0 5.1 7.0
2.1 2.8 3.4 5.0
1.8 2.1 3.0 3.8
6.5 8.0 12.0 14.0
4.3 5.6 6.0 9.7
6.0 7.0 8.0 10.5
3
STD XSTG SCH.160 XXSTG
.216 .300 .438 .600
7.6 10.3 14.3 18.6
5.0 6.5 8.5 11.0
3.0 4.3 6.0 7.3
2.6 3.5 4.4 5.8
10.2 13.0 18.0 22.0
6.0 8.5 12.0 14.6
7.0 8.5 10.0 13.5
0.3 0.4 0.5
0.4 0.5
0.5 0.6 0.6
0.5 0.8 1.0
0.8 0.9 1.0 1.3
391
WEIGHT OF PIPES AND FITTINGS ELBOW
NOM. PIPE NOM. PIPE DESIGNATION WALL 1 Ft. SIZE THK.
<.-
,, 90° L.R.
90° S.R.
RETURN 0
45 L.R.
6
1800 L.R.
1800 S.R.
",. f t
.. TEE
3'12
STD XSTG XXSTG
.226 .318 .636
9.1 12.5 22.9
6.8 8.4 16.0
4.5 6.0 1l.0
3.5 4.5 8.5
1.3.0 16.8 32.00
9.0 12.0 22.0
9.0 12.0 18.0
4
STD XSTG SCH.120 SCH. 160 XXSTG
.237 .337 .438 .531 .674
10.8 15.0 19.0 22.5 27.5
9.0 13.5 15.6 18.0 20.0
6.3 8.5 10.4 12.0 13.0
4.5 6.1 7.8 8.8 10.S
18.5 25.0 31.3 40.0 40.0
12.5 17.0 20.8 24.0 27.0
12.0 15.8 23.5 25.0 25.0
5
STD XSTG SCH.120 SCH.160 XXSTG
.258 .375 .500 .625 .750
14.6 20.S 27.0 33.0 3S.6
15.5 22.0 27.8 32.0 36.0
9.6 14.0 lS.6 22.0 24.0
7.5 10.S 13.9 16.0 19.0
30.0 44.0 55.6 65.0 72.0
19.0 2S.0 37.2 44.0 48.0
21.0 26.0 44.5· 55.0 40.0
6
STD XSTG SCH. 120 SCH.160 XX STG.
.280 .432 .562 .71S .864
19.0 28.6 36.4 45.3 53.2
24.5 35.0 45.2 57.065.0
lS.0 23.0 30.0 3S.0 44.0
12.0 17.5 22.6 30.0 32.0
50.0 70.0 90.3 120.0 130.0
35.0 46.0 60.0 76.0 87.0
34.0 40.0 64.0 62.0 68.0
8
SCH. 20 SCH.30 STD SCH.60 X. STG. SCH. 100 SCH.120 SCH.140 SCH. 160 XX STG.
.250 .277 .322 .406 .500 .593 .718 .812 .906 .875
22.4 24.7 2S.6 35.6 43.4 50.9 60.6 67.8 74.7 72.4
36.5 40.9 50.0 58.0 71.0 84.0 100.8 111.0 120.0 118.0
24.4 27.0 34.0 39.1 47.5 56.0 66.0 74.0 80.0 79
18.2 20.4 23.0 29.4 35.0 42.0 50.4 55.0 62.0 60.0
73.0 81.9 95.0 117.0 142.0 168.0 202.0 222.0 230.0 236.0
4S.8 54.0 68.0 78.0 100.0 112.0 133.0 149.0 160.0 158.0
54.0 57.0 55.0 76.0 75.0 97.0 115.0 133.0 152.0 148.0
10
SCH.20 SCH.30 STD. XSTG.
.250 .307 .365 .500
28.0 34.2 40.5 54.7
56.8 71.4 8S.0 107.0
38.2 46.8 58.0 70.0
28.4 35.7 43.0 53.0
114.0 143.0 177.0 215.0
76.4 73.0 94.0 81.0 115.0 85.0 140.0 105.0
(cont.)
392
WEIGHT OF PIPES AND FITTINGS RETURN
ELBOW
NOM. NOM. WALL PIPE DESIGNATION THK. SIZE
PIPE I ft.
~ (cont.)
180° L.R.
180° S.R.
TEE
A
~
67 79 92 107 130
267 318 370 428 530
177 212 246 286 348
161 180 215 241 260
.250 33.4 .330 43.8 .375 49.6 .406 53.6 .500 65.4 .562 73.2 .687 88.6 .843 108.0 1.000 125.5 1.125 140.0 1.312 161.0
82 108 125 132 160 182 219 268 311 347 450
55 72 80 88 104 121 146 177 207 231 300
41 54 62 66 84 91 109 134 155 174 225
164 216 230 264 320 364 439 535 622 694 910
109 145 155 176 218 242 292 354 414 462 600
120 136 120 147 160 226 245 304 353 404 480
.250 312 .375 .438 .500 .593 .750 .937 1.093 1.250 1.406
37.0 46.0 55.0 63.0 72.0 85.0 107.0 131.0 151.0 171.0 190.0
106 132 160 183 205 245 310
70 87 105 122 140 163 205
53 66 80 91 100 123 154
212 264 325 366 400 490 619
140 175 210 244 275 326 410
193 210 165 252 230 311 369
213
850
.250 .312 .375 .500 .656
42.0 52.0 63.0 83.0 108.0
10
12
SCH.20 SCH.30 STD. SCH.40 X STG SCH.60 SCH. 80 SCH.100 SCH. 120 SCH.140 SCH.160
14
SCH.I0 SCH.20 STD. SCH.40 XSTG SCH.60 SCH. 80 SCH. 100 SCH. 120 SCH.140 SCH.160
(cont.)
45° L.R.
88 106 123 143 174
.592 .718 .843 1.000 1.125
16
90° S.R.
133 159 185 214 260
SCH.80 SCH.100 SCH. 120 SCH.140 SCH.160
SCH.10 SCH.20 SCH. 30 STD SCHAOXSTG SCH.60
.. . " " 90° L.R.
64.4 77.0 89.2 104.2 116.0
425 572
382
286
1092
764
139 172 206 276 355
92 115 132 174 236
69 86 100 135 178
277 344 412 550 710
184 230 260 340 472
201 222 195 280 458
393
WEIGHT OF PIPES AND FITTINGS NOM. NOM. WALL PIPE DESIGNATION THK. SIZE (cont.)
~
45° L.R.
6
A
1618
1080
118 146 167 205 219 259 340 422
88 110 126 154 167 195 247 317
352 438 510 616 690 780 989 1268
226 292 330 410 430 518 680 844
281 307 249 399 332 525 612 710
217 320 420 506 690 861
144 210 275 338 457 573
109 160 206 253 345 431
434 640 830 1012 1380 1722
288 410 .. 550 676 914 1146
439 342 480 706 834 1021
262
174
131
524
348
477
394
197
787
414
520
260
1040
550
540
.250 .312 .375 .438 .500 .562 .750 .937 1.156 1.375 1.562 1. 781
47 59 71 82 93 105 138 171 208 244 275 309
176 219 260 308 340 390 494 634
.250 .375 .500 .593 .812 1.031 1.281 1.50C 1. 750 1.968
53 79 105 123 167 209 256 297 342 379
.250 .312 .375 .437 .500
58 72 87 103 115
20
TEE
405
809
SCH.10 SCH. 20 STD SCH.30XSTG SCH.40 SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH. 160
180° S.R.
600
225
18
... " 180° L.R.
900
300
SCH.10 SCH.20 STD SCH.30 XSTG SCH.40 SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH.160
(cont.)
90° S.R.
450
.843 1.031 1.218 1.438 1.593
22
RETURN
ELBOW
137 165 193 224 245
SCH.80 SCH.100 SCH.120 SCH.140 SCH.160
16
, PIPE 1 ft.
90° L.R ..
548
394
WEIGHT OF PIPES AND FITTINGS NOM. PIPE SIZE
NOM. WALL DESIGNAI1ON THK.
ELBOW
PIPE 1 FT
.562 .625 .688 .750
129 143 157 170
.250 .375 .500 .562 .687 .968 1.218 1.531 1.812 2.062 2.343
63 95 125 141 171 238 297 367 429 484 542
26
.250 .312 .375 .437 .500 .562 .625 .688 .750
67 84 103 119 136 153 169 186 202
30
.312 .375 .500
99 119 158
22
24
SCH.10 SCH. 20 STD XSTG SCH.30 SCH.40 SCH.60 SCH.80 SCH.100 SCH.120 SCH.140 SCH. 160
RETURN
, , ,.. 90 0 L.R.
90 0 S.R.
45° L.R.
1800 L.R.
6
314 460 600 702 846 1188 1470
208 298 392 470 564 783 977
180 0 S.R.
ft
416 590 780 940 1128 1566 1954
.. TEE
677 528 610 977 1257 1446 1673
157 238 300 351 423 594 735
627 890 1200 1404 1692 2377 2940
550
275
1100
770
729
365
1458
875
306 367 488
1223 1465 1950
612 734 975
464 618
930 1235
1058 1060 1200
395
WEIGHT NOM. PIPE SIZE
'12 SA
1 114 Ph
2 2'12 3 3'12 4 5 6
8 10 12 14 16
20
24
30
OF
FLANGES 300 Ibs.
1SO Ibs. SLIP ON
LONG. WELD WELD NECK NECK BLIND STUDS
SLIP ON
WELD NECK
LONG. WELD BLIND STUDS NECK
1.0
2.0
2.0
1.0
1.5
2.0
2.0
1.0
1.5
2.0
2.0
1.0
2.5
3.0
3.0
2.0
2.0
2.5
8.0
2.0
1.0
3.0
4.0
10.0
4.0
2.0
2.5
2.5
10.0
3.0
1.0
4.5
5.0
14.0
6.0
2.0
3.0
4.0
12.0
3.0
1.0
6.5
7.0
17.0
7.0
3.5
5.0
6.0
16.0
4.0
1.5
7.0
8.0
19.0
8.0
4.0
8.0
10.0
21.0
7.0
1.5
10.0
12.0
28.0
12.0
7.0
9.0
1l.5
24.0
9.0
1.5
13.0
16.0
36.0
16.0
7.5
11.0
12.0
31.0
13.0
3.5
16.0
20.0
45.0
21.0
7.5
12.0
16.0
47.0
17.0
4.0
21.0
25.0
54.0
27.0
7.5
13.0
20.0
57.0
20.0
6.0
26.0
34.0
86.0
35.0
8.0
18.0
24.0
77.0
26.0
6.0
35.0
45.0 108.0
50.0
11.5
28.0
42.0 103
45.0
6.5-
54.0
70.0
150
81.0
18.0
37.0
55.0 150
70.0
15.0
77.0
99.0
218
127
38.0
60.0
85.0 215
110
15.0 110
142
289
184
49.0
77.0 114
221
131
22.0 164
186
342
236
62.0
93.0 142
254
170
31.0 220
246
426
307
83.0
18 120
155
278
209
41.0 280
305
493
390
101
155
170
324
272
52.0 325
378
575
492
105
22 159
224
333
69.0 433
429
594
157
210
260
439
411
71.0 490
545
823
754
174
26 248
270
470
498
93.6 552
615
870
950
239
319
375
600
681
112.0 779
858
1130
1403
307
396 WEIGHT NOM. PIPE SIZE
%
% 1 IlJt
1% 2
2Y2 3 3% 4 5
6 8 10 I
, 12 14 16 18 20 22 24 26 30
FLANGES
OF
400 Ibs. SLIP ON
600 Ibs.
LONG. WELD WELD NECK NECK BLIND STUDS
SLIP ON
WELD NECK
LONG. WELD BLIND STUDS NECK
2.0
3.0
2.0
1.0
2.0
3.0
2.0
1.0
3.0
3.5
3.0
2.0
3.0
3.5
3.0
2.0
3.5
4.0
11.0
4.0
2.0
3.5
4.0
11.0
4.0
2.0
4.5
5.5
14.0
6.0
2.0
4.5
5.5
14.0
6.0
2.0
6.5
8.0
17.0
8.0
3.5
6.5
8.0
17.0
8.0
3.5
8.0
10.0
21.0
10.0
4.5
8.0
10.0
21.0
10.0
4.5
12.0
14.0
29.0
15.0
7.5
12.0
14.0
29.0
15.0
8.0
15.0
18.0
38.0
20.0
7.7
15.0
18.0
38.0
20.0
8.0
21.0
26.0
48.0
29.0
11.6
21.0
26.0
48.0
29.0
11.6
24.0
30.0
67.0
33.0
12.0
33.0
37.0
80.0
41.0
12.5
31.0
39.0
90.0
44.0
12.5
63.0
68.0 128
68.0
19.5
39.0
49.0 115.0
61.0
19.0
80.0
73.0 158
86.0
30.0
63.0
78.0 140
100
30.0
97.0 112.0 215
139
40.0
91.0 110.0 230
155
52.0
177
189
324
231
72.0 91.0
129
160
301
226
69.0
215
226
500
295
191
233
336
310
88.0
259
347
417
378
118
253
294
416
398
114
366
481
564
527
152
310
360
481
502
139
476
555
654
665
193
378
445
563
621
180
612
690
840
855
242
464
465
685
205
643
710
962
267
539
640
799
936
274
876
977
1100
1175
.365
616
680
970
1111
307
898
960
1250
1490
398
859
940
1230
1596
453
1158
1230 1520
1972
574
397
WEIGHT
Y2
FLANGES
900 lbs.
NOM. prp~
SIZE
OF
SLIP ON
1500 lbs.
LONG. WELD WELD NECK NECK BLIND STUDS
SLIP ON
LONG. WELD WELD NECK NECK BLIND STUDS
6.0
7.0
4.0
3.2
6.0
7.0
4.0
3.2
6.0
7.0
6.0
3.3
6.0
7.0
6.0
3.3
7.5
8.5
15.0
9.0
7.5
8.5
15.0
9.0
6.0
10.0
10.0
18.0
10.0
10.0
10.0
18.0
10.0
6.0
14.0
14.0
23.0
14.0
14.0
14.0
23.0
14.0
9.0
25.0
24.0
44.0
25.0
25.0
24.0
44.0
25.0
12.5
36.0
36.0
65.0
35.0
19.0
36.0
36.0
72.0
35.0
19.0
3
31.0
29.0
72.0
32.0
12.5
48.0
48.0
84.0
48.0
25.0
4
53.0
51.0
98.0
54.0
25.0
73.0
69.0 118
73.0
3·1.0
83.0
86.0 143
87.0
33.0
132.0 132.0 195
142
60.0 76.0
3,4
1
PA lY2 2 2Y2 3Y2
5
6 8 10 12 14 16 18 20
108.0 110.0 199
113
40.0
164
164
235
159
172
187
310
197
69.0
258
273
366
302
121
245
268
385
290
95.0 436
454
610
507
184
326
372
667
413
124
690
1028
775
306
380
562
558
494
159
940
1030
975
425
459
685
670
619
199
1250
1335
1300
570
647
924
949
880
299
09 r/}E-< E-«
1625
1750
1750
770
792
1164
1040
1107
361
::r: u
C!)~
2050
2130
2225
1010
3325
3180
3625
1560
667
ZZ
-p.. ~p..
22 24 30
~<
2099
687
26 1450 1650 1650 2200
765
1525
1575
2200
3025
1074
2075
2150
3025
1480 2107
1990 2290
1775
2200
398 WEIGHT NOM. PIPE SIZE
'12 %
1 11,4 1'12 2 2'12 3
2500 Ibs. SLIP ON
LONG. WELD WELD NECK NECK BLIND STUDS
7.0
8.0
7.0
3.4
9.0
9.0
10.0
3.6
12.0
13.0
20.0
12.0
6.0
18.0
20.0
30.0
18.0
9.0
25.0
28.0
38.0
25.0
12.0
38.0
42.0
55.0
39.0
21.0
55.0
52.0
85.0
56.0
27.0
83.0
94.0 125.0
86.0
37.0
3'12 4 5
6 8
10 12 14 16 18 20 22 24 26 30
FLANGES
OF
127
146
185
133
.61
210
244
300
223
98
323
378
450
345
145
485
576
600
533
232
925
1068
1150
1025
445
1300
1608
1560
1464
622
SLIP ON
LONG. WELD WELD NECK NECK BLIND STUDS
399
Manufacturers' Standard Gauge for
SHEET STEEL This gage system replaces U.S. Standard Gage for Steel Sheets. It is based on weight 41. 82 pounds per square foot per inch of thickness. In ordering steel sheets, it is advisable to specify the inch equivalent of gage. Mfgrs' Standard Gage Number
3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20
Inch Equivalent
Lbs. Per Square Inch
Lbs. Per Square Foot
Mfgrs' Standard Gage Number
Inch Equivalent
Lbs. Per Square Inch
Lbs. Per Square Foot
.2391 .2242 .2092 .1943 .1793 .1644 .1495 .1345 .1196 .1046 .0897 .0747 .0673 .0598 .0538 .0478 .0418 .0359
.069444 .065104 .060764 .056424 .052083 .047743 .043403 .039062 .034722 .030382 .026042 .021701 .019531 .017631 .015625 .013889 .012153 .010417
10.0000 9.3750 8.7500 8.1250 7.5000 6.8750 6.2500 5.6250 5.0000 4.3750 3.7500 3.1250 2.8125 2.5000 2.2500 2.0000 1.7500 1.5000
21 22 23 24 25 26 27 28 29 30 31 32 33 34 35 36 37 38
.0329 .0299 .0269 .0239 .0209 .0179 .0164 .0149 .0135 .0120 .0105 .0097 .0090 .0082 .0075 .0067 .0064 .0060
.0095486 .0086806 .0078125 .0069444 .0060764 .0052083 .0047743 .0043403 .0039062 .0034722 .0030382 .0028212 .0026042 .0023872 .0021701 .0019531 .0018446 .0017361
1.3750 1.2500 1.1250 1.0000 .87500 .75000 .68750 .62500 .56250 .50000 .43750 .40625 .37500 .34375 .31250 .28125 .26562 .25000
GALVANIZED SHEET Galv. Sheet Gage Number
Ounces Per Square Foot
Pounds Per Square Foot
Pound Per Square Inch
Thickness Equivalent for Galv. Sheet Gage. No.
8 9 10 11 12 13 14 15 16 17 18 19 20
112.5 102.5 92.5 82.5 72.5 62.5 52.5 47.5 42.5 38.5 34.5 30.5 26.5
7.03125 6.40625 5.78125 5.15625 4.53125 3.90625 3.28125 2.96875 2.65625 2.40625 2.15625 1.90625 1.65625
.048828 .044488 .040148 .035807 .031467 .027127 .022786 .020616 .018446 .016710 .014974 .013238 .011502
.1681 .1532 .1382 .1233 .1084 .0934 .0785 .0710 .0635 .0575 .0516 .0456 .0396
Galv. Sheet Gage Number
Ounces Per Square Foot
Pounds Per Square Foot
Pound Per Square linch
Thickness Equivalent for Galv. Sheet Gage No.
21 22 23 24 25 26 27 28 29 30 31 32
24.5 22.5 20.5 18.5 16.5 14.5 13.5 12.5 11.5 10.5 9.5 9.0
1.53125 1.40625 1.28125 1.15625 1.03125 .90625 .84375 .78125 .71875 .65625 .59375 .56250
.0106340 .0097656 .0088976 .0080295 .0071615 .0062934 .0058594 .0054253 .0049913 .0045573 .0041233 .0039062
.0366 .0336 .0306 .0276 .0247 .0217 .0202 .0187 .0172 .0157 .0142 .0134
400
WEIGHT OF PLATES Pounds Per Linear Foot Thickness, Inches Width In.
~
U
~6
.16 .32 .48 .64
.21 .43 .64 .85
.80 .96 1.12 1.28
~
~
1~6
%;
Y2
?16
.27 .32 .53 .64 .80 .96 1.06 1.28
.37 .74 1.12 1.49
.43 .85 1.28 1.70
.48 .53 .58 .96 1.06 Ll7 1.43 1.59 1.75 1.91 2.13 2.34
.64 1.28 1.91 2.55
.69 .74 .80 .85 1.38 1.49 1.59 1.70 2.07 2.23 2.39 2.55 2.76 2.98 3.19 3.40
1.06 1.28 1.49 1.70
1.33 1.59 1.86 2.13
1.59 1.91 2.23 2.55
1.86 2.13 2.23 2.55 2.60 2.98 2.98 3.40
2.39 2.87 3.35 3.83
2.66 3.19 3.72 4.25
3.19 3.83 4.46 5.10
3.45 4.14 4.83 5.53
1.43 1.59 1.75 1.91
1.91 2.13 2.34 2.55
2.39 2.66 2.92 3.19
2.87 3.35 3.83 3.19 3.72 4.25 3.51 4.09 4.68 3.83 4.46 5.10
4.30 4.78 5.26 5.74
4.78 5.26 5.74 6.22 6.69 7.17 7.65 5.31 5.84 6.38 6.91 7.44 7.97 8.50 5.84 6.43 7.01 7.60 8.18 8.77 9.35 6.38 7.01 7.65 8.29 8.93 9.56 10.2
3~ 2.07 3Y2 2.23 3% 2.39 2.55 4
2.76 2.98 3.19 3.40
3;45 3.72 3.98 4.25
4.14 4.83 5.53 6.22 6.91 7.60 8.29 4.46 5.21 5.95 6.69 7.44 8.18 8.93 4.78 5.58 6.38 7.17 7.97 8.77 9.56 5.10 5.95 6.80 7.65 8.50 9.35 10.2
8.98 9.67 10.4 11.1
9.67 10.4 11.2 11.9
10.4 11.2 12.0 12.8
11.1 11.9 12.8 13.6
4~ 2.71 4V2 2.87 4% 3.03 3.19 5
3.61 3.83 4.04 4.25
4.52 4.78 5.05 5.31
5.42 5.74 6.06 6.38
6.32 7.23 8.13 9.03 9.93 6.69 7.65 8.61 9.56 10.5 7.07 8.08 9.08 10.1 11.1 7.44 8.50 9.56 10.6 11.7
10.8 11.5 12.1 12.8
11.7 12.4 13.1 13.8
12.6 13.4 14.1 14.9
13.6 14.3 15.1 15.9
14.5 15.3 16.2 17.0
5~ 3.35 5V2 3.51 5% 3.67 3.83 6
4.46 4.68 4.89 5.10
5.58 5.84 6.11 6.38
6.69 7.01 7.33 7.65
7.81 8.93 10.0 8.18 9.35 10.5 8.55 9.78 11.0 8.93 10.2 11.5
15.6 16.7 17.9 16.4 17.5 18.7 17.1 18.3 19.6 17.9 19.1 20.4
61,4 6V2 6% 7
3.98 4.14 4.30 4.46
5.31 5.53 5.74 5.95
6.64 6.91 7.17 7.44
7.97 9.30 10.6 8.29 9.67 ILl 8.61 10.0 11.5 8.93 10.4 11.9
71,4 7Y2 7% 8
4.62 4.78 4.94 5.10
6.16 6.38 6.59 6.80
7.70 7.97 8.23 8.50
9.24 9.56 9.98 10.2
10.8 11.2 ll.5 11.9
12.3 12.8 13.2 13.6
8 1,4 8V2 8% 9
5.26 5.42 5.58 5.74
7.01 7.23 7.44 7.65
8.77 9.03 9.30 9.56
7.86 9.83 8.08 10.1 8.29 10.4 8.50 10.6
1,4
V2 % 1 1~
1V2 1% 2 2~
2V2 2% 3
9 1,4 5.90 9Y2 6.06 9% 6.22 10 6.38
%
1!{6
2.92 3.51 4.09 4.68
1~
Va
1
3.72 3.98 4.25 4.46 4.78 5.10 5.21 5.58 5.95 5.95 6.38 6.80
11.2 11.7 12.2 12.8
12.3 12.9 13.4 14.0
13.4 14.0 l4.7 15.3
14.5 15.2 15.9 16.6
12.0 12.4 12.9 13.4
13.3 13.8 14.3 14.9
14.6 15.2 15.8 16.4
15.9 16.6 17.2 17.9
17.3 18.6 19.9 21.3 18.0 19.3 20.7 22.1 18.7 20.1 21.5 23.0 19.3 20.8 22.3 23.8
13.9 14.3 14.8 15.3
15.4 15.9 16.5 17.0
17.0 17.5 18.1 18.7
18.5 19.1 19.8 20.4
20.0 20.7 21.4 22.1
21.6 23.1 24.7 22.3 23.9 25.5 23.1 24.7 26.4 23.8 25.5 27.2
10.5 10.8 11.2 ll.5
12.3 14.0 15.8 17.5 19.3 12.6 14.5 16.3 18.1 19.9 13.0 14.9 16.7 18.6 20.5 13.4 15.3 17.2 19.1 21.0
21.0 21.7 22.3 23.0
22.8 23.5 24.2 24.9
24.5 25.3 26.0 26.8
11.8 12.1 12.4 12.8
13.8 14.1 14.5 14.9
15.7 17.7 19.7 16.2 18.2 20.2 16.6 18.7 20.7 17.0 19.1 21.3
21.6 22.2 22.8 23.4
23.6 5.6 24.2 26.2 24.9 26.9 25.5 27.6
26.3 27.1 27.9 28.7
28.1 28.9 29.8 30.6
27.5 29.5 31.5 28.3 30.3 32.3 29.0 31.1 33.2 29.8 31.9 34.0
401
WEIGHT OF PLATES Pounds Per Linear Foot Width In.
Thickness, Inches
;,s
7.(
~6
I%;
1
26.1 28.3 30.5 26.8 29.0 31.2 27.4- 29.7 32.0 28.1. 30.4 32.7
32.7 33.5 34.3 35.1
34.9 35.7 36.6 37.4
28.7 29.3 30.0 30.6
33.5 34.2 35.0 35.7
35.9 36.7 37.5 38.3
38.3 39.1 40.0 40.8
23.9 26.6 29.2 31.9 34.5 24.9 27.6 3Q.4 33.2 35.9 25.8 28.7 32.6 34.4 37.3 26.8 29.8 32.7 35.7 38.7
37.2 3S.7 40.2 41.7
39.8 41.4 43.0 44.6
42.5 44.2 45.9 47.6
43.1 44.6 46.1 47.6
46.2 47.8 49.4 51.0
49.3 51.0 52.7 54.4
VB
?16
Y2
%;
%
1!{6
13.1 13.4 13.7 14.0
15.3 15.6 16.0 16.4
17.4 17.9 18.3 18.7
19.6 20.1 20.6 21.0
21.8 22.3 22.8 23.4
24.0 24.5 25.1 25.7
12.0 12.2 12.5 12.8
14.3 16.7 19.1 14.7 17.1 19.6 15.0 17.5 20.0 15.3 17.9 20.4
21.5 22.0 22.5 23.0
23.9 24.4 25.0 25.5
26.3 26.9 27.5 28.1
31.1 31.8 32.5 33.2
15.9 18.6 21.3 16.6 19.3 22.1 17.2 20.1 23.0 17.9 20.8 23.8
1014 6.53 8.71 10.9 10Y2 6.69 8.93 11.2 1034 6.85 9.14 11.4 11 7.01 9.35 11.7
%
1;{6
Va
1114 11Y2 11% 12
7.17 9.56 7.33 9.78 7.49 9.99 7.65 10.2
12% 13 13Y2 14
7.97 8.29 8.61 8.93
10.6 11.1 11.5 11.9
13.3 13.8 14.3 14.9
14Y2 15 15Y2 16
9.24 9.56 9.88 10.2
12.3 12.8 13.2 13.6
15.4 18.5 15.9 19.1 16.5 19.8 17.0 20.4
21.6 22.3 23.1 23.8
24.7 27.7 30.8 33.9 37.0 40.1 25.5 28.7 31.9 35.1 38.3 41.4 26.4 29.6 32.9 36.2 39.5 42.8 27.2 30.6 34.0 37.4 40.8 44.2
16Y2 17 17% 18
10.5 10.8 11.2 11.5
14.0 14.5 14.9 15.3
17.5 18.1 18.6 19.1
21.0 21.7 22.3 23.0
24.5 25.3 26.0 26.8
2S.1 2S.9 29.8 30.6
42.1 43.4 44.6 45.9
45.6 47.0 48.3 49.7
49.1 50.6 52.1 53.6
52.6 54.2 55.8 57.4
56.1 57.8 59.5 61.2
18Y2 19 19Y2 20
11.8 12.1 12.4 12.8
15.7 16.2 16.6 17.0
19.7 20.2 20.7 21.3
23.6 24.2 24.9 25.5
27.5 28.3 29.0 29.8
31.5 35.4 39.3 43.2 47.2 32.3 36.3 40.4 44.4 48.5 33.2 37.3 41.4 45.6 49.7 34.0 38.3 42.5 46.8 51.0
51.1 52.5 53.9 55.3
55.0 56.5 58.0 59.5
59.0 60.6 62.2 63.8
62.9 64.6 66.3 68.0
20Y2 21 21Y2 22
13.1 13.4 13.7 14.0
17.4 17.9 18.3 18.7
21.8 22.3 22.8 23.4
26.1 26.8 27.4 28.1
30.5 31.2 32.0 32.7
34.9 35.7 36.6 37.4
52.3 53.6 54.8 56.1
56.6 58.0 59.4 60.8
61.0 62.5 64.0 65.5
65.3 69.7 66.9 71.4 68.5 73.1 70.1 74.8
22% 23 23% 24
14.3 14.7 15.0 15.3
19.1 19.6 20.0 20.4
23.9 24.4 25.0 25.5
28.7 29.3 30.0 30.6
33.5 34.2 35.0 35.7
38.3 43.0 47.8 52.6 57.4 39.1 44.0 48.9 53.8 58.7 40.0 44.9 49.9 54.9 59.9 40.8 45.9 51.0 56.1 61.2
62.2 63.5 64.9 66.3
66.9 68.4 69.9 71.4
71.7 76.5 73.3 78.2 74.9 79.9 76.5 81.6
25 26 27 28
15.9 21.3 16.6 22.1 17.2 23.0 17.9 23.8
26.6 27.6 28.7 29.8
31.9 33.2 34.4 35.7
37.2 38.7 40.2 41.7
42.5 44.2 45.9 47.6
47.8 49.7 51.6 53.6
53.1 55.3 57.4 59.5
58.4 60.8 63.1 65.5
63.8 69.1 74.4 66.3 71.8 77.4 68.9 74.6 SO.3 71.4 77.4 83.3
79.7 85.0 82.9 88.4 86.1 91.8 89.3 95.2
29 30 31 32
18.5 19.1 19.8 20.4
24.7 25.5 26.4 27.2
30.8 31.9 32.9 34.0
37.0 38.3 39.5 40.8
43.1 44.6 46.1 47.6
49.3 51.0 52.7 54.4
55.5 57.4 59.3 61.2
61.6 63.8 65.9 68.0
67.S 70.1 72.5 74.8
74.0 76.5 79.1 81.6
31.6 32.5 33.5 34.4
39.2 40.2 41.1 42.1
35.1 36.1 37.2 38.3
43.6 44.6 45.7 46.8
38.6 39.7 40.9 42.1
47.9 49.1 50.3 51.4
80.1 82.9 85.6 88.4
86.3 92.4 9S.6 89.3 95.6 102 92.2 98.8 105 95.2 102 109
402
WEIGHT OF PLATES Pounds Per Linear Foot Thickness, Inches Width In.
~6
%
lYt6
~
63.1 65.0 66.9 68.9
70.1 72.3 74.4 76.5
77.1 79.5 81.8 84.2
84.2 86.7 89.3 91.8
31.5 32.3 33.2 34.0
39.3 47.2 55.0 62.9 70.8 78.6 86.5 40.4 48.5 56.5 64.6 72.7 80.8 88.8 41.4 49.7 58.0 66.3 74.6 82.9 91.2 42.5 51.0 59.5 68.0 76.5 85.0 93.5
94.4 96.9 99.5 102
102 105 108 111
26.1 26.8 27.4 28.1
34.9 35.7 36.6 37.4
43.6 44.6 45.7' 46.8
52.3 53.6 54.8 56.1
61.0 62.5 64.0 65.5
69.7 71.4 73.1 74.8
78.4 80.3 82.2 84.2
87.1 89.3 91.4 93.5
105 107
45 46 47 48
28.7 29.3 30.0 30.6
38.3 39.1 40.0 40.8
47.8 48.9 49.9 51.0
57.4 58.7 59.9 61.2
66.9 68.4 69.9 71.4
76.5 78.2 79.9 81.6
86.1 88.0 89.9 91.8
95.6 97.8 99.9 102
49 50 51 52
31.2 21.9 32.5 33.2
41.7 42.5 43.4 44.2
52.1 53.1 54.2 55.3
62.5 63.8 65.0 66.3
72.9 83.3 93.7 104 74.4 85.0 95.6 106 75.9 86.7 97.5 108 77.4 88.4 99.5 111
53 54 55 56
33.8 34.4 35.1 35.7
45.1 45.9 46.8 47.6
56.3 57.4 58.4 59.5
67.6 78.8 68.9 80.3 70.1 81.8 71.4 83.3
57 58 59 60
36.3 37.0 37.6 38.3
48.5 49.3 50.2 51.0
60.6 61.6 62.7 63.8
61 62 63 64
38.9 39.5 40.2 20.8
51.9 52.7 53.6 54.4
65 66 67 68
41.4 42.1 42.7 43.4
55.3 56.1 57.0 57.8
69 70 71 72
44.0 44.6 45.3 45.9
~6
VB
~
U
33 34 35 36
21.0 21.7 22.3 23.0
28.1 28.9 29.8 30.6
35.1 42.1 49.1 36.1 43.4 50.6 37.2 44.6 52.1 38.3 45.9 53.6
37 38 39 40
23.6 24.2 24.9 25.5
41 42 43 44
?16
Y2 56.1 57.8 59.5 61.2
IlH'6
l~
1
105 108 112 115
112 116 119 122
110 113 116 119
118 121 124 128
126 129 133 136
122 125 128 131
131 134 137 140
139 143 146 150
VB
91.2 98.2 93.9 101 96.1 104 99.5 107
95.8 98.2 101 103
112
113 116 119 122
105 108 110 112
115 117 120 122
124 127 130 133
134 137 140 143
143 147 150 153
153 156 160 163
115 117 119 122
125 128 130 133
135 138 141 144
146 149 152 155
156 159 163 166
167 170 173 177
llO
90.1 91.8 93.5 95.2
101 103 105 107
113 115 117 119
124 126 129 131
135 138 140 143
146 149 152 155
158 161 164 167
169 172 175 179
180 184 187 190
72.7 74.0 75.2 76.5
84.8 96.9 86.3 98.6 87.8 100 89.3 102
109 111 113 115
121 123 125 128
133 136 138 140
145 148 151 153
158 160 163 166
170 173 176 179
182 185 188 191
194 197 201 204
64.8 65.9 66.9 68.0
77.8 79.1 80.3 81.6
90.7 1()t. 92.2 105 93.7 107 95.2 109
117 119 121 122
130 132 134 136
143 145 147 150
156 158 161 163
169 171 174 177
182 185 187 190
194 198 201 204
207 211 214 218
69.1 70.1 71.2 72.3
82.9 84.2 85.4 86.7
96.7 98.2 99.7 101
111 112 114 116
124 126 128 130
138 140 142 145
152 154 157 159
166 168 171 173
180 182 185 188
193 196 199 202
207 210 214 217
221 224 228 231
58.7 73.3 59.5 74.4 60.4 75.4 61.2 76.5
88.0 89.3 90.5 91.8
103 104 106 107
117 119 121 122
132 134 136 138
147 149 151 153
161 164 166 168
176 179 181 184
191 193 196 199
205 208 211 214
220 223 226 230
235 238 241 245
403
WEIGHTS OF PLATES Pounds Per Linear Foot Thickness, Inches Width In. I
~
~
~6
%
?{6
Y2
%
%
l!{S
~
IHs
VB
1~6
1
46.5 47.2 47.8 48.5
62.1 62.9 63.8 64.6
77.6 78.6 79.7 80.8
93.1 94.4 95.6 96.9
109 110 112 113
124 126 128 129
140 142 143 145
155 157 159 162
171 173 175 178
186 189 191 194
202 204 207 210
217 220 223 226
233 236 239 242
248 252 255 258
49.1 78 49.7 79 50.4 80 51.0
65.5 66.3 67.2 68.0
81.8 82.9 83.9 85.0
98.2 99.5 101 102
115 116 118 119
131 133 134 136
147 149 151 153
164 166 168 170
180 182 185 187
196 199 202 204
213 216 218 221
229 232 235 238
245 249 252 255
262 265 269 272
81 82 83 84
51.6 52.3 52.9 53.6
68.9 69.7 70.6 71.4
86.1 87.1 88.2 89.3
103 105 106 107
121 122 124 125
138 139 141 143
155 157 159 161
172 174 176 179
189 192 194 196
207 209 212 214
224 227 229 232
241 244 247 250
258 261 265 268
275 279 282 286
85 86 87 88
54.2 54.8 55.5 56.1
72.3 73.1 74.0 74.8
90.3 91.4 92.4 93.5
lOS 110 111 112
126 128 129 131
145 163 146 165 148 166 150 168
181 183 185 187
199 201 203 206
217 219 222 224
235 238 240 243
253 256 259 262
271 274 277 281
289 292 296 299
89 56.7 90 57.4 91 92
75.7 76.5 77.4 78.2
94.6 95.6 96.7 97.8
114 115 116 117
132 134 135 137
151 153 155 156
170 172 174 176
189 191 193 196
20S 210 213 215
227 230 232 235
246 249 251 254
265 268 271 274
284 287 290 293
303 306 309 313
93 94 95 96
79.1 79.9 80.8 81.6
98.8 99.9 101 102
119 120 121 122
138 140 141 143
158 160 162 163
178 180 182 184
198 200 202 204
217 220 222 224
237 240 242 245
257 260 262 265
277 280 283 286
296 300 303 306
316 320 323 326
98 100 102 104
83,3 85.0 86.7 88.4
104 106 lOS 111
125 128 130 133
146 149 152 155
167 170 173 177
187 191 195 199
20S 213 217 221
229 234 238 243
250 255 260 265
271 276 282 287
292 298 304 309
312 319 325 332
333 340 347 354
106 108 110 112
90.1 91.8 93.5 95.2
113 115 117 119
135 138 140 143
158 161 164 167
180 184 187 190
203 207 210 214
225 230 234 238
248 253 257 262
270 275 281 286
293 298 304 309
315 321 327 333
338 344 351 357
360 367 374 381
114 116 118 120
96.9 98.6 100 102
121 123 125 128
145 148 151 153
170 173 176 179
194 197 201 204
218 222 226 230
242 247 251 255
267 271 276 281
291 296 301 306
315 321 326 332
339 345 351 357
363 370 376 383
388 394 401 40S
122 124 126 128
104 105 107 109
130 132 134 136
156 158 161 163
182 185 187 190
207 211 214 218
233 237 241 245
259 264 268 272
285 290 295 299
311 316 321 326
337 343 348 354
363 369 375 381
389 415 395 422 402 428 40S 435
73 74 75 76 77
I
404
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
3/16
~
5116
y.
1/16
1.00 1.25 1.50 1.75
.042 .065 .094 .128
.056 .087 .125 .170
.070 .109 .156 .213
.083 .130 .188 .256
2.00 2.25 2.50 2.75
.167 .211 .261 .315
.223 .282 .348 .421
.278 .352 .435 .526
.334 .422 .521 .631
3.00 3.25 3.50 3.75
.375 .441 .511 .587
.501 .588 .681 .782
.626 .734 .852 .978
4.00 4.25 4.50 4.75
.668 .754 .845 .941
.890 ).005 1.126 1.255
1.113 1.256 1.408 1.569
5.00 5.25 5.50 5.75
1.043 1.150 1.262 1.379
1.391 1.533 1.683 1.839
6.00 6.50 7.00 7.50
1.502 1.763 2.044 2.347
2.003 2.350 2.726 3.129
8.00 8.50 9.00 9.50
2.670 3.560 4.450 3.014 4.019 5.024 3.379 4.S06 5.632 3.765 5.020 6.275
DIA
13116
Y2
'11&
o/a
11116
%
.097 .152 .219 .298
.111 .174 .250 .341
.125 .196 .282 .383
.139 .217 .313 .426
.153 .239 .344 .468
.167 .261 .375 .511
.181 .282 .407 .554
.389 .493 .608 .736
.445 .563 .695 .841
.SOl .634 .782 .946
.556 .704 .869 1.052
.612 .774 .956 1.157
.668 .845 1.043 1.262
.723 .915 1.130 1.367
.876 .751 .881 1.028 1.022 1.192 1.173 1.369
1.001 1.175 1.363 1.564
1.126 1.322 1.533 1.76.0
Ya
1
.209 .326 .469 .639
.223 .348 .501 .681
.779 .834 .986 1.056 1.217 1.304 1.472 1.577
.890 1.126 1.391 1.683
1.252 1.377 1.502 1.469 1.616 1.763 1.704 1.874 2.044 1.956 2.151 2.347
1.627 1.752 1.877 1.910 2.056 2.203 2.215 2.385 2.555 2.542 2.738 2.933
2.003 2.350 2.726 3.129
1.335 1.558 1.780 2.003 1.S07 1.758 2.009 2.261 1.690 1.971 2.253 2.534 1.883 2.196 2.510 2.824
2.225 2.512 2.816 3.138
2.893 3.265 3.661 4.079
1.738 1.916 2.103 2.299
2.086 2.434 2.781 2.300 2.683 3.066 2.524 2.945 3.365 2.759 3.218 3.678
3.477 3.824 4.172 3.833 4.216 4.600 4.207 4.627 5.048 4.598 5.058 5.517
2.503 2.938 3.407 3.911
3.004 3.525 4.088 4.693
3.129 3.450 3.786 4.138
3.504 4.005 4.506 4.113 4.700 5.288 4.770 5.451 6.133 5.476 6.258 7.040
5.006 5.875 6.814 7.822
5.340 6.230 7.120_ 8.010 8.900 6.028 7.033 8.038 9.043 10.04 6.758 7.885 9.011 10.13 11.26 7.530 8.785 10.04 11.29 12.55
2.448 2.670 2.763 3.014 3.098 3.379 3.451 3.765
.195 .304 .438 .596
lo/i6
3.115 3.517 3.942 4.393
3.338 3.560 3.768 4.019 4.224 4.S06 4.706 5.020
4.520 4.867 5.215 4.983 5.366 5.749 5.469 5.889 6.310 5.977 6.437 6.897
5.563 6.133 6.731 7.356
5.507 6.008 6.508 7.009 7.509 8.010 6.463 7.051 7.638 8.226 8.813 9.401 7.496 8.177 8.858 9.540 10.22 10.90 8.605 9.387 10.16 10.95 11.73 12.51 9.790 11.05 12.39 13.80
10.68 12.05 13.51 15.06
11.57 12.46 13.35 13.06 14.06 15.07 14.64 15.77 16.89 16.31 17.57 18.82
14.24 16.07 18.02 20.08
10.00 10.50 11.00 11.50
4.172 5.563 6.953 8.344 9.734 4.600 6.133 7.666 9.199 10.73 5.048 6.731 ··8.413 10.09 11.77 5.517 7.356 9.196 11.03 12.87
11.12 12.51 12.26 13.79 13.46 15.14 14.71 16.55
13.90 15.33 16.82 18.39
15.29 16.68 16.86 18.39 18.SO 20.19 20.23 22.06
18.07 19.46 20.85 19.93 21.46 22.99 21.87 23.55 25.24 23.90 25.74 27.58
22.25 24.53 26.92 29.42
12.00 12.50 13.00 13.50
6.008 8.010 10.01 6.519 8.691 10.86 7.051 9.401 11.75 7.603 10.13 12.67
14.00 14.50 15.00 15.50
8.177 8.771 9.387 10.02
16.00 16.50 17.00 17.50
12.01 13.03 14.10 15.20
14.01 15.21 16.45 17.74
16.02 17.38 18.80 20.27
18.02 19.55 21.15 22.81
20.02 21.72 23.50 25.34
22.02 23.90 25.85 27.87
24.03 26.07 28.20 30.41
26.03 28.24 30.55 32.94
28.03 3D.42 32.90 35.48
30.03 32.59 35.25 38.01
32.04 34.76 37.60 40.55
10.90 11.69 12.51 13.36
13.62 16.35 14.61 17.54 15.64 18.77 16.70 20.04
19.07 20.46 21.90 23.38
21.80 23.39 25.03 26.72
24.53 26.31 28.16 30.06
27.25 29.23 31.28 33.41
29.98 32.70 32.16 35.08 34.41 37.54 36.75 40.09
35.43 38.00 40.67 43.43
38.15 40.93 43.80 46.77
40.88 43.85 46.93 SO. 11
43.61 46.78 50.06 53.45
10.68 11.35 12.05 12.77
14.24 15.14 16.07 17.03
17.80 18.93 20.09 21.29
21.36 22.71 24.11 25.55
24.92 26.50 28.13 29.81
28.48 30.28 32.15 34.07
32.04 34.07 36.17 38.32
35.60 37.86 40.18 42.58
39.16 42.72 41.64 45.43 44.20 48.22 46.84 51.10
46.28 49.21 52.24 55.36
49.84 53.00 56.26 59.62
53.40 56.79 60.28 63.88
56.96 60.57 64.30 68.14
18.00 18.50 19.00 19.50
13.51 14.27 15.06 15.86
18.02 22.52 27.03 19.03 23.79 28.55 20.08 25.1;) 30.12 21.15 26.43 31.72
31.54 33.31 35.14 37.01
36.04 38.07 40.16 42.30
40.55 42.83 45.18 47.59
45.05 47.59 50.20 52.87
49.56 52.35 55.22 58.16
54.06 57.11 60.24 63.45
58.57 61.87 65.26 68.74
63.07 66.63 70.28 74.03
67.58 71.39 75.30 79.31
72.09 76.15 80.32 84.60
20.00 20.SO 21.00 21.50
16.68 17.53 18.39 19.28
22.25 27.81 33.37 23.37 29.22 35.06 24.53 30.66 36.79 25.71 32.14 38.56
38.93 40.90 42.92 44.99
44.SO 46.75 49.06 51.42
SO.06 52.59 55.19 57.85
55.62 58.44 61.32 64.28
61.18 66.75 64.28 70.13 67.46 73.59 70.71 77.13
72.31 75.97 79.72 83.56
77.87 81.81 85.85 89.99
83.43 89.00 87.66 93.50 91.99 98.12 96.42 102.85
405
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
DIA
31!6
\t4
51!6
Ya
11!6
22 22Y2 23 23Y2 24 24Yl 25 25Y2 26 26Y2 27 27Yl 28 28Y2 29 29Y2 30 30Yl 31 31Y2 32 32Yl 33 33Yl 34 34Y2 35 35Yl 36 36Y2 37 37Yl
20 21 22 23 24 25 26 27 28 29 30 32 33 34 35 36 38 39 40 41 43 44 45 47 48 50 51 53 54 56 57 59
27 28 29 31 32 33 35 36 38 39 41 42
34 35 37 38
45 47 48 50 52 53 55 57 59 61 62 64 66 68 70 72 74 76 78
40 42 44 46 48 50 52 54 56 59 61 63 65 68 70 73 75 78 80 83 85 88 91
38 38Yz 39 39Yz 40 40Yz 41 41Yz 42 42Yz 43 43I!z 44 44Yz 45 45Yz 46 46Yz 47 47\7 48 48Yz 49 49Y7
60 62 63 65 67 68 70 72 74 75 77 79 81 83 84 86 88 90 92 94 96 98 100 102
80 82 85 87 89 91 94 96 98 100 103 105 108 110 113 115 118 120 123 126 128 131 134 136
44
40
42 43 45 47 49 51 53 55 56 58 61 63 65 67 69 71 73 76 78
Ya
61 63 66 69 72 75 78 81 85 88 91 95 98 90 102 94 105 97 109 100 113 103 116 107 120 110 124 114 128 118 132 121 136 125 140 129 145 132 149 136 153 140 158 144 162 148 167 152 171 156_ ,-176
67 70 74 77 80 83 87
102 105 108 111 114 117
47 49 51 54 56 58 61 63 66 68 71 74 76 79 82 85 88 91 94 97 100 103 106 109 113 116 119 123 126 130 133 137
120 124 127 130 134 137 140 144 147 151 154 158 162 165 169 173 J77 180 184 188 192 196 200 204
141 144 148 152 156 160 164 168 172 176 180 184 188 193 197 202 206 210 215 220 224 229 234 239
161 165 169 i74 178 182 187 192 196 201 206 211 215 220 225 230 235 241 246 251 256 262 267 273
94
80
96
99
83 85 88
90 93 95 98
il!6
~-
100 103 106 108
III 114 117 120 123 126 129 132 135 138 141 144 147 150 154 157 160 164 167 170
~
Y2 54 56 59 61 64' 67 70 72 75 78 81 84 87
181 186 190 195 200 205 210 216 221 226 231 237 242 248 253 259 265 271
276 282 288 294 301 307
90 94 98 101 105 109 113 117 121 125 129 134 138 142 147 151 156 161 166 170 175 180 185 190 196 201 206 212 217 223 228 234 240 245 251 257 263 269 275 282 288 294 301 307 314 320 327 334 341
1J1!6
%
1l1!6
74 81 87 77 84 92 81 88 96 84 92 100 88 96 104 92 100 109 96 104 113 99 109 118 103 113 122 107 117 127 112 122 132 116 126 137 120 131 142 124 136 147 129 140 152 157 133 145 138 150 163 142 155 168 147 160 174 152 166 179 157 171 185 162 176 191 167 182 197 172 187 203 177 193 209 182 199 215 187 204 221 193 210 228 198 216 234 204 222 W 209 228 247 215 ~5 254 221 241 261 227 247 268 233 254· 275 239 260 282 245 267 289 274 251 297 257 281 304 263 287 311 270 294 319 276 301 327 283 309 334 289 316 342 296 323 350 303 330 358 310 338 366 317 345 374 324 353 383 331 361 391 338 369 399 345 377 408 352 384 417 360 393 4.25 367 401 434 375 409 443
Ya
151!6
1
94 99 103 108 112 117 122 127 132 137 142 147 153 158 164 169 175 181 187 193 199 206 212 218 225 232 238 245 252 259 267 274
101 106 110 115 120 125 130 136 141 146 152 158 164 169 175 182 188 194 200 207 214 220 227 234 241 248 256 263 270 278 286 293
108 113 118 123 128 134 139 145 150 156 162 168 174 181 187 194 200 207 214 221 228 235 242 250 257 265 273 280 288 296 305 313
281 289 296 304 312 319 327 335 343 352 360 368 377 386 394 403 412 421 430 439 449 458 467 477
301 309 317 325 334 342 351 359 368 377 386 395 404 413 422 432 441 451 461 471 481 491 501 511
321 330 338 347 356 365 374 383 392 402 411 421 431 441 451 461 471 481 492 502 513 523 534 545
406
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
DIA
lf16
Y4
5/16
Ys
'/16
YI
9/16
Ya
50 50'4 51 51 Yz 52 52Yi 53 53Yz 54 5417 55 55Y7 56 56Yz 57 571h 58 58Y7 59 59Yz 60 60Yz 61 61 Yz 62 62Yz 63 63Yz 64 64Yz 65 65Yl 66 66Yz 67 67Yz 68 68Yz 69 69'll 70 70'll 71
104 106 109 III 113 115 117 119 122 124 126 129 131 133 136 138 140 143 145 148 150 153 155 158 160 163 166 168 171 174 176 179 182 184 187 190 193 196 199 202 204 207 210 213 216 219 222 225 228 232 235 238 241 244 247 251
139 142 145 148 150 153 156 159 162 165 168 17l 1/4 178 181 184 187 190 194 197 200 204 207 210 214 217 221 224 228 231 235 239 242 246 250 253 257 261 265 269 273 276 280 284 288 292 296 301 305 309 313 317 321 326 330 334
174 177 181 184 188 192 195 199 203 207 210 214 218 222 226 230 234 238 242 246 250 255 259 263 267 272 276 280 285 289 294 298 303 307 312 317 322 326 331 336 341 346 351 355 360 365 371 376 381 386 391 396 402 407 412 418
209 213 217 221 226 230 234 239 243 248 252 257 262 266 271 276 281 286 290 295 300 305 310 316 321 326 331 336 342 347 353 358 363 369 375 380 386 392 397 403 409 415 421 427 433 439 445 451 457 463 469 476 482 488 495 501
243 248 253 258 263 268 273 279 284 289 294 300 305 311 316 322 327 333 339 345 350 356 362 368 374 380 386 393 399 405 411 418 424 430 437 444 450 457 463 470 477 484 491 498 505 512 519 526 533 540 548 555 562 570 577 585
278 284 289 295 301 307 313 318 324 330 337 343 349 355 361 368 374 381 387 394 401 407 414 421 428 435 442 449 456 463 470 477 485 492 499 507 514 522 530 537 545 553 561 569 577 585 593 601 609 617 626 634 643 651 660 668
313 319 326 332 338 345 352 358 365 372 379 386 392 400 407 414 421 428 436 443 451 458 466 473 481 489 497 505 513 521 529 537 545 553 562 570 579 587 596 605 613 622 631 640 649 658 667 676 685 695 704 713 723 732 742 752
348 355 362 369 376 383 391 398 406 413 421 428 436 444 452 460 468 476 484 492 501 509 517 526 535 543 552 561 570 579 588 597 606 615 624 634 643 653 662 672 681 691 701 7ll 721 731 741 751 762 772 782 793 803 814 825 835
7l'll 72 72'll 73 73'll 74 74'll 75 75'll 76 76Yz 77 77'll
11/16
%
382 417 390 426 398 434 406 443 414 451 422 460 430 469 438 478 446 487 454 496 463 505 471 514 480 523 488 533 497 542 506 552 515 561 524 571 532 581 542 591 551 601 560 611 569 621 579 631 588 641 598 652 607 662 617 673 627 684 636 694 646 705 656 716 666 727 676 738 687 749 697 760 707 772 718 783 728 795 739 806 750 818 760 829 841 771 782 853 793 865 804 877 815 889 826 902 838 914 849 926 860 939 872 951 884 964 895 977 907 989 919 1002
13/16
Ys
15/16
1
452 461 470 479 489 498 508 517 527 537 547 557 567 577 587 598 608 619 629 640 651 662 673 684 695 706 718 729 740 752 764 776 787 799 812 824 836 848 861 873 886 899 911 924 937 950 963 977 990 1003 1017 1031 1044 1058 1072 1086
487 497 506 516 526 537 547 557 568 578 589 600 611 622 633 644 655 666 678 689 701 713 724 736 748 761 773 785 797 810 823 835 848 861 874 887 900 914 927 940 954 968 981 995 1009 1023 1038 1052 1066 1081 1095 1110 1125 1139 1154 1169
521 532 543 553 564 575 586 597 608 620 631 643 654 666 678 690 702 714 726 738 751 764 776 789 802 815 828 841 854 868 881 895 909 922 936 950 965 979 993 1008 1022 1037 1052 1066 1081 1096 1112 1127 1142 1158 1173 1189 1205 1221 1237 1253
556 567 579 590 602 613 625 637 649 661 673 685 698 710 723 736 749 761 775 788 801 814 828 842 855 869 883 897 911 926 940 955 969 984 999 1014 1029 1044 1059 1075 1090 1106 1122 1137 1153 1170 1186 1202 1218 1235 1252 1268 1285 1302 1319 1336
407
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
DIA
3/16
14
5/16
%
7/16
Yz
9/16
18
11/16
%
13iJ6
!Is
15/16
1
78 78Yz 79 79Yz 80 80Yz 81 81 Yz 82 82Yz 83 83Yz 84 84Yz 85 85Yz 86 86Yz 87 87Yz 88 88Yz 89 89Yz 90 90Yz 91 91 Yz 92 92Yz 93 93Yz 94 94Y1 95
254 257 260 264 267 270 274 277 281 284 287 291 294 298 301 305 309 312 316 319 323 327 330 334 338 342 345 349 353 357 361 365 369 373 377 380 384 389 393 397 401 405 409 413 417 421 426 430 434 438 443 447 451 456 460 464
338 343 347 352 356 360 365 369 374 379 383 388 392 397 402 407 411 416 421 426 431 436 441 446 451 456 461 466 471 476 481 486 492 497 502 507 513 518 523 529 534 540 545 551 556 562 567 573 579 584 590 596 602 607 613 619
423 428 434 439 445 451 456 462 468 473 479 485 491 496 502 508 514 520 526 532 538 545 551 557 563 569 576 582 589 595 601 608 614 621 628 634 641 648 654 661 668 675 681 688 695 702 709 716 723 731 738 745 752 759 767 774
508 514 521 527 534 541 547 554 561 568 575 582 589 596 603 610 617 624 632 639 646 654 661 668 676 683 691 699 706 714 722 729 737 745 753 761 769 777 785 793 801 810 818 826 834 843 851 860 868 877 885 894 902 911 920 929
592 600 608 615 623 631 639 647 655 663 671 679 687 695 703 712 720 728 737 745 754 762 771 780 788 797 806 815 824 833 842 851 860 869 879 888 897 907 916 925 935 944 954 964 973 983 993 1003 1013 1023 1033 1043 1053 1063 1073 1083
677 686 694 703 712 721 730 739 748 757 766 776 785 794 804 813 823 832 842 852 862 871 881 891 901 911 921 931 942 952 962 973 983 994 1004 1015 1025 1036 1047 1058 1068 1079 1090 1101 1113 1124 1135 1146 1157 1169 1180 1192 1203 1215 1227 1238
761 771 781 791 801 811 821 831 842 852 862 873 883 894 904 915 926 936 947 958 969 980 991 1003 1014 1025 1036 1048 1059 1071 1082 1094 1106 1118 1130 1141 1153 1166 1178 1190 1202 1214 1227 1239 1252 1264 1277 1289 1302 1315 1328 1341 1354 1367 1380 1393
846 857 868 879 890 901 912' 924 935 947 958 970 981 993 1005 1017 1029 1041 1053 1065 1077 1089 1102 1114 1126 1139 1152 1164 1177 1190 1203 1216 1229 1242 1255 1268 1282 1295 1308 1322 1336 1349 1363 1377 1391 1405 1419 1433 1447 1461 1475 1490 1504 1519 1533 1548
931 943 955 967 979 991 1004 1016 1029 1041 1054 1067 1079 1092 1105 1118 1131 1145 1158 1171 1185 1198 1212 1225 1239 1253 1267 1281 1295 1309 1323 1337 1352 1366 1381 1395 1410 1425 1439 1454 1469 1484 1499 1514 1530 1545 1560 1576 1592 1607 1623 1639 1655 1670 1687 1703
1015 1028 1041 1055 1068 1081 1095 1108 1122 1136 1150 1164 1177 1192 1206 1220 1234 1249 1263 1278 12:12 1307 1322 1337 1352 1367 1382 1397 1412 1428 1443 1459 1475 1490 1506 1522 1538 1554 1570 1586 1603 1619 1636 1652 1669 1686 1702 1719 1736 1753 1770 1788 1805 1822 1840 1857
1100 1114 1128 1143 1157 1172 1186 1201 1216 1230 1245 1260 1276 1291 1306 1322 1337 1353 1368 1384 1400 1416 1432 1448 1464 1481 1497 1514 1530 1547 1564 1580 1597 1614 1632 1649 1666 1684 1701 1719 1736 1754 1772 1790 1808 1826 1844 1862 1881 1899 1918 1937 1955 1974 1993 2012
1184 1200 1215 1230 1246 1262 1277 1293 1309 1325 1341 1357 1374 1390 1407 1423 1440 1457 1474 1491 1508 1525 1542 1560 1577 1595 1612 1630 1648 1666 1684 1702 1720 1739 1757 1776 1794 1813 1832 1851 1870 1889 1908 1927 1947 1966 1986 2006 2026 2045 2065 2086 2106 2126 2146 2167
1269 1285 1302 1318 1335 11352 1369 1386 1403 1420 1437 1454 1472 1489 1507 1525 1543 1561 1579 1597 1615 1634 1652 1671 1690 1708 1727 1746 1766 1785 1804 1824 1843 1863 1883 1902 1922 1943 1963 1983 2003 2024 2044 2065 2086 2107 2128 2149 2170 2192 2213 2235 2256 2278 2300 2322
1354 1371 1389 1406 1424 1442 1460 1478 1496 1514 1533 1551 1570 1589 1608 1627 1646 1665 1684 1704 1723 1743 1762 1782 1802 1822 1843 1863 1883 1904 1924 1945 1966 1987 2008 2029 2051 2072 2094 2115 2137 2159 2181 2203 2225 2247 2270 2292 2315 2338 2361 2384 2407 2430 2453 2477
951~
913 50Yz 97 97~~
98 98Yz 99 99Yz 100 100Yz 101 101Yz 102 102Yz 103 1031;, 104 104Yz 105 105Yz
408
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
DIA
106 106\1 107 107\1 108 108\1 109 109\1 110 110\1
111
111\1 112 112\1 113 113\1 114 114\1 115 115\1 116 116\1 117 117\1 118 118\1 119 119\1 120 120\1 121 121\1 122 122\1 123 123Y, 124 124\1 125 125\1 126 126\1 127 127Y1
128 128\1 129 129YI 130 1301;7 131 131 \1 132 1321;7 133 133 1h
3/16
\t4
469 473 478 482 487 491 496 500 505 509 514 519 523 528 533 537 542 547 552 557 561 566 571 576 581 586 591 596 601 606 611 616 621 626 631 636 641 647 652 657 662 668 673 678 684 689 694 700 705 710 716 721 727 732 738 744
625 631 637 643 649 655 661 667 673 679 685 692 698 704 710 717 723 729 736 742 749 755 761 768 775 781 788 794 801 808 814 821 828 835 842 848 855 862 869 876 883 890 897 904 911 919 326 933 940 947 955 962 969 977 984 991
51I6
781 789 796 804 811 819 826 834 841 849 857 864 872 880 888 896 904 912 920 928 936 944 952 960 968 976 985 993 1001 1010 1018 1026 1035 1043 1052 1061 1069 1078 1086 1095 1104 1113 1121 1130 1139 1148 1157 1166 1175 1184 1193 1202 1212 1221 1230 1239
%
938 946 955 964 973 982 991 1000 1010 1019 1028 1037 1047 1056 1065 1075 1084 1094 1103 1113 1123 1132 1142 1152 1162 1172 1182 1192 1202 1212 1222 1232 1242 1252 1262 1273 1283 1293 1304 1314 1325 1335 1346 1356 1367 1378 1389 1399 1410 1421 1432 1443 1454 1465 1476 1487
WEIGHTS IN POUNDS 7/16
1094 1104 1115 1125 1135 1146 1157 1167 1178 1189 1199 1210 1221 1232 1243 1254 1265 1276 1287 1299 1310 1321 1333 1344 1355 1367 1379 1390 1402 1413 1425 1437 1449 1461 1473 1485 1497 1509 1521 1533 1545 1558 1570 1582 1595 1607 1620 1633 1645 1658 1671 1683 1696 1709 1722 1735
\1 1250 1262 1274 1286 1298 1310 1322 1334 1346 1358 1371 1383 1396 1408 1421 1433 1446 1459 1471 1484 1497 1510 1523 1536 1549 1562 1575 1589 1602 1615 1629 1642 1656 1669 1683 1697 1711 1724 1738 1752 1766 1780 1794 1809 1823 1837 1851 1866 1880 1895 1909 1924 1338 1953 1968 1983
91I6
1406 1420 1433 1446 1460 1473 1487 1501 1514 1528 1542 1556 1570 1584 1598 1612 1627 1641 1655 1670 1684 1699 1713 1728 1743 1758 1772 1787 1802 1817 1832 1848 1863 1878 1894 1909 1924 1940 1956 1971 1987 2003 2019 2035 2051 2067 2083 2099 2115 2131 2148 2164 2181 2197 2214 2231
%
I III 6
1563 11719 1577 1735 1592 1751 1607 1768 1622 1784 1637 1801 1652 1817 1667 1834 1683 1851 1698 1868 1713 1885 1729 1902 1744 1919 1760 1936 1776 1953 1791 1971 1807 1988 1823 2005 1839 2023 1855 2041 1871 2058 1887 2076 1904 2094 1920 2112 1936 2130 1953 2148 1969 2166 1986 2184 2003 2203 2019 2221 2036 2240 2053 2258 2070 2277 2087 2296 .2104 2314 2121 2333 2138 2352 2156 2371 2173 2390 2190 2409 2208 2429 2225 2448 2243 2467 2261 2487 2278 2506 2296 2526 2314 2546 2332 2565 2350 2585 2368 2605 2386 2625 2405 2645 2423 2665 2441 2686 2460 2706 2478 2726
%
1875 1893 1911 1928 1946 1965 1983 2001 2019 2038 2056 2075 2093 2112 2131 2150 2169 2188 2207 2226 2246 2265 2284 2304 2324 2343 2363 2383 2403 2423 2443 2463 2484 2504 2525 2545 2566 2587 2607 2628 2649 2670 2692 2713 2734 2756 2777 2799 2820 2842 2864 2886 2908 2930 2952 2974
13/16
2031 2050 2070 2089 2109 2128 2148 2168 2187 2207 2227 2248 2268 2288 2308 2329 2349 2370 2391 2412 2433 2454 2475 2496 2517 2539 2560 2582 2603 2625 2647 2669 2691 2713 2735 2757 2780 2802 2825 2847 2870 2893 2916 2939 2962 2985 3008 3032 3055 3079 3102 3126 3150 3174 3198 3222
Ya
2188 2208 2229 2250 2271 2292 2313 2334 2356 2377 2399 2420 2442 2464 2486 2508 2530 2552 2575 2597 2620 2642 2665 2688 2711 2734 2757 2780 2804 2827 2850 2874 2898 2922 2945 2969 2994 3018 3042 3066 3091 3115 3140 3165 3190 3215 3240 3265 3290 3316 3341 3367 3392 3418 3444 3470
lYi6
2344 2366 2388 2411 2433 2456 2478 2501 2524 2547 2570 2593 2617 2640 2664 2687 2711 2735 2759 2783 2807 2831 2855 2880 2905 2929 2954 2979 3004 3029 3054 3079 3105 3130 3156 3182 3207 3233 3259 3285 3312 3338 3364 3391 3418 3444 3471 3498 3525 3552 3580 3607 3635 3662 3690 3718
1 2500 2524 2547 2571 2595 2619 2644 2668 2692 2717 2741 2766 2791 2816 2841 2866 2892 2917 2943 2968 2994 3020 3046 3072 3098 3124 3151 3177 3204 3231 3258 3285 3312 3339 3366 3394 3421 3449 3477 3504 3532 3561 3589 3617 3645 3674 3703 3731 3760 3789 3818 3848 3877 3906 3936 3966
409
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
WEIGHTS IN POUNDS
DIA
3/16
Y4
5/16
%
7/16
12
9116
%
11/16
Y4
13j16
Va
15116
1
134 13412 135 135» 136 13612 137 13712 138 1381;7 139 13912 140 14012 141 14112 142 1421h 143 14312 144 14412 145 14512 146 14612 147 14712 148 14812 149 14912 150 15012 151 15112 152 15212 153 15312 154 15412 155 15512 156 15612 157 15712 158 15812 159 15912 160 16012 161 16112
749 755 760 766 772 777 783 789 795 800 806 812 818 824 829 835 841 847 853 859 865 871 877 883 889 895 902 908 914 520 '926 932 939 945 951 958 964 970 977 983 989 996 1002 1009 1015 1022 1028 1035 1041 1048 1055 1061 1068 1075 1081 1088
999 1006 1014 1021 1029 1036 1044 1052 1059 1067 1075 1082 1090 1098 1106 1114 1122 1130 1137 1145 1153 1161 1170 1178 1186 1194 1202 1210 1218 1227 1235 1243 1252 1260 1268 1277 1285 1294 1302 1311 1319 1328 1336 1345 1354 1362 1371 1380 1389 1397 1406 1415 1424 1433 1442 1451
1249 1258 1267 1277 1286 1296 1305 1315 1324 1334 1343 1353 1363 1373 1382 1392 1402 1412 1422 1432 1442 1452 1462 1472 1482 1492 1503 1513 1523 1533 1544 1554 1564 1575 1585 1596 1606 1617 1628 1638 1649 1660 1671 1681 1692 1703 1714 1725 1736 1747 1758 1769 1780 1791 1802 1814
1498 1509 1521 1532 1543 1555 1566 1578 1589 1601 1612 1624 1635 1647 1659 1671 1682 1694 1706 1718 1730 1742 1754 1766 1779 1791 1803 1815 1828 1840 1852 1865 1877 1890 1902 1915 1928 1940 1953 1966 1979 1992 2005 2018 2031 2044 2057 2070 2083 2096 2109 2123 2136 2149 2163 2176
1748 1761 1774 1787 1800 1814 1827 1840 1854 1867 1881 1894 1908 1922 1935 1949 1963 1977 1991 2005 2019 2033 2047 2061 2075 2089 2104 2118 2132 2147 2161 2176 2190 2205 2220 2234 2249 2264 2279 2294 2309 2324 2339 2354 2369 2384 '2399 2415 2430 2446 2461 2476 2492 2508 2523 2539
1998 2013 2028 2043 2058 2073 2088 2103 2119 2134 2149 2165 2181 2196 2212 2228 2243 2259 2275 2291 2307 2323 2339 2355 2371 2388 2404 2420 2437 2453 2470 2487 2503 2520 2537 2553 2570 2587 2604 2621 2638 2656 2673 2690 2707 2725 2742 2760 2777 2795 2813 2830 2848 2866 2884 2902
2247 2264 2281 2298 2315 2332 2349 2366 2384 2401 2418 2436 2453 2471 2488 2506 2524 2541 2559 2577 2595 2613 2631 2650 2668 2686 2705 2723 2741 2760 2779 2797 2816 2835 2854 2873 2892 2911 2930 2949 2968 2988 3007 3026 3046 3065 3085 3105 3124 3144 3164 3184 3204 3224 3244 3264
2497 2516 2534 2553 2572 2591 2610 2629 2648 2668 2687 2706 2726 2745 2765 2784 2804 2824 2844 2864 2884 2904 2924 2944 2964 2985 3005 3026 3046 -3067 3087 3108 3129 3150 3171 3192 3213 3234 3255 3277 3298 3320 3341 3363 3384 3406 3428 3450 3472 3494 3516 3538 3560 3582 3605 3627
2747 2767 2788 2809 2829 2850 2871 2892 2913 2934 2956 2977 2998 3020 3041 3063 3085 3106 3128 3150 3172 3194 3216 3238 3261 3283 3306 3328 3351 3373 3396 3419 3442 3465 3488 3511 3534 3558 3581 3604 3628 3651 3675 3699 3723 3747 3771 3795 3819 3843 3867 3892 3916 3941 3965 3990
2996 3019 3041 3064 3087 3109 3132 3155 3178 3201 3224 3247 3271 3294 3318 3341 3365 3389 3412 3436 3460 3484 3509 3533 3557 3582 3606 3631 3655 3680 3705 3730 3755 3780 3805 3830
3246 3270 3295 3319 3344 3368 3393 3418 3443 3468 3493 3518 3543 3569 3594 3620 3645 3671 3697 3723 3749 3775 3801 3827 3854 3880 3907 3933 3960 3987 4014 4041 4068 4095 4122 4149 4177 4204 4232 4260 4287 4315 4343 4371 4400 4428 4456 4485 4513 4542 4570 4599 4628 4657 4686 4715
3496 3522 3548 3575 3601 3628 3654 3681 3708 3735 3762 3789 3816 3843 3871 3898 3926 3953 3981 4009 4037 4065 4093 4122 4150 4178 4207 4236 4264 4293 4322 4351 4381 4410 4439 4469 4498 4528 4558 4587 4617 4647 4677 4708 4738 4768 4799 4830 4860 4891 4922 4953 4984 5015 5047 5078
3746 3774 3802 3830 3858 3887 3915 3944 3973 4001 4030 4059 4088 4118 4147 4177 4206 4236 4266 4295 4325 4356 4386 4416 4446 4477 4508 4538 4569 4600 4631 4662 4693 4725 4756 4788 4819 4851 4883 4915 4947 4979 5012 5044 5076 5109 5142 5175 5207 5240 5274 5307 5340 5374 5407 5441
3995 4025 4055 4085 4115 4146 4176 4207 4237 4268 4299 4330 4361 4392 4424 4455 4487 4518 4550 4582 4614 4646 4678 4710 4743 4775 4808 4841 4874 4907 4940 4973 5006 5040 5073 5107 5141 5175 5209 5243 5277 5311 5346 5380 5415 5450
~'856
3881 3906 3932 3958 3983 4009 4035 4061 4087 4113 4140 4166 4192 421'9 4245 4272 4299 4326 4353
5~84
5519 5555 5590 5625 5661 5696 5732 5768 5803
410
WEIGHT OF CIRCULAR PLATES WEIGHTS IN POUNDS
ALL DIMENSIONS IN INCHES
DIA
162 16212 163 16312 164 16412 16S' 16512 166 16612 167 16712 168 168Yl 169 169Yl 170 170Yl 171 171Yl 172 17212 173 173Yl 174 174Yl 175 175Yl 176 176Yl 177 177Yl 178 178 112 179 17912 180 18012 181 18112 182 18212 183 18312 184 18412 185 18512 186 18612 187 18N? 188 188Yl 189 189Yl
3lis
Y4
5/16
Ys
7/16
1095 1102 1108 1115 1122 1129 1136 1143 1150 1157 1164 1170 1177 1185 1192 1199 1206 1213 1220 1227 1234 1241 1249 1256 1263 1270 1278 1285 1292 1300 1307 1314 1322 1329 1337 1344 1352 1359 1367 1374 1382 1390 1397 1405 1412 1420 1428 1436 1443 1451 1459 1467 1475 1482 1490 1498
1460 1469 1478 1487 1496 1505 1514 1524 1533 1542 1551 1561 1570 1579 1589 1598 1608 1617 1627 1636 1646 1655 1665 1674 1684 1694 1704 1713 1723 1733 1743 1753 1762 1772 1782 1792 1802 1812 1822 1832 1843 1853 1863 1873 1883 1894 1904 1914 1924 1935 1945 1956 1966 1977 1987 1998
1825 1836 1847 1859 1870 1882 1893 1905 1916 1928 1939 1951 1962 1974 1986 1998 2009 2021 2033 2045 2057 2069 2081 2093 2105 2117 2129 2142 2154 2166 2178 2191 2203 2215 2228 2240 2253 2265 2278 2291 2303 2316 2329 2341 2354 2367 2380 2393 2406 2418 2431 2444 2458 2471 2484 2497
2190 2203 2217 2231 2244 2258
2555 2571 2586 2602 2618 2634 2650 2666 2682 2699 2715 2731 2747 2764 2780 2797 2813 2830 2846 2863 2880 2897 2913 2930 2947 2964 2981 2998 3015 3033 3050 3067 3084 3102 3119 3136 3154 3172 3189 3207 3224 3242 3260 3278 3296 3314 3332 3350 3368 3386 3404 3422 3441 3459 3477 3496
'i.?72
2285 2299 2313 2327 2341 2355 2369 2383 2397 241l 2426 2440 2454 2468 2483 2497 2512 2526 2541 2555 2570 2585 2599 2614 2629 2644 2659 2673 2688 2703 2718 2734 2749 2764 2779 2794 2810 2825 2840 2856 2871 2887 2902 2918 2933 2949 2965 2981 2996
I 12 2920 2938 2956 2974 2992 3010 3029 3047 3066 3084 3103 3121 3140 3159 3177 3196 3215 3234 3253 3272 3291 3310 3330 3349 3368 3388 3407 3427 3446 346b 3485 3505 3525 3545 3565 3585 3605 3625 3645 3665 3685 3705 3726 3746 3767 3787 3808 3828 3849 3870 3890 3911 3932 3953 3974 3995
9liS
Ys
liliS
3285 3305 3325 3346 3366 3387 3407 3428 3449 3470 3491 3511 3532 3554 3575 3596 3617 3638 3660 3681 3703 3724 3746 3768 3789 3811 3833 3855 3877 3899 3921 3943 3966 3988 4010 4033 4055 4078 4100 4123 4146 4169 4191 4214 4237 4260 4284 4307 4330 4353 4377 4400 4424 4447 4471 4494
3650 3672 3695 3718 3740 3763 3786 3809 3832 3855 3878 3902 3925 3948 3972 3995 4019 4043 4066 4090 4114 4138 4162 4186 4210 4235 4259 4283 4308 4332 4357 4381 4406 4431 4456 4481 4506 4531 4556 4581 4606 4632 4657 4683 4708 4734 4759 4785 4811 4837 4863 4889 4915 4941 4968 4994
4015 4039 4064 4089 4114 4139 4165 4190 4215 4241 4266 4292 4317 4343 4369 4395 4421 4447 4473 4499 4525 4552 4578 4605 4631 4658 4685 4712 4738 4765 4792 4820 4847 4874 4901 4929 4956 4984 5011 5039 5067 5095 5123 5151 5179 5207 5235 5264 5292 5321 5349 5378 5407 5435 5464 5493
% 4380 4407 4434 4461 4488 4516 4543 4571 4598 4626 4654 4682 4710 4738 4766 4794 4823 4851 4880 4908 4937 4966 4994 5023 5052 5081 5111 5140 5169 5199 5228 5258 5287 5317 5347 5377 5407 5437 5467 5497 5528 5558 5589 5619 5650 5681 5711 5742 5773 5804 5836 5867 5898 5930 5961 5993
13/16
Va
15lis
4744 4774 4803 4833 4862 4892 4922 4952 4982 5012 5042 5072 5102 5133 5163 5194 5225 5255 5286 5317 5348 5379 5411 5442 5473 5505 5537 5568 5600 5632 5664 5696 5728 5760 5792 5825 5857 5890 5923 5955 5988 6021 6054 6087 6121 6154 6187 6221 6254 6288 6322 6356 6390 6424 6458 6492
5109 5141 5173 5205 5236 5268 5300 5333 5365 5397 5430 5462 5495 5528 5561 5594 5627 5660 5693 5726 5760 5793 5827 5861 5894 5928 5962 5997 6031 6065 6099 6134 6169 6203 6238 6273 6308 6343 6378 6414 6449 6484 6520 6556 6591 6627 6663 6699 6736 6772 6808 6845 6881 6918 6955 6991
5474 5508 5542 5576 5610 5645 5679 5714 5748 5783 5818 5852 5887 5923 5958 5993 6028 6064 6100 6135 6171 6207 6243 6279 6315 6352 6388 6425 6461 6498 6535 6572 6609 6646 6684 6721 6759 6796 6834 6872 6910 6948 6986 7024 7062 7101 7139 7178 7217 7255 7294 7333 7373 7412 7451 7491
1 5839 5875 5912 5948 5984 6021 6058 6094 6131 6168 6205 6243 6280 6317 6355 6393 6430 6468 6506 6544 6583 6621 6659 6698 6737 6775 6814 6853 6892 6931 6971 7010 7050 7089 7129 7169 7209 7249 7289 7330 7370 7411 7451 7492 7533 7574 7515 7656 7698 7739 7781 7822 7864 7906 7948 7990
411
WEIGHT OF CIRCULAR PLATES ALL DIMENSIONS IN INCHES
I
WEIGHTS IN POUNDS
DIA
3/16
1f4
5/16
%
7/16
lh
9/16
%
11/16
Y.
13/16
Ya
15/16
1
190 190Y1 191 191Yz 192 192Yl 193 193Y2 194 194Yl 195 195Y2 196 196Y7 197 1971h 198 198Y2 199 199Y2 200
1506 1514 1522 1530 1538 1546 1554 1562 1570 1578 1586 1595 IG03 1611 1619 1627 1636 1644 1652 1660 1669
2008 2019 2029 2040 2051 2061 2072 2083 2094 2104 2115 2126 2137 2148 2159 2170 2181 21£2 2203 2214 2225
2510 2523 2537 2550 2563 2577 2590 2603 2617 2630 2644 2658 2G71 2685 2698 2712 2726 2740 2754 2767 2781
3012 3028 3044 3060 3076 3092 3108 3124 3140 3157 3173 3189 3205 3222 3238 3255 3271 3288 3304 3321 3338
3514 3533 3551 3570 3589 3607 3626 3645 3664 3683 3702 3721 3740 3759 3778 3797 3816 3836 3855 3874 3894
4016 4037 4059 4080 4101 4123 4144 4166 4187 4209 4230 4252 4274 4296 4318 4340 4362 4384 4406 4428 4450
4518 4542 4566 4590 4614 4638 4662 4686 4710 4735 4759 4784 4808 4833 4857 4882 4907 4932 4956 4981 5006
5020 5047 5073 5100 5126 5153 5180 5207 5234 5261 5288 5315 5342 5370 5397 5424 5452 5479 5507 5535 5563
5522 5551 5581 5610 5639 5669 5698 5728 5757 5787 5817 5847 5877 5907 5937 5967 5997 6027 6058 6088 6119
6024 6056 6088 6120 6152 6184 6216 6248 6281 6313 6346 6378 6411 6444 6476 6509 6542 6575 6609 6642 6675
6526 6561 6595 6630 6664 6699 6734 6769 6804 6839 6874 6910 6945 6980 7016 7052 7087 7123 7159 7195 7231
7028 7065 7102 7140 7177 7214 7252 7290 7327 7365 7403 7441 7479 7517 7556 7594 7633 7671 7710 7749 7788
7530 7570 7610 7650 7690 7730 7770 7810 7851 7891 7932 7973 8013 8054 8095 8137 8178 8219 8261 8302 8344
8032 8075 8117 8160 8202 8245 8288 8331 8374 8417 8461 8504 8548 8591 8635 8679 8723 8767 8811 8856 8900
412
WEIGHT OF BOLTS With square heads and hexagon nuts in pounds per 100 Length Under Head Inches
Diameter of Bolt in Inches
~
VB
Y2
%
%
Ys
1
2.38 2.71 3.05 3.39
6.11 6.71 7.47 8.23
13.0 14.0 15.1 16.5
24.1 25.8 27.6 29.3
38.9 41.5 44.0 46.5
67.3 70.8
95.1 99.7
3.73 4.06 4.40 4.74
8.99 9.75 10.5 11.3
17.8 19.1 20.5 21.8
31.4 33.5 35.6 37.7
49.1 52.1 55.1 58.2
74.4 77.9 82.0 86.1
5.07 5.41 5.75 6.09
12.0 12.8 13.5 14.3
23.2 24.5 25.9 27.2
39.8 41.9 44.0 46.1
61.2 64.2 67.2 70.2
6.42 6.76 7.10 7.43
15.1 15.8 16.6 17.3
28.6 29.9 31.3 32.6
48.2 50.3 52.3 54.4
73.3 76.3 79.3 82.3
7.77 8.11 8.44 8.78
18.1 18.9 19.6 20.4
33.9 35.3 36.6 38.0
85.3 88.4 91.4 94.4
9.12 9.37 9.71 10.1
21.1 21.7 22.5 23.3
39.3 40.4 41.8 43.1
10.4 10.7 11.0 11.4
24.0 24.8 25.5 26.3
44.4 45.8 47.1 48.5
56.5 5&.6 60.7 62.8 64.9 66.7 68.7 70.8 72,9 75.0 77.1 79.2
11.7
27.0 28.6 30.1 31.6
49.8 52.5 55.2 57.9
10 10Y2 11 11 %
33.1 34.6 36.2 37.7
12 12% 13 13% 14 14% 15 15%
39.2
1
1~
IY2 1%
2
2~
2Y2 2%
3
3~
3% 3% 4
4~
412 4% 5
5~
5Y2 5%
6
6~
6% 6 3,4 7
7~
7% 7% 8 8Y2 9 9%
16 Per Inch Additional Notes:
1.3
3.0
1%
17.1
104 109 114 119
143 149 155 161
206 213
90.2 94.4 98.5 103
124 129 135 140
168 174 181 188
221 229 237 246
107
145 151 156 162
195 202 208 215
254 262 271 279
III
115 119
167 172 178 183
222 229 236 242
288 296 304 313
97.4 100 103 106
123 127 131 136 140 143 147 151
188 193 198 204
321 329 337 345
109 112 115 118
156 160 164 168
209 214 220 225
249 255 262 269 275 282 289 296
354 362 371 379
81.3 85.5 89.7 93.9
121 127 133 139
172 180 189 197
231 241 252 263
303 316 330 343
387 404 421 438
60.6 63.3 66.0 68.7
98.1 102 106 110
145 151 157 163
205 213 221 230
274 284 295 306
357 371 384 398
454 471 488 505
71.3 74.0 76.7 79.4
115 119 123 127
170 176 182 188
238 246 254 263
316 327 338 349
411 425 439 452
522 538 556 572
82.1 84.8 87.5 90.2
131 135 140 144
194 200 206 212
271 279 287 296
359 370 381 392
466 479 493 507
589 605 622 639
92.9
148
218
304
402
520
656
5.4
8.4
12.1
16.5
21.4
27.2
33.6
Bolt is Regular Square Bolt, ASA B18.2 and nut is finished Hexagon Nut, ASA B18.2. This table conforms to weight standards adopted by the Industrial Fasteners Institute.
413
WEIGHTS OF OPENINGS
NOZZLES With ANSI Welding Neck Flange and Reinforcing Pad (Table for Quick Reference)
CLASS
SIZE 1Y2
2 3 4 6 8 10 12 14 16 18 20 24
150
300
600
900
6 9 16 25 45 65 95 135 165 215 331 428 589
11 12 25 40 70 110 145 220 285 370 610 708 1131
13 15 40 60 120 175 285 365 515 695 935 1245 1815
17 28 45 75 155 260 375 550 775 965 1379 1693 3041
1500 18 30 70 105 225 380 620 920
NOZZLES With ASA Welding Neck Flange, Reinforcing Pad, Blind Flange Studs and Gasket (Table for .Quick Reference)
CLASS
SIZE 3 4 6 8 10 12 14
16 18 20 24
150
300
600
900
25 42 71 110 165 245 296 440 540 700 1000
41 67 120 191 272 404 521 800 1000 1200 1885
60 101 206 314 516 660 893 1300 1600 2100 2990
129 268 457 665 963 1269 1600 2250 2800 5140
1500 118 178 384 682 1127 1695
77
3510 4460 5700 9350
SCREWED COUPLINGS NOMINAL PIPE SIZE
%
30001b 60001b
0.25 0.50
% 0.44 1.00
1
1%
0.63 2.13
2.19 4.38
2 3.13 7.75
2%
4.00 10.75
3 6.75 13.50
414 WEIGHTS OF PACKING Pounds Per Cubic Foot SIZE
!i %
Yz
RASCHIG RING CERAMIC
CARBON
60
133
46
61
94
55
75
Yz % %
CARBON STEEL
INTALOX
PLASTIC
54 50 45
27
132 56
62
50
52
%
37
7.25 44
34
94 1
42
39
27
30
5.50
44
71
1
l!i lYz lYz 2
3Yz
PALL RING
CARBON STEEL
3
46
62
31
43
49
34
26
4.75
42
41
37
27
24
4.50
42
37
25
23
46 37 4.25
4
36
The data condensed from the technical literature of the U. S. Stoneware Co. The weights of carbon steel in percentage of other metals: Stainless Steel 105%, Copper 120%, Aluminum 37%, Monel or Nickel 115%
WEIGHTS OF INSULATION POUNDS PER CUBIC FOOT CALCIUM SILICATE
12.5
FOAMGLASS
9.0
MINERAL WOOL
8.0
GLASS FIBER
4-8
FOAMGLASS
8-10
For mechanical design of vessel add 80% to these weights which covers the weight of seal, jacketing and the absorbed moisture.
415
SPECIFIC GRAVITIES METALS 62°F. Aluminum .............................. 2.70 Antimony ............................. 6.618 Barium .................................... 3. 78 Bismuth ................................ 9.781 Boron ................................... 2.535 Brass: 80 C., 2 OZ ............... 8.60 70 C., 3 OZ ............... 8.44 60 C., 4 OZ ............... 8.36 50 C., 5 OZ ............... 8.20 Bronze: 90 C., 10 T. ................ 8.78 Cadmium ............................... 8.648 Calcium .................................. 1.54 Chromium ............................... 6.93 Cobalt .................................... 8.71 Copper ................................... 8.89 Gold ....................................... 19.3 Iridium ................................. 22.42 Iron - cast .................... 7.03 - 7.73 Iron - wrought ............ 7.80 - 7.90 Lead ................................... 11.342 Magnesium ........................... 1.741 Manganese ............................... 7.3 Mercury(68°F.) ................. 13.546 Molybdenum .......................... 10.2 Nickel ...................................... 8.8 Platinum .............................. 21.37 Potassium ............................ 0.870 Silver ....................... 10.42 - 10.53 Sodium ............................... 0.9712 Steel ....................................... 7.85 Tantalum ................................. 16.6 Tellurium ................................ 6.25 Tin .......................................... 7.29 Titanium ................................... 4.5 Tungsten ..................... 18.6-19.1 Uranium ................................. 18.7 Vanadium ................................. 5.6 Zinc ............................. 7.04 -7.16
HYDROCARBONS 60/600 F. Ethane ................................ 0.3564 Propane .............................. 0.5077 N-butane ............................ 0.5844 Iso-butane .......................... 0.5631 N-pentane .......................... 0.6310 Iso-pentane ........................ 0.6247 N-hexane ............................ 0.6640 2-methylpentane ................ 0.6579 3-methylpentane ................ 0.6689 2,2-dimethylbutane (neohexane) ................. 0.6540 2, 3-dimethylbutane .......... 0.6664 N-heptane .......................... 0.6882 2-methylhexane .................. 0.6830 3-methylhexane .................. 0.6917 2, 2-dimethylpentane ......... 0.6782 2, 4-dimethylpentane ......... 0.6773 I, 1-dimethylcyclopentane 0.7592
N-octane ............................ 0.7068 Cyclopentane ..................... 0.7504 Methylcyclopentane .......... 0.7536 Cyclohexane ...................... 0.7834 Methylcyclohexane ........... 0.7740 Benzene .............................. 0.8844 Toulene ............................... 0.8718
LIQUIDS 62°F. Acetic Acid ........................... 1.06 Alcohol, commercial .............. 0.83 Alcohol, pure ......................... 0.79 Ammonia ................................ 0.89 Benzine .................................. 0.69 Bromine .................................. 2.97 Carbolic acid .......................... 0.96 Carbon disulphide ................. 1.26 Cotton-seed oil ...................... 0.93 Ether, sulphuric .................... 0.72 Fluoric acid ........................... 1.50 Gasoline ................................ 0.70 Kerosene ................................ 0.80 Linseed oil ............................ 0.94 Mineral oil ............................. 0.92 Muriatic acid .......................... 1.20 Naphtha ................................. 0.76 Nitric Acid ............................ 1.50 Olive oil ................................ 0.92 Palm oil ................................. 0.97 Petroleum oil ......................... 0.82 Phosphoric acid .................... 1.78 Rape oil ................................. 0.92 Sulphuric acid ....................... 1.84 Tar .......................................... 1.00 Turpentine oil .................:...... 0.87 Vinegar ................................... 1.08 Water ...................................... 1.00 Water, sea ............................... 1.03 Whale oil ............................... 0.92
GASSES 32°F. Air ................................................ Acetylene .................................... Alcohol vapor .............................. Ammonia..................................... Carbon dioxide .......... .................. Carbon monoxide ........................ Chlorine ....................................... Ether vapor .................................. Ethylene ...................................... Hydrofluoric acid ....................... Hydrogen .................................... Illuminating gas ........................... Mercury vapor ............................ Marsh gas .................................... Nitrogen ....................................... Nitric oxide .................................. Nitrous oxide ................................ Oxygen ........................................
1.000 0.920 1.601 0.592 1.520 0.967 2.423 2.586 0.967 1.261 0.069 0.400 6.940 0.555 0.971 1.039 1.527 1.106
Sulphur dioxide ............................ 2.250 Water vapor ................................. 0.623
NITSCELLANEOUSSOLIDS 62° F. Asbestos .................................. 2.4 Asphaltum ............................... 1.4 Borax ........................................ 1.8 Brick, common ...... .................... 1.8 Brick, fire ................................. 2.3 Brick, hard ............................... 2.0 Brick, pressed .......................... 2.2 Brickwork, in mortar ............... 1.6 Brickwork, in cement... ............ 1. 8 Cement, Portland (set) ............. 3.1 Chalk ........................................ 2.3 Charcoal ................................... 0.4 Coal, anthracite ....................... 1.5 Coal, bituminous ..................... 1.3 Concrete ................................... 2.2 Earth, dry ................................. 1.2 Earth, wet.... ............................. 1. 7 Emery ....................................... 4.0 Glass ........................................ 2.6 Granite ..................................... 2.7 Gypsum .................................... 2.4 Ice ............................................ 0.9 Iron slag ................................... 2.7 Limestone ................................ 2.6 Marble ...................................... 2.7 Masonry ................................... 2.4 Mica ......................................... 2.8 Mortar ...................................... 1.5 Phosphorus .............................. I. 8 Plaster of Paris ........................ 1.8 Quartz ...................................... 2.6 Sand, dry .................................. 1.6 Sand, wet ................................. 2.0 Sandstone ................................ 2.3 Slate ......................................... 2.8 Soapstone ................................ 2.7 Sulphur .................................... 2.0 Tar, bituminous ........................ 1.2 Tile ........................................... 1.8 Tap rock ................................... 3.0 Speci~c gravity of sO.lids and liquids is the ratIO of theIr denSity to the density of water at a specified temperature. Specific gravity of gases is the ratio of their density to the density of air at standard conditions of pressure and temperature. To find the weight per cubic foot of a material, multiply the specific gravity by 62.36. EXAMPLE: The weight of a cubic foot of gasoline 62.36 x 0.7 =43.65Ibs.
416
VOLUME OF SHELLS AND HEADS I.D. of Vessel in. 12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90 96 102 108 114 120 126 132 138 144
Cylindrical SHELL/LIN. FT. Cu.Ft. 0.8 1.1
1.4 1.8 2.2 2.6 3.1 3.7 4.3 4.9 5.6 6.3 7.1 7.9 8.7 9.6 12.6 15.9 19.6 23.8 28.3 33.2 38.5 44.2 50.3 56.7 63.6 70.9 78.5 86.6 95.0 103.9 113.1
2: 1 ELLIP. HEAD*
Gal.
Bbl.
Wt. of Water lb.
Cu.Ft.
Gal.
Bbl.
Wt. of Water lb.
5.9 8.0 10.4 13.2 16.3 19.7 23.5 27.6 32.0 36.7 41.8 47.2 52.9 58.9 65.3 72.0 94.0 119.0 146.9 177.7 211.5 248.2 287.9 330.5 376.0 424.4 475.9 530.2 587.5 647.7 710.9 777.0 846.0
0.14 0.19 0.25 0.31 0.39 0.47 0.56 0.66 0.76 0.87 0.99 1.12 1.26 1.40 1.55 1.71 2.24 2.83 3.50 4.23 5.04 5.91 6.85 7.87 8.95 10.11 11.33 12.62 13.99 15.42 16.93 18.50 20.14
49 67 87 110 136 165 196 230 267 306 349 394 441 492 545 601 784 993 1226 1483 1765 2071 2402 2758 3138 3542 3971 4425 4903 5405 5932 6484 7060
0.1 0.2 0.3 0.4 0.6 0.8 1.0 1.3 1.7 2.0 2.5 3.0 3.5 4.2 4.8 5.6 8.4 11.9 16.3 21.8 28.3 35.9 44.9 55.2 67.0 80.3 95.4 112.2 130.9 151.5 174.2 190.1 226.2
0.98 1.55 2.32 3.30 4.53 6.03 7.83 9.96 12.44 15.30 18.57 22.27 26.47 31.09 36.27 41.98 62.67 89.23 122.4 162.9 211.5 268.9 335.9 413.1 501.3 601.4 713.8 839.5 979.2 1134 1303 1489 1692
0.02 0.04 0.06 0.08 0.11 0.14 0.19 0.24 0.30 0.36 0.44 0.53 0.63 0.74 0.86 1.00 1.49 2.12 2.91 3.88 5.04 6.40 8.00 9.84 11.94 14.32 17.00 20.00 23.31 27.00 31.03 35.46 40.29
8.17 12.98 19.37 27.58 37.83 50.35 65.37 83.11 103.8 127.7 155.0 185.9 220.1 259.5 302.6 350.4 523.0 744.6 1021 1360 1765 2244 2802 3447 4184 5018 5957 7006 8171 9459 10876 12428 14120
*Volume within the straight flange is not included
417
VOLUME OF SHELLS AND HEADS 1.0. of Vessel in.
12 14 16 18 20 22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90 96 102 108 114 120 126 132 138 144
ASME F & D. HEAD*
I
Cu.Ft.
Gal.
0.08 0.12 0.19 0.27 0.37 0.50 0.65 0.82 1.10 1.30 1.64 1.88 2.15 2.75 3.07 3.68 5.12 7.30 10.08 13.54 17.65 22.32 28.47 35.56 42.51 52.14 60.96 73.66 84.35 97.32 108.7 127.0 147.9
0.58 0.94 1.45 2.04 2.80 3.78 4.86 6.14 8.21 9.70 12.30 14.10 16.10 20.60 23.00 27.50 38.30 54.60 75.40 101 13~
167 213 266 318 390 456 551 631 728 813 950 1106
I
HEMIS. HEAD*
Bbl.
Wt. of Water lb.
Cu.Ft.
Gal.
Bbl.
Wt. of Water lb.
0.01 0.04 0.03 0.05 0.07 0.09 0.12 0.15 0.20 0.23 0.29 0.34 0.38 0.49 0.55 0.65 0.91 1.30 1.80 2.41 3.14 3.98 5.07 6.33 7.57 9.29 10.86 13.12 15.02 17.33 19.36 22.62 26.33
4.83 7.83 12.08 17.00 28.33 31.49 40.49 51.15 68.40 80.81 102.5 117.5 134.1 171.6 191.6 229.1 319.1 454.9 628.2 843.9 1100 1391 1775 2216 2649 3249 3799 4590 5257 6065 6773 7915 9214
0.26 0.42 0.62 0.88 1.21 1.61 2.09 2.66 3.33 4.09 4.96 5.95 7.07 8.31 9.70 11.22 16.76 - 23.86 32.73 43.56 56.55 71.90 89.80 110.4 134.0 160.8 190.9 224.5 261.8 303.1 348.5 398.2 452.4
1.96 3.11 4.64 6.61 9.07 12.07 15.67 19.92 24.88 30.60 37.14 44.54 52.88 62.19 72.53 83.97 125.3 178.5 244.8 325.8 423.0 537.8 671.7 826.2 1003 1203 1428 1679 1958 2267 2607 2978 3384
0.05 0.07 0.11 0.16 0.22 0.29 0.37 0.47 0.59 0.73 0.88 1.06 1.26 1.48 1.73 2.00 2.98 4.25 5.83 7.76 10.07 12.80 16.00 19.67 23.87 28.63 34.00 39.98 46.63 53.98 62.06 70.91 80.57
16.34 25.95 38.74 55.16 75.66 100.7 130.7 166.2 207.6 255.4 309.9 371.7 441.2 519.0 605.3 700.7 1046 1489 2043 2719 3530 4488 5606 6895 8368 10037 11914 14012 16343 18919 21752 24856 28241
*Volume within the straight flange is not included
418 PARTIAL VOLUMES IN HORIZONTAL CYLINDERS l
I
I
~J3
Partial volumes of horizontal cylinder equals total volume x coefficient (found from table below)
10
EXAMPLE HORIZONTAL CYLINDER D = 10 ft., 0 in. H = 2.75 ft. L = 60 ft., 0 in. TOTAL VOLUME: 0.7854 x D2 xL Find the partial volume of the cylindrical shell Total volume: 0.7854 x 102 x 60 = 4712.4 cu. ft.
Coefficient from table: H/D = 2.75/10 =.275 Refer to the first two figures (.27) in the column headed (H/D) in the table below. Proceed to the right until the coefficient is found under the column headed (5) which is the third digit. The coefficient of 0.275 is found to be .223507 Total volume x coefficient = partial volume 4712.4 x .223507 = 1053.25 cu. ft. cu. ft. multiplied by 7.480519 = U. S. Gallon cu. ft. multiplied by 28.317016 = Liter COEFFICIENTS H/D
0
1
2
3
4
5
6
7
8
9
.00 .01 .02 .03 .04
.000000 .001692 .004ii3 .008742 .0134li
.0000.'53 .0019.52 .005134 .009179 .013919
.000151 .002223 .005503 .009625 .014427
.000279 .002507 .005881 .010076 .014940
.000429 .002800 .006267 .010534 .015459
.000600 .003104 .006660 .010999 .015985
.000788 .003419 .007061 .011470 .016515
.000992 .003743 .007470 .011947 .017052
.001212 .004077 .007886 .012432 .017593
.001445 .004421 .008:HO .012920 .018141
.05 .06 .07 .08 .09
.018692 .024496 .030772 .037478 .044579
.0192.50 .025103 .031424 .038171 .04.5310
.019813 .02.5715 .032081 .038867 .046043
.020382 .026331 .032740 .039569 .046782
.0209.5.',) .026952 .033405 .040273 .047523
.021533 .027578 .034073 .040981 .048268
.022115 .028208 .oa4747 .041694 .049017
.022703 .028842 .035423 .042410 .049768
.023296 .029481 .036104 .043129 .050524
.023894 .030124 .036789 .043852 .051283
.10 .11 .12 .13 .14
.052044 .0598.50 .067972 .076393 .085094
.052810 .0.53579 .0.54351 .060648 .061449 .062253 .068802 .069633 .070469 .0772.51 .078112 .078975 .085979 .086866 .087756
.05.5126 .063062 .071307 .079841 .088650
.055905 .063872 .072147 .080709 .089545
.056688 .064687 .072991 .081581 .090443
.057474 .065503 .073836 .082456 .091343
.058262 .066323 .074686 .083332 .092246
.059054 .067147 .07.5539 .084212 .093153
.15 .16 .17 .18 .19
.094061 .103275 .112728 .122403 .132290
.094971 .104211 .113686 .123382 .133291
.095884 .10.'5147 .114646 .124364 .134292
.096799 .106087 .115607 . 12.5:J47 .135296
.097717 .107029 .116.572 .126333 .136302
.098638 .107973 .1.17538 .127321 .137310
.099560 .108920 .118506 .128310 .138320
.100486 .109869 .119477 .129302 .139332
.101414 .110820 .120450 .130296 .140345
.102343 .111773 .121425 .131292 .141361
.20 .21 .22 .23 .24
.142378 .1526.'59 .163120 .173753 .1845.'50
.143398 .153697 .164176 .174825 .185639
.144419 .1.54737 .165233 .175900 .186729
.145443 .155779 .166292 .176976 .187820
.146468 .147494 .148524 .149554 .156822 .157867 .1.'58915 .l!i9963 .167353 .168416 .169480 .170546 .178053 179131 .180212 .181294 .188912 190007 .191102 .192200
.150587 .161013 .171613 .182378 .193299
.151622 .162066 .172682 .18346:1 .194400
.25 .26 .27 .28 .29
.19.5501 .206600 .2li839 .229209 .240703
.196604 .207718 .218970 .230352 .2418.59
.197709 .208837 .220102 .231498 .243016
.198814 .209957 .221235 .232644 .244173
.199922 .211079 .222371 .233791 .245333
.201031 .202141 .203253 .212202 .213326 .214453 .223507 .224645 .225783 .234941 .236091 .237242 .246494 .247655 .248819
.204368 .215580 .226924 .238395 .249983
.205483 .216708 .228065 .239548 .251148
.:30 .31
.2.')231.5 .264039
.253483 .254652 .255822 .265218 .266397 .267578
.256992 .258165 .259338 .260512 .268760 .269942 .271126 .272310
.261687 .262863 .273495 .274682
419
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS COEFFICIENTS (Cont.) HID
0
1
2
3
4
5
6
7
8
9
.285401 .286598 .297403 .298605 .309492 .310705
.32 .33 .34
.275869 .277058 .278247 .279437 .287795 .288992 .290191 .291390 .299814 .301021 .302228 .3034:38
.280627 .281820 .292591 .293793 .304646 .305857
.35 .:36 .37 .38 .39
.:311918 .324104 .336363 .348690 .:mI082
.313134 .325:326 .337593 .349926 .36232.')
.:314350 .:326550 .338823 .:351164 .363568
.315566 .327774 .340054 .3.'>2402 .364811
.31678a .328999 .341286 .353640 .366056
.318001 .330225 .342519 .354879 .367300
.:319219 .331451 .343751 .3.'>6119 .:368545
.320439 .332678 .344985 .357359 . 3697!)()
.321660 .333905 .346220 .358599 .371036
.322881 .335134 .3474.'>5 .359840 .372282
.40 ,41 ,42 ,43
.:373530 .:3860:m .:398.577 ,41116:) .42;m;8
.:374778 .387283 .:m9834 ,412426 .42.5052
.376026 .388537 .401092 .413687 ,426316
.377275 .389790 .402350 .414949 .427,582
.378,524 .391044 .403608 .416211 .428846
.379774 .392298 .404866 .417473 ,4:30112
.:381024 .393M3 .40612.5 .418736 .431:378
.382274 .394808 .407384 .419998 .4:~2645
.383526 .:396063 .408645 .421261 .433911
.384778 .397320 .409904 .422.'52:'5 .43.5li8
.444050 .456741 .469453 .482176 .494906
.445318 .458012 .470725 .483449 ,496179
.446587 .459283 .471997 .484722 .497452
.447857 .460554 .473269 .485995 .498726
A4
.283013 .284207 .294995 .296198 .307068 .308280
.45 ,46 .47 .48 .49
.43644.5 .44912.') .461825 .474541 .487269
.437712 .450394 .463096 .475814 o4R8.542
.438979 .451663 .464367 .477086 o48!l814
.440246 .4,52932 .465638 .4783.58 .491087
.441,514 .4.54201 .466910 .479631 .492360
.442782 .455472 .468182 .480903 .493633
.50 .51 .52 .:i3 .54
.500000 .512731 .525459 .53817,5· .550875
.501274 .514005 .526731 .5:39446 .,5,52143
.502548 ..515278 .528003 ..540717 .,55a4U
.503821 .5165.51 .52927.5 .541988 .5.54682
..505094 ..517824 .530547 ..543259 .5.559,50
.506367 .:'510097 .,531818 .,544,528 .:'557218
.507640 .520369 .533090 .545799 .558486
.508913 ..521642 .534362 .547068 .559754
.510186 .,522914 .,535633 .548337 .561021
.511458 .524186 .536904 .549606 .562288
.55 .,56 .57 .58 .59
.5635.55 .576212 588835 .601423 .613970
.564822 .577475 .590096 .602680 .615222
.566089 ..578739 .591355 .60:3937 .616474
.56n55 ..,)80002 .592616 .605192 .617726
..'568622 .581264 .593875 .606447 .618976
.:'569888 ..582527 .595134 .607702 .620226
.571154 .583789 .596392 .608956 .621476
..,)72418 .58,5051 .597650 .610210 .622725
.573684 ..586313 .598908 .611463 .623974
.574948 .587574 .600166 .612717 .625222
.1i0 .61 62 .63 .1\4
.626470 .638918 .651:UO .663637 .tl758!l6
.027718 .640160 .652545 .664866 .677119
.628!)64 .1\41401 .6.'i:mm .6fif!095 .H71n40
.630210 .6:n·I.')i'l .632700 .642641 .64:3~R1 .645121 .6SS01S .65624!l .0."i7481 .607322 .6f>R."i4!l .669775 .G7!)561 .680781 .681!}!}9
.63:J!)44 .646360 .658714 .671001 .683217
.63518!) .647.')98 .659946 .672226 .fl84434
.636432 .648836 .661177 .673450 .68.')6.'50
.637675 .6.')0074 .662407 .674674 .686866
.fi.'l .fl6 .H7 .fi8 .fI!)
.688082 .700186 .712205 .724131 .7:W161
.6R929.'5 .701392 .713402 .72.5:318 .7:37137
.GHO!iOS .702.')97 .7 I 45!)!} .72650.') .7:3S31a
.691720 .703802
.69;')3.')4 .707409 .719373 .731240 .74:l00R
.696.'562 .708610 .720.563 .732422 .74417S
.697772 .709809 .721753 .733603 .74.5348
.698979 .711008 .722942 .n4782 .74(i.')17
.70 .71 .72 .7::1 .74
.747(lS;,) .748S.,)2 .7.'i!}297 .7l104.52 .7707!)1 .7719:\.') .7S2HH .7S:3292 .79:\400 .7!}4.,)17
.7.')0017 .76WO.') .77:m7fi .7S4420 .7!l;')fi:32
.7.54667 .766200 .7776211 .78S921 .I-\0007R
.7.').,)R27 .71i73.'iG .7787f1.') .700c)4:l .80l1S(i
.7.')6984 .768502 .779898 .791163 $02291
.7,')8141 .i6!l64S .7810:m .792282
.727690 .7394SR
.6!)2!l32 .70.')()().') .716987 .728874 .740H62
.694143 .706207 .718180 .7300.58
.7.,)IIS1 .7627:)S .774217 .78.').')47 .7!l!i747
.7:)2:\4;') .7m90!) .77.'):l5.'i .7S1ili74 .7!l7l-\5!l
.753."i06 .76.')0.')9
.71579:~
.7418:~5
.7764~l3
.787798 .7!18969
.80:~396
.7~)
.80449~)
.76 .77 .7S .79
.81.')450 .826247 .S3nR8() .847341
.805G()() .816.')37 .827318 .8:n9:34 .848:m,
.8OGiOI :817622 .1-\28387 .838987 .84941:\
.807800 .8187()(i .829454 .lW)()37 .8.'>0446
.808898 .819788 .8:l0.520 .84108.') .8.')14i6
.S0099:! .R20869 .831584 .842133 .8.'>2.')06
.R11088 .821947 .832647 .843178 .8.5:l532
.R12180 .823024 .8:l3708 .844221 .8.54.5.')7
.813271 .824100 .834767 .845263 .855581
.814361 .825175 .835824 .846303 .856602
.80 .81 .82 .83 .84
.857(i22 .8G7710 .877597 .887272 .896725
.8586:39 .868708 .87857.,> .888227 .897657
.8.')9655 .8tl9704 .879.'>50 .889180 .898586
.860668 .870698 .880523 .8!}0131 .899514
.861680 .871690 .881494 .891080 .900440
.862690 .872679 .882462 .892027 .901362
.863698 .873667 .883428 .892971 .902283
.864704 .874653 .884393 .893913 .903201
.865708 .875636 .885354 .894853 .904116
.866709 .876618 .886314 .895789 .905029
.8.'> .86 .87 .88 .89
.905939 .914906 .923607 .932028 .940150
.906847 .915788 .924461 .932853 .940946
.!lO7754 .908657 .916668 .917.544 .925:n4 .926164 .933677 .934497 .941738 .942526
.909557 .918419 .927009 .935313 .943312
.910455 .919291 .927853 .936128 .944095
.911350 .920159 .928693 .936938 .944874
.912244 .921025 .929531 .937747 .945649
.913134 .921888 .930367 .938551 .946421
.914021 .922749 .931198 .939352 .947190
.90 .91 .92
.947956 .948717 .955421 .956148 .962522 .96:-1211
.!l49476 .9S0232 .956871 .957590 .963896 .964577
.950983 .9.'>1732 .958306 .959019 .965253 .965927
.952477 .953218 .959727 .960431 .966595 .967260
.953957 .954690 .961133 .961829 .967919 .968.')76
420 PARTIAL VOLUMES IN HORIZONTAL CYLINDERS COEFFICIENTS (cont.) HID .!l3 .94 .9!i
.!)(i .Hi .98 . HI) 1.00
0
1
.!If>!l22R .!lIM'il) .97!i.504 .97f>106 .!lSlaOR .!lX()58:{ .!lHl2.,)8 .91):;227 .H9S30X 1.000000
.9S18;,)!l .!lRiOSO .!l!lHi!)() .!lH!ii'i7!l .!I!lk.').'lii
2
3
4
.HiO;")l9 .!lill.')~ .!liI792 .976i04 .!l772!l7 .!lii88.'} .HX240i .987.,)6R .!l!)2114 .!l9i'i923 .!19878B
.982948 .!l88();):{ .H!l2i'j:{O .996257 .999008
5 .972422 .978467
.98348.') .984015 .988530 .989001 .992939 .9!J3340 .996.,}81 .996896 .999212 .999400
6
7
8
9
.!17:1048 .973669 .97D045 .979618
.974285 .980187
.974897 .980750
.984541 .98946(\ .99:1733 .997200 .999.571
.98.,}573 .990375 .994497 .997777 .999849
.986081 .990821 .994866 .998048 .999947
.985060 .989924 .994119 .997493 .9D9721
421
PARTIAL VOLUMES IN HORIZONTAL CYLINDERS (pp.rcentage Relation of Diameter to Volume)
10
20
30
40
I 50
I
60
PERCENTAGE OF TOTAL DIAMETER
70
100 HID
80
90
100
422
PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES
~
0
Two 2: 1 Ellipsoidal Heads on Horizontal Vessel Total Volume: 0.2618 D3 D
Q~Q Two 2: 1 Ellipsoidal Heads on Vertical Vessel Total Volume: 2.0944 D3 D
H
O~HO
Sphere Total Volume: 0.5236 D3
Partial volumes of ellipsoidal heads and spheres equals total volume x coefficient (found from table below) EXAMPLE:
D = 10ft., 0 in.
H=2.75 ft.
Find the partial volume of(2) 2: 1 ellipsoidal heads ofa horizontal vessel. The total volume of the two heads: 0.2618 x D3 = 0.2618 x 103 = 261.8 cu. ft. Coefficient from table:
HID=2.75110 = .275 Referr to the first two figures (.27) in the column headed (HID) in the table below. Proceed to the right until the coefficient is found under the column headed (5) which is the third digit. The coefficient of .275 is found to be .185281. Total volume x coefficient = partial volume 261.8 x 185281 = 48.506 cu. ft. cu. ft. multiplied by 7.480519 = U.S. Gallon c.u. ft. multiplied by 28.317016 = Liter COEFFICIENTS
HID .00 .01 .02 .03 .04
.000003 .000360 .001304 .002823 .004905
2 .000012 .000429 .001431 .003006 .005144
3 .000027 .000503 .001563 .003195 .005388
0 .000000 .000298 .001184 .002646 .004672
4 .000048 .000583· .001700 .003389 .005638
5 .000075 .000668 .001844 .003589 .005893
6 .000108 .000760 .001993 .003795 .006153
.05 .06 .07 .08 .09
.007250 .010368 .014014 .018176 .022842
.007538 .010709 .014407 .018620 .023336
.007831 .011055 .014806 .019069 .023835
.008129 .011407 .015209 .019523 .024338
.008433 .011764 .015618 .019983 .024847
.008742 .012126 .016031 .020447 .025360
.10 .11 .12 .13 .14
.028000 .033638 .039744 .046306 .053312
.028542 .034228 .040380 .046987 .054037
.029090 .034822 .041020 .047672 .054765
.029642 .035421 .041665 .048362 .055499
.030198 .036025 .042315 .049056 .056236
.030760 .036633 .042969 .049754 .056978
1
.000146 .000857 .002148 .004006 .006419
8 .000191 .000960 .002308 .004222 .006691
9 .000242 .001069 .002474 .004444 .006968
.009057 .012493 .016450 .020916 .025879
.009377 .012865 .016874 .021390 .026402
.009702 .013243 .017303 .021869 .026930
.010032 .013626 .017737 .022353 .027462
.031326 .037246 .043627 .050457 .057724
.031897 .037864 .044290 .051164 .058474
.032473 .038486 .044958 .051876 .059228
.033053 .039113 .045630 .052592 .059987
7
.15 .060750 .061517 .062288 .063064 .063843 .064627 .065415 .066207 .067003 .067804 .16 .068608 .069416 .070229 .071046 .071866 .072691 .073519 .074352 .075189 .076029 .17 .076874 .077723 .078575 .079432 .080292 .081156 .082024 .082897 .083772 .084652
423 PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES: COEFFICIENTS (Cont.) HID 0 1 2 3 4 5 6 7 9 8
.18 .085536 .086424 .087315 .. 088210 .089109 .090012 .090918 .091829 .092743 .093660 .19 .094582 .095507 .096436 .097369 .098305 .099245 .1 00189 .101136 .102087 .103042 .20 .21 .22 .23 .24
.104000 .113778 .123904 .134366 .145152
.104962 .114775 .124935 .135430 .146248
.105927 .115776 .125970 .136498 .147347
.106896 .116780 .127008 .137568 .148449
.107869 .117787 .128049 .138642 .149554
.108845 .118798 .129094 .139719 .150663
.109824 .119813 .130142 .140799 .151774
.110808 .120830 .131193 .141883 .152889
.111794 .121852 .132247 .142969 .154006
.112784 .122876 .133305 .144059 .155127
.25 .26 .27 .28 .29
.156250 .167648 .179334 .191296 .203522
.157376 .168804 .180518 .192507 .204759
.158506 .169963 .181705 .193720 .205998
.159638 .171124 .182894 .194937 .207239
.160774 .172289 .184086 .196155 .208484
.161912 .173456 .185281 .197377 .209730
.163054 .174626 .186479 .198601 .210979
.164198 .175799 .187679 .199827 .212231
.165345 .176974 .188882 .201056 .213485
.166495 .178153 .190088 .202288 .214741
.30 .31 .32 .33 .34
.216000 .228718 .241664 .254826 .268192
.217261 .230003 .242971 .256154 .269539
.218526 .231289 .244280 .257483 .270889
.219792 .232578 .245590 .258815 .272240
.221060 .233870 .246904 .260149 .273593
.222331 .235163 .248219 .261484 .274948
.223604 .236459 .249536 .262822 .276305
.224879 .237757 .250855 .264161 .277663
.226157 .239057 .252177 .265503 .279024
.227437 .240359 .253500 .266847 .280386
.35 .36 .37 .38 .39
.281750 .295488 .309394 .323456 .337662
.283116 .296871 .310793 .324870 .339090
.284484 .298256 .312194 .326286 .340519
.285853 .299643 .313597 .327703 .341950
.287224 .301031 .315001 .329122 .343382
.288597 .302421 .316406 .330542 .344815
.289972 .303812 .317813 .331963 .346250
.291348 .305205 .319222 .333386 .347685
.292727 .306600 .320632 .334810 .349122
.294106 .307996 .322043 .336235 .350561
.40 .41 .42 .43 .44
.352000 .366458 .381024 .395686 .410432
.353441 .367910 .382486 .397157 .411911
.354882 .369363 .383949 .398629 .413390
.356325 .370817 .385413 .400102 .414870
.357769 .372272 .386878 .401575 .416351
.359215 .373728 .3-88344 .403049 .417833
.360661 .375185 .389810 .404524 .419315
.362109 .376644 .391278 .406000 .420798
.363557 .378103 .392746 .407477 .422281
.365007 .379563 .394216 .408954 .423765
.45 .46 .47 .48 .49
.425250 .440128 .455054 .470016 .485002
.426735 .441619 .456549 .471514 .486501
.428221 .443110 .458044 .473012 .488001
.429708 .444601 .459539 .474510 .489501
.431195 .446093 .461035 .476008 .491000
.432682 .447586 .462531 .477507 .492500
.434170 .449079 .464028 .479005 .494000
.435659 .450572 .465524 .480504 .495500
.437148 .452066 .467021 .482003 .497000
.438638 .453560 .468519 .483503 .498500
.50 .51 .52 .53 .54
.500000 .514998 .529984 .544946 .559872
.501500 .516497 .531481 .546440 .561362
.503000 .517997 .532979 .547934 .562852
.504500 .519496 .534476 .549428 .564341
.506000 .520995 .535972 .550921 .565830
.507500 .522493 .537469 .552414 .567318
.509000 .523992 .538965 .553907 .568805
.510499 .525490 .540461 .555399 .570292
.511999 .526988 .541956 .556890 .571779
.513499 .528486 .543451 .558381 .573265
.55 .56 .57 .58 .59
.574750 .589568 .604314 .618976 .633542
.576235 .591046 .605784 .620437 .634993
.577719 .592523 .607254 .621897 .636443
.579202 .594000 .608722 .623356 .637891
.580685 .595476 .610190 .624815 .639339
.582167 .596951 .611656 .626272 .640785
.583649 .598425 .613122 .627728 .642231
.585130 .599898 .614587 .629183 .643675
.586610 .601371 .616051 .630637 .645118
.588089 .602843 .617514 .632090 .646559
424 PARTIAL VOLUMES IN ELLIPSOIDAL HEADS AND SPHERES: COEFFICIENTS (Cont.) 1 3 4 5 6 7 HID 0 2 8 9
.60 .61 .62 .63 .64
.648000 .662338 .676544 .690606 .704512
.649439 .663765 .677957 .692004 .705894
.650878 .665190 .679368 .693400 .707273
.652315 .666614 .680778 .694795 .708652
.653750 .668037 .682187 .696188 .710028
.655185 .669458 .683594 .697579 .711403
.656618 .670878 .684999 .698969 .712776
.658050 .672297 .686403 .700357 .714147
.659481 .673714 .687806 .701744 .715516
.660910 .675130 .689207 .703129 .716884
.65 .66 .67 .68 .69
.718250 .731808 .745174 .758336 .771282
.719614 .733153 .746500 .759641 .772563
.720976 .734497 .747823 .760943 .773843
.722337 .735839 .749145 .762243 .775121
.723695 .737178 .750464 .763541 .776396
.725052 .738516 .751781 .764837 .777669
.726407 .739851 .753096 .766130 .778940
.727760 .741185 .754410 .767422 .780208
.719111 .742517 .755720 .768711 .781474
.730461 .743846 .757029 .769997 .782739
.70 .71 .72 .73 .74
.784000 .796478 .808704 .820666 .832352
.785359 .797712 .809912 .821847 .833505
.786515 .798944 .811118 .823026 .834655
.787769 .800173 .812321 .824201 .835802
.789021 .801399 .813521 .825374 .836946
.790270 .802623 .814719 .826544 .838088
.791516 .803845 .815914 .827711 .839226
.792761 .805063 .817106 .828876 .840362
.794002 .806280 .818295 .830037 .841494
.795241 .807493 .819482 .831196 .842624
.75 .76 .77 .78 .79
.843750 .854848 .865634 .876096 .886222
.844873 .855941 .866695 .877124 .887216
.845994 .857031 .867753 .878148 .888206
.847111 .858117 .868807 .879170 .889192
.848226 .859201 .869858 .880187 .890176
.849337 .860281 .870906 .881202 .891155
.850446 .861358 .871951 .882213 .892131
.851551 .862432 .872992 .883220 .893104
.852653 .863502 .874030 .884224 .894073
.853752 .864570 .875065 .885225 .895038
.80 .81 .82 .83 .84
.896000 .905418 .914464 .923126 .931392
.896958 .906340 .915348 .923971 .932196
.897913 .907257 .916228 .924811 .932997
.898864 .908171 .917103 .925648 .933793
.899811 .909082 .917976 .926481 .934585
.900755 .909988 .918844 .927309 .935373
.901695 .910891 .919708 .928134 .936157
.902631 .911790 .920568 .928954 .936936
.903564 .912685 .921425 .929771 .937712
.904493 .913576 .922277 .930584 .938483
.85 .86 .87 .88 .89
.939250 .946688 .953694 .960256 .966362
.940013 .947408 .954370 .960887 .966947
.940772 .948124 .955042 .961514 .967527
.941526 .948836 .955710 .962136 .968103
.942276 .949543 .956373 .962754 .968674
.943022 .950246 .957031 .963367 .969240
.943764 .950944 .957685 .963975 .969802
.944501 .951638 .958335 .964579 .970358
.945235 .952328 .958980 .965178 .970910
.945963 .953013 .959620 .965772 .971458
.90 .91 .92 .93 .94
.972000 .977158 .981824 .985986 .989632
.972538 .977647 .982263 .986374 .989968
.973070 .978131 .982697 .986757 .990298
.973598 .978610 .983126 .987135 .990623
.974121 .979084 .983550 .987507 .990943
.974640 .979553 .983969 .987874 .991258
.975153 .980017 .984382 .988236 .991567
.975662 .980477 .984791 .988593 .991871
.976165 .980931 .985194 .988945 .992169
.976664 .981380 .985593 .989291 .992462
.95 .96 .97 .98 .99
.992750 .995328 .997354 .998816 .999702
.993032 .995556 .997526 .998931 .999758
.993309 .995778 .997692 .999040 .999809
.993581 .995994 .997852 .999143 .999854
.993847 .996205 .998007 .999240 .999892
.994107 .996411 .998156 .999332 .999925
.994362 .996611 .998300 .999417 .999952
.994612 .996805 .998437 .999497 .999973
.994856 .996994 .998569 .999571 .999988
.995095 .997177 .998696 .999640 .999997
1.00 1.000000
425
AREA OF SURFACES (In Square Feet)
* The area of straight flanges is not included in the figures of the table. Outside Diameter of Vessel o inches
12 14 16 18 20
22 24 26 28 30 32 34 36 38 40 42 48 54 60 66 72 78 84 90 96 102 108 114 120 126 132 138 144
Cylindrical Shell per Lineal Foot ( 7r X D)
2: I Ellipsoidal Head* (1.09 x 0 2)
3.14 3.66 4.19
1.09 1.48 1.94 2.45 3.02 3.66 4.36 5.12 5.92 6.81 7.76 8.75 9.82 10.93 12.11 13.35 17.47 22.09 27.30 33.10 39.20 46.00 53.40 61.20 69.80 78.80 88.25 98.25 109.00 120.11 132.00 144.00 157.00
4.71 5.23 5.76 6.28 6.81 7.32 7.85 8.37 8.90 9.43 9.94 10.47 11.00 12.57 14.14 15.71 17.28 18.85 20.42 21.99 23.56 25.20 26.70 28.27 29.85 31.50 32.99 34.56 36.20 37.70
ASME¥ HemisFlat Flanged and pherical Head* Dished Head Head* (0.918 x 0 2) (1.5708 x 0 2) (0.7854 x 0 2)
0.92 1.25 1.64 2.07 2.56 3.10 3.68 4.32 5.00 5.76 6.53 7.39 8.29 9.21 10.20 11.25 14.70 18.60 23.60 27.80 33.00 38.85 45.00 51.60 58.90 66.25 74.35 83.00 92.00 100.85 111.50 121.50 132.20
1.57 2.14 2.79 3.53 4.36 5.28 6.28 7.08 8.55 9.82 11.17 12.11 14.14 15.75 17.44 19.23 25.13 31.81 39.27 47.52 56.55 66.37 76.97 88.37 100.54 113.43 127.25 141.78 157.08 173.20 190.09 207.76 226.22
0.79 1.07 1.40 1.77 2.18 2.64 3.14 3.69 4.28 4.91 5.58 6.31 7.07 7.88 8.72 9.62 12.57 15.90 19.64 23.76 28.27 33.18 38.49 44.16 50.27 56.25 63.62 70.88 78.87 86.59 95.03 102.00 113.50
426
DECIMALS OF AN INCH WITH MILLIMETER EQUIVALENTS Decimal
!U ~6 ~
VB ~ ~6 ~ ~
.03125 .0625 .09375 .125 .15625 .1875 .21875 .25
MiIIimeter
.794 1.587 2.381 3.175 3.969 4.762 5.556 6.350
Decimal
~
%'6
l~
VB l~
h6
1~
Y2
.28125 .3125 .34375 .375 .40625 .4375 .46875 .5
MiIIimeter
7.144 7.937 8.731 9.525 10.319 11.113 11.906 12.700
IJ.i2 ~
l~
% %
l~
23~ 3/ /4
Decimal
Mill imeter
.53125 .5625 .59375 .625
13.494 14.287 15.081 15.875
.65625 .6875 .71875 .75
Decimal
Millimeter
.78125 .8125 .84375 .875
19.844 20.637 21.431 22.225
.90625 .9375 .96875 1.
23.019 23.812 24.606 25.400
25~ l~
27Al Ys
29~
16.669 17.462 18.256 19.050
15,,{6 3~
1
DECIMALS OF A FOOT INCHES 8
9
10
11
.5833 .5885 .5937 .5989
.6667 .6719 .6771 .6823
.7500 .7552 .7604 .7656
.8333 .8385 .8437 .8489
.9167 .9219 .9271 .9323
.5208 .5260 .5313 .5365
.6041 .6093 .6146 .6198
.6875 .6927 .6980 .7032
.7708 .7760 .7813 .7865
.8541 .8593 .8646 .8698
.9375 .9427 .9480 .9532
.4584 .4636 ".4688 .4740
.5417 .5469 .5521 .5573
.6250 .6302 .6354 .6406
.7084 .7136 .7188 .7240
.7917 .7969 .8021 .8073
.8750 .8802 .8854 .8906
.9584 .9336 .9f)88 .9740
.4792 .4844 .4896 .4948
.5625 .5677 .5729 .5781
.6458 .6510 .6562 .6614
.7292 .7344 .7396 .7448
.8125 .8177 .8229 .8281
.8958 .9010 .9062 .9114
.9792 .9844 .9896 .9948
In.
0
1
2
0
.0000 .0052 .0104 .0156
.0833 .0885 .0937 .0989
.1667 .1719 .1771 .1823
.2500 .2552 .2604 .2656
.3333 .3385 .3437 .3489
.4167 .4219 .4271 .4323
.5000 .5052 .5104 .5156
~ ~6 ~
.0208 .0260 .0313 .0365
.1041 .1093 .1146 .1198
.1875 .1927 .1980 .2032
.2708 .2760 .2813 .2865
.3541 .3593 .3646 .3698
.4375 .4427 .4480 4532
Y2
.0417 .0469 .0521 .0573
.1250 .1302 .1354 .1406
.2084 .2136 .2188 .2240
.2917 .2969 .3021 .3073
.3750 .3802 .3854 .3906
.0625 .0677 .0729 .0781
.1458 .1510 .156:! .1614
.2292 .2344 .2396 .2448
.3125 .3177 .3229 .3281
.3958 .4010 .4062 .4114
~6
VB
~6
Us %1 %
1~6
%
1~6
%
l~fI
3
4
5
6
7
427
METRIC SYSTEM OF MEASUREMENT This system has the advantage that it is a coherent system. Each quantity has only one unit and all base units are related to each other. The fractions and mUltiples of the units are made in the decimal system.
UNITS OF METRIC MEASURES unit meter meter2 meter) gram second degree Celsius
Length Area Volume Weight Imassl Time Temperature
symbol m m2 m3 g
s °C
equivalent of 39.37 in 1.196 sq.yard 1.310 cu.yard 0.035 oz second DoC = 32°F 100°C = + 212°F
MULTIPLES AND FRACfIONS OF UNITS Symbol
Unit Multiplied by
Prefix mikro milli centi deci deka hekto kilo mega
~
m c d D h k M
Name
10-6
millionth
10-) 10- 2 10- 1 10 102 103 106
thousendth hundredth tenth ten hundred thousand million
EXAMPLE: Unit of weight is gram; 1000 gram is one kilogram, 1 kg
en ~
....JEo-<
1 ,OOOm = 1 kilometer, km
~Z ~::J ::J~
::Eo
MEASURES OF LENGTH UNIT: METER, m
en Z
9t: bz
~ ~o_ ~
*1 decimeter, dm = O.lm 1 centimeter, cm = 0.01 m 1 millimeter, mm = 0.001 m
*not used in practice
428
METRIC SYSTEM OF MEASUREMENT 1,000,ooom2 = 1 sq. kilometer, km2 10,000 m2 = 1 sq. hectare, ha 100 m2 = 1 sq. are, a *
r:a
......lE-< Q..-
Z ;:J 6 ;:J
:E
~
0
MEASURES OF AREA UNIT: SQUARE METER, m2 CI)
Z
9E-< t: Z
~
;:J
*1 sq. decimeter, dm 2 = 0.01m2 1 sq. centimeter, cm 2 = 0.0001m2 1 sq. millimeter, mm 2 = 0.000,00Im2
~
0
*not used in practice CI)
r..tJ
not used in practice
E-< ~Z tl ;:J ;:J
:E
~
0
MEASURES OF VOLUME UNIT: CUBIC METER, m 3 CI)
Z 0 E-<
1= Z
U ;:J ~
g: 0
~
1 hectoliter, hI = 1 liter, -I = 1 cu. centimeter = 1 cu. millimeter =
0.lm 3 0.001m3 0.000,00Im 3 0.OOO,000,00Im3 CI)
1,000,000 100,000 1,000 10
g= g= g= g=
1 ton, t 1 quintal, q 1 kilogram, kg I dekagram, dg
MEASURES OF WEIGHT UNIT: GRAM, g CI)
Z 0
- t: E-< u Z
;:J
~~
centigram, cg = 0.01 g milligram, mg = 0.001 g
r..tJ ......l Q..
t:
:E
0
z ;:J 6 ;:J ~
429
METRIC SYSTEM OF MEASUREMENT
km 1 1 1 1 1 1 1
km m dm* em mm J-L mJ-L
1 10-3
lOA 10-5 10-6 10-9 10- 12
m
MEASURES OF LENGTH em mm dm
103 1 10- 1 10- 2 10-3 10-6 10-9
104 10 1 10- 1 10- 2 10-5 10-8
106 103 102 10 1 10-3 10-6
105 102 10 1 10- 1
lOA 10-7
J-L
mJ-L
109 106 105 104 103 1 10-3
10 12 109 108 107 106 103 1
MEASURES OF AREA 1 1 1 1 1 1 1
km 2 ha a
m2 dm2 cm2 mm2
km 2
ha
a
m2
dm 2
cm2
mm 2
1 10- 2
lOA
102 1 10- 2
10-6 10-8 10-10 10- 12
lOA
104 102 1 10- 2
10-6 10- 8 10-10
lOA
106 104 102 1 10- 2
10-6 10- 8
lOA
108 106 104 102 1 10- 2
10-6
lOA
1010 108 106 104 102 1 10- 2
10 12 1010 108 106 104 102 1
MEASURES OF VOWME m3 1 1 1 1 1 1
m
3
hI I
dm 3 em 3 mm 3
dm 3
em 3
mm 3
103
103
106
102 1 1 10- 3 10-6
10 2 1 1 10- 3 10- 6
105 103 103 1 10- 3
109 108 106 106 103 1
hI
1 10- 1 10- 3 10- 3 10-6 10-9
10 1 10- 2 10- 2 10-5 10-8
MEASURES OF WEIGHT 1 t ~ q 1 kg 1 dg 1 g 1 eg 1 mg
10- 1 10-3 10-5 10-6 lO- B 10-9
q
kg
dg
g
eg
mg
10 1 10- 2
103 10 2 1 10- 2 10-3 10-5 10-6
105 104 102 I 10- 1 10- 3
106 105 103 10 1 10- 2 10-3
108 107 105 103 102 1 10- 1
109 lOB 106 104 103 10 1
lOA 10-5 10- 7 10-B
lOA
EXAMPLE CALCULATION Weight of the water in a cylindrical vessel of 2,000 mm inside diameter and 10,000 mm length: 3.1416 x 1,0002 X 10,000 = 31,416,000,000 mm 3 31,416 liter, 1 31.416 cu. meter, m 31416 kilogram, kg (The weight of one liter of pure water at the maximum density (4°C) equals one kilogram.)
430
METRIC SYSTEM OF MEASUREMENT RECOMMENDED PRESSURE VESSEL DIAMETERS Diameter in inches
Diameter in millimeters
Diameter in inches
Diameter in millimeters
24-30 36 42-48 54-60
630 800 1,000 1,250
66-72 78-90 96-120 126-156
1,600 2,000 2,500 3,150
RECOMMENDED TANK DIAMETERS Diameters in API feet 10 15 20 25 30 35-40 45-50 60
Diameters in meters
Diameters in API feet
Diameters in meters
3.15 4.00 5.00 6.30 8.00 10.00 12.50 16.00
70-80 90-100 120 140-163 180-200 220-240 260-300
20.00 25.00 31.50 40.00 50.00 63.00 80.00
The recommended diameters are based on a geometric progression, called Renard Series (RIO) of Preferred Numbers. * Dimensions on drawings shall be expressed in millimeters. The symbol for millimeters, mm (no period) need not be shown on the drawings. However, the following note shall be shown on the darawings: ALL DIMENSIONS ARE IN MILLIMETERS. Dimensions above 5 digits in millimeters may be expressed in meters ( e.g. 110.75 m) Scales if Metric Drawings: enlarging the object, 2, 5, 10, 20 times reducing the object in proportion of 1:2.5, 1:5, 1:10, 1:20, 1:50, 1:100, 1:200, 1:500, 1:1000
* Reference:
Makin!? it with Metric. The National Board of Boiler and Pressure Vessel Inspectors.
CONVERSION TABLE - LENGTH INCHES TO MILLIMETERS (l Inch = 25.4 Millimeters)
IN.
0
1/16
1/8
3/16
1/4
5/16
3/8
7/16
1/2
9/16
5/8
11/16
3/4
13/16
7/8
15/16
0 1 1 3 4
0.0 15.4 50.8 76.1 101.6
1.6 27.0 52.4 77.8 103.1
3.2 28.6 54.0 79.4 104.8
4.8 30.2 55.6 81.0 106.4
6.4 31.8 57.2 82.6 108.0
7.9 33.3 58.7 84.1 109.5
9.5 34.9 60.3 85.7 111.1
11.1 36.5 61.9 87.3 112.7
12.7 38.1 63.5 88.9 114.3
14.3 39.7 65.1 90.5 115.9
15.9 41.3 66.7 92.1 117.5
17.5 42.9 68.3 93.7 119.1
19.1 44.5 69.9 95.3 120.7
20.6 46.0 71.4 96.8 122.2
22.2 47.6 73.0 98.4 123.8
23.8 49.2 74.6 100.0 125.4
5 6 7 8 9
127.0 152.4 177.8 203.2 128.6
128.6 154.0 179.4 204.8 230.2
130.2 155.6 181.0 206.4 231.8
131.8 157.2 182.6 208.0 233.4
133.4 158.8 184.2 209.6 235.0
134.9 160.3 185.7 211.1 236.5
136.5 161.9 187.3 212.7 238.1
138.1 163.5 188.9 214.3 239.7
139.7 165.1 190.5 215.9 241.3
141.3 166.7 192.1 217.5 242.9
142.9 168.3 193.7 219.1 244.5
144.5 169.9 195.3 220.7 246.1
146.1 171.5 196.9 221.3 247.7
147.6 173.0 198.4 223.8 249.2
149.2 174.6 200.0 225.4 250.8
150.8 176.2 201.6 227.0 252.4
10 11 12 13 14
154.0 279.4 304.8 330.2 355.6
255.6 281.0 306.4 331.8 357.2
257.2 282.6 308.0 333.4 358.8
258.8 284.2 309.6 335.0 360.4
260.4 285.8 311.2 336.6 362.0
261.9 287.3 312.7 338.1 363.5
263.5 288.9 314.3 339.7 365.1
265.1 290.5 315.9 341.3 366.7
266.7 292.1 317.5 342.9 368.3
268.3 293.7 319.1 344.5 369.9
269.9 295.3 320.7 346.1 371.5
271.5 296.9 322.3 347.7 373.1
273.1 298.5 323.9 349.3 374.7
274.6 300.0 325.4 350.8 376.2
276.2 301.6 327.0 352.4 377.8
277.8 303.2 328.6 354.0 379.4
15 '16 17 18 19
381.0 406.4 431.8 451.2 482.6
382.6 408.0 433.4 458.8 484.2
384.2 409.6 435.0 460.4 485.8
385.8 411.2 436.6 462.0 487.4
387.4 412.8 438.2 463.6 489.0
388.9 414.3 439.7 465.1 490.5
390.5 415.9 441.3 466.7 492.1
392.1 417.5 442.9 468.3 493.7
393.7 419.1 444.5 469.9 495.3
395.3 420.7 446.1 471.5 496.9
396.9 422.3 447.7 473.1 498.5
398.5 423.9 449.3 474.7 500.1
400.1 425.5 450.9 476.3 501.7
401.6 427.0 452.4 477.8 503.2
403.2 428.6 454.0 479.4 504.8
404.8 430.2 455.6 481.0 506.4
20 21
508.0 533.4 558.8 584.2 609.6
509.6 535.0 560.4 585.8 611.1
511.2 536.6 562.0 587.4 612.8
512.8 538.2 563.6 589.0 614.4
514.4 539.8 565.2 590.6 616.0
515.9 541.3 566.7 592.1 617.5
517.5 542.9 568.3 593.7 619.1
519.1 544.5 569.9 595.3 620.7
520.7 546.1 571.5 596.9 622.3
522.3 547.7 573.1 598.5 623.9
523.9 549.3 574.7 600.1 625.5
525.5 550.9 576.3 601.7 627.1
527.1 552.5 577.'1 603.3 628.7
528.6 554.0 579.4 604.8 630.2
530.2 555.6 581.0 606.4 631.8
531.8 557.2 582.6 608.0 633.4
12
23 24
~
w .....
MEASURES
~
W tv
INCHES TO MILLIMETERS (con't.)
IN.
0
1/16
1/8
3/16
1/4
5/16
3/8
7/16
1/2
9/16
5/8
11/16
3/4
13/16
7/8
15/16
25 26 27 28 29
635.0 660.4 685.8 711.2 736.6
636.6 662.0 687.4 712.8 738.2
638.2 663.6 689.0 714.4 739.8
639.8 665.2 690.6 716.0 714.4
641.4 666.8 692.2 717.6 743.0
642.9 668.3 693.7 719.1 744.5
644.5 669.9 695.3 720.7 746.1
646.1 671.5 696.9 722.3 747.7
647.7 673.1 698.5 723.9 749.3
649.3 674.7 700.1 725.5 750.9
650.9 676.3 701.7 727.1 752.5
652.5 677.9 703.3 728.7 754.1
654.1 679.5 704.9 730.3 755.7
655.6 681.0 706.4 731.8 757.2
657.2 682.6 708.0 733.4 758.8
658.8 684.2 709.6 735.0 760.4
30 31 32 33 34
762.0 787.4 812.8 838.2 863.6
763.6 789.0 814.4 839.8 865.2
765.2 790.6 816.0 841.4 866.8
766.8 792.2 817.6 843.0 868.4
768.4 793.8 819.2 844.6 870.0
769.9 795.3 820.7 846.1 871.5
771.5 796.9 822.3 847.7 873.1
773.1 798.5 823.9 849.3 874.7
774.7 800.1 825.5 850.9 876.3
776.3 801.7 827.1 852.5 877.9
777.9 803.3 828.7 854.1 879.5
779.5 804.9 830.3 855.7 881.1
781.1 806.5 831.9 857.3 882.7
782.6 808.0 833.4 858.8 884.2
784.2 809.6 835.0 860.4 885.8
785.8 811.2 836.6 862.0 887.4
35 36 37 38 39
889.0 914.4 939.8 965.2 990.6
890.6 916.0 941.4 966.8 992.2
892.2 917.6 943.0 968.4 993.8
893.8 919.2 944.6 970.0 995.4
895.4 920.8 946.2 971.6 997.0
896.9 922.3 947.7 973.1 998.5
898.5 923.9 949.3 974.7 1000.1
900.1 925.5 950.9 976.3 1001.7
901.7 927.1 952.5 977.9 1003.3
903.3 928.7 954.1 979.5 1004.9
904.9 930.3 955.7 981.1 100&.5
906.5 931.9 957.3 982.7 1008.1
"908.1 933.5 958.9 984.3 1009.7
909.6 935.0 %0.4 985.8 1011.2
911.2 936.6 962.0 987.4 1012.8
912.8 938.2 963.6 989.0 1014.4
40
41 42 43 44
1016.0 1041.4 1066.8 1092.2 1117.6
1017.6 1043.0 1068.4 1093.8 1119.2
1019.2 1044.6 1070.0 1095.4 1120.8
1020.8 1046.2 1071.6 1097.0 1122.4
1022.4 1047.8 1073.2 1098.6 1124.0
1023.9 1049.2 1074.7 1100.1 1125.5
1025.5 1050.9 1l01.7 1127.1
1027.1 1052.5 1077.9 1103.3 1128.7
1028.7 1054.1 1079.5 1104.9 Il30.3
1030.3 1055.7 1081.1 1106.5 Il31.9
1031.9 1057.3 1082.7 1108.1 1133.5
1033.5 1058.9 1084.3 1l09.7 1135.1
1035.1 1060.5 1085.9 1111.3 1136.7
1036.6 1062.0 1087.4 IIl2.8 1138.2
1038.2 1063.6 1089.0 1114.4 1139.8
1039.8 1065.2 1090.6 1116.0 1141.4
45 46 47 48 49
1143.0 1161>.4 1193.8 1219.2 1244.6
1144.6 1170.0 1195.4 1220.8 1246.2
1146.2 Il71.6 1197.0 1222.4 1247.8
1147.8 1173.2 1198.6 1224.0 1249.4
1149.4 Il74.8 1200.2 1225.6 1251.0
1150.9 1176.3 1201.7 1227.1 1252.5
1152.5 1177.9 1203.3 1228.7 1254.1
1154.1 1179.5 1204.9 1230.3 1255.7
1155.7 1181.1 1206.5 1231.9 1257.3
1157.3 1182.7 1208.1 1233.5 1258.9
1158.9 Il84.3 1209.7 1235.1 1260.5
1160.5 1185.9 1211.3 1236.7 1262.1
1162.1 1187.5 1212.9 1238.3 1263.7
1163.6 1189.0 1214.4 1239.8 1265.2
1165.2 Il90.6 1216.0 1241.4 1266.8
Il66.8 1192.2 1217.6 1243.0 1268.4
50
1270.0
1271.6
1273.2
1274.8
1276.4
1277.9
1279.5
1281.1
1282.7
1284.3
1285.9
1287.5
1289.1
1290.6
1292.2
1293.8
~076.3
CONVERSION TABLE - LENGTH MILLIMETERS TO INCHES (1 Millimeter = 0.0394 Inch) Millimeters
0
1
2
3
4
5
6
7
8
9
Millimeters
0 10 20 30 40
0.00 0.39 0.79 1.18 1.57
0.039 0.43 0.83 J.22 1.61
0.079 0.47 0.87 1.26 1.65
0.118 0.51 0.91 1.30 1.69
0.157 0.55 0.94 1.34 1.73
0.197 0.59 0.98 1.38 1.77
0.236 0.63 1.02 1.42 1.81
0.276 0.67 1.06 1.46 1.85
0.315 0.71 1.10 1.50 1.89
0.354 0.75 1.14 1.54 1.93
0 10 20 30 40
50 60 70 80 90
1.97 '2.36 2.76 3.15 3.54
2.01 2.40 2.80 3.19 3.58
2.05 2.44 2.83 3.23 3.62
2.09 2.48 2.87 3.27 3.66
2.13 2.52 2.91 3.31 3.70
2.17 2.56 2.95 3.35 3.74
2.20 2.60 2.99 3.39 3.78
2.24 2.64 3.03 3.43 3.82
2.28 2.68 3.07 3.46 3.86
2.32 2.72 3.11 3.50 3.90
50 60 70 80 90
100 110 120 130 140
3.94 4.33 4.72 5.12 5.51
3.98 4.37 4.76 5.16 5.55
4.02 4.41 4.80 5.20 5.59
4.06 4.45 4.84 5.24 5.63
4.09 4.49 4.88 5.28 5.67
4.13 4.53 4.92 5.31 5.71
4.17 4.57 4.96 5.35 5.75
4.21 4.61 5.00 5.39 5.79
4.25 4.65 5.04 5.43 5.83
4.29 4.69 5.08 5.47 5.87
100 110 120 130 140
150 160 170 180 190
5.91 6.30 6.69 7.09 7.48
5.94 6.34 6.73 7.13 7.52
5.98 6.38 6.77 7.17 7.56
6.02 6.42 6.81 7.20 7.60
6.06 6.46 6.85 7.24 7.64
6.10 6.50 6.89 7.28 7.68
6.14 6.54 6.93 7.32 7.72
6.18 6.57 6.97 7.36 7.76
6.22 6.61 7.01 7.40 7.80
6.26 6.65 7.05 7.44 7.83
160 170 180 190
200 210 220 230 240
7.87 8.27 8.66 9.06 9.45
7.91 8.31 8.70 9.09 9.49
7.95 8.35 8.74 9.13 9.53
7.99 8.39 8.78 9.17 9.57
8.03 8.43 8.82 9.21 9.61
8.07 8.46 8.86 9.25 9.65
8.11 8.50 8.90 9.29 9.69
8.15 8.54 8.94 9.33 9.72
8.19 8.58 8.98 9.37 9.76
8.23 8.62 9.02 9.41 9.80
200 210 220 230 240
250 260 270 280 290
9.84 10.24 10.63 11.02 11.42
9.88 10.28 10.67 11.06 11.46
9.92 10.31 10.71 11.10 11.50
9.96 10.35 10.75 11.14 11.54
10.00 10.39 10.79 11.18 11.57
10.04 10.43 10.83 11.22 11.61
10.08 10.47 10.87 11.26 11.65
10.12 10.51 10.91 11.30 11.69
10.16 10.55 10.94 11.34 11.73
10.20 10.59 10.98 11.38 11.77
250 260 270 280 290
MEASURES
I
I
ISO
~ V.) V.)
+0W
+0-
MILLIMETERS TO INCHES (con't.)
8
9
6
11.97 12.36 12.76 13.15 13.54
12.01 12.40 12.80 13.19 13.58
12.05 12.44 12.83 13.23 13.62
12.09 12.48 12.87 13.27 13.66
12.13 12.52 12.91 13.31 13.70
12.17 12.56 12.95 13.35 13.74
300 310 320 330
13.90 14.29 14.69 15.08 15.47
13.94 14.33 14.n 15.1:2 15.51
13.98 14.37 14.76 15.16 15.55
14.02 14.41 14.80 15.20 15.59
14.06 14.45 14.84 15.24 15.63
14.09 14.49, 14.88 15.28 15.67
14.13 14.53 14.92 15.31 15.71
350 360 370 380 390
15.83 16.22 16.61 17.01 17.40
15.87 16.26 16.65 17.05 17.44
15.91 16.30 16.69 17.09 17.48
15.94 16.34 16.73 17.13 17.52
15.98 16.38 16.77 17.17 17.56
16.02 16.42 16.81 17.20 17.60
16.06 16.46 16.85 17.24 17.64
16.10 16.50 16.89 17.28 17.68
400
440
17.76 18.15 18.54 18.94 19.33
17.80 18.19 18.58 18.98 19.37
17.83 18.23 18.62 19.02 19.41
17.87 18.27 18.66 19.06 19.45
17.91 18.31 18.70 19.09 19.49
17.95 18.35 18.74 19.13 19.53
17.99 18.39 18.78 19.17 19.57
18.03 18.43 18.82 19.21 19.61
18.07 18.46 18.86 19.25 19.65
450 460 470 480 490
19.69 20.08 20.47 20.87 21.26
19.72 20.12 20.51 20.91 21.30
19.76 20.16 20.55 20.94 21.34
19.80 20.20 20.59 20.98 21.38
19.84 20.24 20.63 21.02 21.42
19.88 20.28 20.67 21.06 21.46
19.92 20.31 20.71 21.10 21.50
19.96 20.35 20.75 21.14 21.54
20.00 20.39 20.79 21.18 21.58
20.04 20.43 20.83 21.22 21.61
500 510 520 530 540
21.65 22.05 22.44 22.83 23.2-3
21.69 22.09 22.48 22.87 23.27
21.73 22.13 22.52 22.91 23.31
21.77 22.17 22.56 22.95 23.35
21.81 22.20 22.60 22.99 23.39
21.85 22.24 22.64 23.03 23.43
21.89 22.28 22.68 23.07 23.46
21.93 22.32 22.72 23.11 23.50
21.97 22.36 22.76 23.15 23.54
22.01 22.40 22.80 23.19 23.58
550 560 570 580 590
0
1
2
3
300 310 320 330 340
11.81 12.20 12.60 12.99 13.39
11.85 12.24 12.64 13.03 13.43
11.8' 12.28 12.68 13.07 13.46
11.93 12.32 12.72 13.11 13.50
350 360 370 380 390
13.78 14.17 14.57 14.96 15.35
13.82 14.21 14.61 15.00 15.39
13.86 14.25 14.65 15.04 15.43
400
440
15.75 16.14 16.54 16.93 17.32
15.79 16.18 16.57 16.97 17.36
450 460 470 480 490
17.72 18.11 18.50 18.90 19.29
500 510 520 530 540 550 560 570 580 590
410 420 430
7
5
Millimeters
4
Millimeters
340
410 420 430
MILLIMETERS TO INCHES (con't.)
Millimeters
0
1
2
3
4
5
6
7
8
9
Millimeters
600
640
23.62 24.02 24.41 24.80 25.20
23.66 24.06 24.45 24.84 25.24
23.70 24.09 24.49 24.88 25.28
23.74 24.13 24.53 24.92 25.31
23.78 24.17 24.57 24.96 25.35
23.82 24.21 24.61 25.00 25.39
23.86 24.25 24.65 25.04 25.43
23.90 24.29 24.68 25.08 25.47
23.94 24.33 24.72 25.12 25.51
23.98 24.37 24.76 25.16 25.55
610 620 630 640
650 660 670 680 690
25.59 25.98 26.38 26.77 27.17
25.63 26.02 26.42 26.81 27.20
25.67 26.06 26.46 26.85 27.24
25.71 26.10 26.50 26.89 27.28
25.75 26.14 26.54 26.93 27.32
25.79 26.18 26.57 26.97 27.36
25.83 26.22 26.61 27.01 27.40
25.87 26.26 26.65 27.05 27.44
25.91 26.30 26.69 27.09 27.48
25.94 26.34 26.73 27.13 27.52
650 660 670 680 690
700 710 720 730 740
27.56 27.95 28.35 28.74 29.13
27.60 27.99 28.39 28.78 29.17
27.64 28.03 28.43 28.82 29.21
27.68 28.07 28.46 28.86 29.25
27.72 28.11 28.50 28.90 29.29
27.76 28.15 28.54 28.94 29.33
27.80 28.19 28.58 28.98 29.37
27.83 28.23 28.62 29.02 29.41
27.87 28.27 28.66 29.06 29.45
27.91 28.31 28.70 29.09 29.49
700 710 720 730 740
750 760 770 780 790
29.53 29.92 30.31 30.71 31.10
29.57 29.96 30.35 30.75 31.14
29.61 30.00 30.39 30.79 31.18
29.65 30.04 30.43 30.83 31.22
29.68 30.08 30.47 30.87 31.26
29.72 30.12 30.51 30.91 31.30
29.76 30.16 30.55 30.94 31.34
29.80 30.20 30.59 30.98 31.38
29.84 30.24 30.63 31.02 31.42
29.88 30.28 30.67 31.06 31.46
750 760 770 780 790
800
810 820 830 840
31.50 31.89 32.28 32.68 33.07
31.54 31.93 32.32 32.72 33.11
31.57 31.97 32.36 32.76 33.15
31.61 32.01 32.40 32.80 33.19
31.65 32.05 32.44 32.83 33.23
31.69 32.09 32.48 32.87 33.27
31.73 32.13 32.52 32.91 33.31
31.77 32.17 32.56 32.95 33.35
31.81 32.20 32.60 32.99 33.39
31.85 32.24 32.64 33.03 33.43
800 810 820 830
850 860 870 880 890
33.46 33.86 34.25 34.65 35.04
33.50 33.90 34.29 34.68 35.08
33.54 33.94 34.33 34.72 35.12
33.58 33.98 34.37 34.76 35.16
33.62 34.02 34.41 34.80 35.20
33.66 34.06 34.45 34.84 35.24
33.70 34.09 34.49 34.88 35.28
33.74 34.13 34.53 34.92 35.31
33.78 34.17 34.57 34.96 35.35
33.82 34.21 34.61 35.00 35.39
850 860 870 880 890
600
610 620 630
840
~ ~
Vl
MEASURES
+:0W 0'1
MILLIMETERS TO INCHES (con't.)
Millimeters
0
1
2
3
4
S
6
7
8
9
Millimeters
35.43 35.83 36.22 36.61 37.01
35.47 35.87 36.26 36.65 37.05
35.51 35.91 36.30 36.69 37.09
35.55 35.94 36.34 36.73 37.13
35.59 35.98 36.38 36.77 37.17
35.63 36.02 36.42 36.81 37.20
35.67 36.06 36.46 36.85 37.24
35.71 36.10 36.50 36.89 37.28
35.75 36.14 36.54 36.93 37.32
35.79 36.18 36.57 36.97 37.36
910 920 930
980 990
37.40 37.80 38.19 38.58 38.98
37.44 37.83 38.23 38.62 39.02
37.48 37.87 38.27 38.66 39.06
37.52 37.91 38.31 38.70 39.09
37.56 37.95 38.35 38.74 39.13
37.60 37.99 38.39 38.78 39.17
37.64 38.03 38.43 38.82 39.21
37.68 38.07 38.46 38.86 39.25
37.72 38.11 38.50 38.90 39.29
37.76 38.15 38.54 38.94 39.33
950 960 970 980 990
1000
39.37
39.41
39.45
39.49
39.53
39.57
39.61
39.65
39.68
39.72
1000
900
910 920 930 940
950 960
970
------
-----
900
940
SQUARE FEET TO SQUARE METERS Square Feet 0 10 20 30 40 50 60 70 80 90
0 0.000 0.929 1.858 2.787 3.716 4.645 5.574 6.503 7.432 8.361
1 0.093 1.022 1.951 2.880 3.809 4.738 5.667 6.596 7.525 8.454
3
2
4
0.279 1.208 2.137 3.066 3.995 4.924 5.853 6.782 7.711 8.640
0.186 1.115 2.044 2.973 3.902 4.831 5.760 6.689 7.618 8.547
0.372 1.301 2.230 3.159 4.088 5.017 5.946 6.875 7.804 8.733
5
0.465 1.394 2.323 3.252 4.181 5.110 6.039 6.968 7.897 8.826
6 0.557 1.486 2.415 3.345 4.274 5.203 6.132 7.061 7.990 8.919
=
1 Sq. Ft.
7
8
0.650 1.579 2.508 3.437 4.366 5.295 6.225 7.154 8.083 9.012
0.743 1.672 2.601 3.530 4.459 5.388 6.317 7.246 8.175 9.105
0.0929034 Square Meters 9 0.836 1.765 2.694 3.623 4.552 5.481 6.410 7.339 8.268 9.197
I
SQUAR~
METERS TO SQUARE FEET
1 Sq. M
=
10.76387 Square Feet I
Square Meters 0 10 20 30 40 50 60 70 80 90
0
1
0.00 107.64 215.28 322.92 430.56 538.19 645.83 753.47 861.11 968.75
10.76 118.40 226.04 333.68 441.32 548.96 656.60 764.23 871.87 979.51
2
21.53 129.17 236.81 344.44 452.08 559.72 667.36 . 775.00 882.64 990.28
3 32.29 139.93 247.57 355.21 462.85 570.49 678.12 785.76 893.40 1001.04
4 43.06 150.69 258.33 365.97 473.61 581.25 688.89 796.53 904.17 1011.80
5
53.82 161.46 269.10 376.74 484.37 592.01 699.65 807.29 914.93 1022.57
MEASURES
6
7
8
9
64.58 172.22 279.86 387.50 495.14 602.7R 710.42 818.05 925.69 1033.33
75.35 182.99 290.62 398.26 505.90 613.54 721.18 828.82 936.46 1044.10
86.11 193.75 301.39 409.03 516.67 624.30 731.94 839.58 947.22 1054.86
96.87 204.51 312.15 419.79 527.43 635.07 742.71 850.35 957.98 1065.62
I
~
Vl -..l
oj::.
W 00
CONVERSION TABLE - WEIGHTS
POUNDS TO KILOGRAMS (1 pound = 0.4536 kilogram) Pounds
0
0 10 20 30 40 50 60 70 80 90
0.00 4.54 9.07 13.61 18.14 22.68 27.22 31.75 36.29 40.82
1 0.45 4.99 9.53 14.06 18.60 23.13 27.67 32.21 36.74 41.28
2
3
0.91 5.44 9.98 14.52 19.05 23.59 28.12 32.66 37.20 41.73
1.36 5.90 10.43 14.97 19.50 24,04 28.58 33.11 37.65 42.18
5
4 1.81 6.35 10.89 15.42 19.96 24.49 29.03 33.57 38.10 42.64
2.27 6.80 11.34 15.88 20.41 24.95 29.48 34.02 38.56 43.09
6
8
7
2.72 7.26 11.79 16.33 20.87 25.40 29.94 34.47 39.01 43.55
9
3.18 7.71 12.25 16.78 21.32 25.86 30.39 34.93 39.46 44.00
3.63 8.16 12.70 17.24 21.77 26.31 30.84 35.38 39.92 44.45
4.08 8.62 13.15 17.69 12.23 26.76 31.30 35.83 40.37 44.91
KILOGRAMS TO POUNDS (1 kilogram = 2.2046 pounds) Kilograms 0 10 20 30 40 50 60 70 80 90
0
1
2
3
4
5
6
7
8
9
0.00 22.05 44.09 66.14 88.18 110.23 132.28 154.32 176.37 198.41
2.20 24.25 46.30 68.34 90.39 112.43 134.48 156.53 178.57 200.62
4.41 26.46 48.50 70.55 92.59 114.64 136.69 158.73 180.78 202.82
6.61 28.66 50.71 72.75 94.80 116.84 138.89 160.94 182.98 205.03
8.82 30.86 52.91 74.96 97.00 119.05 141.09 163.14 185.19 207.23
11.02 33.07 55.12 77.16 99.21 121.25 143.30 165.35 187.39 209.44
13.23 35.27 57.32 79.37 101.41 123.46 145.50 167.55 189.60 211.64
15.43 37.48 59.52 81.57 103.62 125.66 147.71 169.75 191.80 213.85
17.64 39.68 61.73 83.77 105.82 127.87 149.91 171.96 194.00 216.05
19.84 41.89 63.93 85.98 108.03 130.07 152.12 174.16 196.21 218.26
--
--
-
L - ..
-----
--
-
-
'--------
~
----
---
-
--
-
'-
-
I
U. S. GALLONS TO LITERS Gallon 0 10 20 30 40 50 60 70 80 90
1
u. S. Gallon
= 3.785329 Liter
0
1
2
3
4
5
6
7
8
9
0 37.85 75.71 113.56 151.41 189.27 227.12 264.97 302.83 340.68
3.79 41.64 79.49 117.35 155.20 193.05 230.91 268.76 306.61 344.46
7.57 45.42 13.28 121.13 158.98 196.84 234.69 272.54 310.40 348.25
11.36 49.21 87.01 124.92 162.77 200.62 238.48 276.33 314.18 352.04
15.14 52.99 90.85 128.70 166.55 204.41 242.26 280.11 317.97 355.82
18.93 56.78 94.63 132.49 170.34 208.19 246.05 283.90 321.75 359.60
22.71 60.57 98.42 136.27 174.13 211.98 249.83 287.69 325.54 363.39
26.50 64.35 102.20 140.06 177.91 215.76 253.62 291.47 329.32 367.18
30.28 68.14 105.99 143.84 181.70 219.55 257.40 295.26 333.11 370.96
34.07 71.92 109.77 147.63 185.48 223.33 261.19 299.04 336.89 374.75 :
LITER TO U. S. GALLON Liter 0 10 20 30 40 50 60 70 80 90 ~
0 0 2.64 5.28 7.93 10.57 13.21 15.85 18.49 21.13 23.78
1 0.26 2.91 5.55 8.19 10.83 13.47 16.11 18.76 21.40 24.04
2 0.53 3.17 5.81 8.45 11.10 13.74 16.38 19.02 21.66 24.30
3 0.79 3.43 6.08 8.72 11.36 14.00 16.64 19.28 21.93 24.57
4 1.06 3.70 6.34 8.98 11.62 14.27 16.91 19.55 22.19 24.83
5 1.32 3.96 6.60 9.25 11.89 14.53 17.17 19.81 22.45 25.10
- -
MEASURES
1 Liter = 0.264168 U. S. Gallon 6
1.59 4.23 6.87 9.51 12.15 14.79 17.44 20.08 22.72 25.36
7 1.85 4.49 7.13 9.77 12.42 15.06 17.70 20.34 22.98 25.62
8 2.11 4.76 6.60 10.04 12.68 15.32 17.96 20.61 23.25 25.89
9 2.38 5.02 7.66 10.30 12.94 15.59 18.23 20.87 23.51 26.15
~
W \0
~ ~
CONVERSION TABLE - PRESSURE
o
POUNDS PER SQUARE INCH TO KILOGRAMS PER SQUARE CENTIMETER (1 pound per square inch = .0703066 kilogram per square centimeter)
1 to 30 Lbs. Per Kg. Per Sq. In. Sq. em.
1 2 3 4 5 6 7 8 9 10 11 12 13 14 15 16 17 18 19 20 21 22 23 24 25 26 27 28 29 30
.07 .14 .21 .28 .35 .42 .49 .56 .63 .70 .77 .84 .91 .98 1.05 1.12 1.20 1.27 T.34 1.41 1.48 1.55 1.62 1.69 1.76 1.83 1.90 1.97 2.04 2.11
31 to 60 Lbs. Per Kg. Per Sq. In. Sq. em.
31 32 33 34 35 36 37 38 39 40 41 42 43 44 45 46 47 48 49 50 51 52 53 54 55 56 57 58 59 60
2.18 2.25 2.32 2.39 2.46 2.53 2.60 2.67 2.74 2.81 2.88 2.95 3.02 3.09 3.16 3.23 3.30 3.37 3.45 3.52 3.59 3.66 3.73 3.80 3.87 3.94 4.01 4.08 4.15 4.22
61 to 90 Lbs. Per Kg. Per Sq. In. Sq. em.
61 62 63 64 65 66 67 68 69 70 71 72 73 74 75 76 77 78 79 80 81 82 83 84 85 86 87 88 89 90
4.29 4.36 4.43 4.50 4.57 4.64 4.71 4.78 4.85 4.92 4.99 5.06 5.13 5.20 5.27 5.34 5.41 5.48 5.55 5.62 5.69 5.77 5.84 5.91 5.98 6.05 6.12 6.19 6.26 6.33
91 to 200
205 to 400
Lbs. Per Sq. In.
Kg. Per Sq. em.
Lbs. Per Sq. In.
Kg. Per Sq. em.
91 92 93 94 95 96 97 98 99 100 105 110 115 120 125 130 135 140 145 150 155 160 165 170 175 180 185 190 195 200
6.40 6.47 6.54 6.61 6.68 6.75 6.82 6.89 6.96 7.03 7.38 7.73 8.09 8.44 8.79 9.14 9.49 9.84 10.19 10.55 10.90 11.25 11.60 11.95 12.30 12.66 13.01 13.36 13.71 14.06
205 210 215 220 225 230 235 240 245 250 255 260 265 270 275 280 285 290 295 300 310 320 330 340 350 360 370 380 390 400
14.41 14.76 15.12 15.47 15.82 16.17 16.52 16.87 17.23 17.58 17.93 18.28 18.63 18.98 19.33 19.69 20.04 20.39 20.74 21.09 21.80 22.50 23.20 23.90 24.61 25.31 26.01 26.72 27.42 28.12
410 to 700
710 to 1000
1010to 1500
Lbs. Per Kg. Per Sq. In. Sq. em.
Lbs. Per Kg. Per Sq. In. Sq. em.
Lbs. Per Kg. Per Sq. em. Sq. In.
410 420 430 440 450 460 470 480 490 500 510 520 530 540 550 560 570 580 590 600 610 620 630 640 650 660 670 680 690 700
28.83 29.53 30.23 30.93 31.64 32.34 33.04 33.75 34.45 35.15 35.86 36.56 37.26 37.97 38.67 39.37 40.07 40.78 41.48 42.18 42.89 43.59 44.29 45.00 45.70 46.40 47.11 47.81 48.51 49.21
710 720 730 740 750 760 770 780 790 800 810 820 830 840 850 860 870 880 890 900 910 920 930 940 950 960 970 980 990 1000
49.92 50.62 51.32 52.03 52.73 53.43 54.14 54.84 55.54 56.25 56.95 57.65 58.35 59.06 59.76 60.46 61.17 61.87 62.57 63.28 63.98 64.68 65.39 66.09 66.79 67.49 68.20 68.90 69.60 70.31
1010 1020 1030 1040 1050 1060 1070 1080 1090 1100 1120 1140 1160 1180 1200 1220 1240 1260 1280 1300 1320 1340 1360 1380 1400 1420 1440 1460 1480 1500
71.01 71.71 72.42 73.12 73.82 74.52 75.23 75.93 76.63 77.34 78.74 80.15 81.56 82.96 84.37 85.77 87.18 88.59 89.99 91.40 92.80 94.21 95.62 97.02 98.43 99.84 101.24 102.65 104.05 105.46
441
CONVERSION TABLE - DEGREE DEGREES TO RADIANS 1 DEGREE = 180 = 0.01745 RADIANS Degrees
i
Minutes
Seconds
0° 1 2 3 4
0.0000000 0.01745 H 0.03490 66 0.05235 99 0.06981 32
60° 61 62 63 64
1.0471976 1.0646508 1.0821041 1.09955 74 I.Il701 07
120° 121 122 123 124
2.09439 51 2.11184 84 2.12930 17 2.1467550 2.16420 83
0 1 2 3 4
0.0000000 0.00029 09 0.00058 18 0.0008727 0.0011636
0 1 2 3 4
0.0000000 0.0000048 0.00000 97 0.00001 45 0.00001 94
5 6 7 8 9
0.08726 0.10471 0.12217 0.13962 0.15707
65 98 30 63 96
65 66 67 68 69
1.1344640 1.1519173 1.16937 06 1:1868239 1.2042772
125 126 127 128 129
2.18166 16 2.1991149 2.21656 82 2.23402 14 2.2514747
5 6 7 8 9
0.00145 0.00174 0.00203 0.00232 0.00261
80
5 6 7 8 9
0.0000242 0.00002 91 0.00003 39 0.0000388 0.00004 36
70 71 72 73 74
1.22173 05 1.2391838 1.25663 7 I 1.27409 04 1.29154 36
130
14
0.17453 29 0.1919862 0.20943 95 0.22689 28 0.2443461
132 133 134
2.26892 80 2.28638 13 2.30383 46 2.3212879 2.3387412
10 11 12 13 14
0.0029089 0.0031998 0.00349 07 0.00378 15 0.00407 24
10 11 12 13 14
0.00004 0.00005 0.00005 0.00006 0.00006
I5 16 17 18 19
0.26179 94 0.2792527 0.29670 60 0.31415 93 0.33161 26
75 76 77 78 79
1.30899 69 1.32645 02 1.3439035 1.36135 68 1.37881 01
135 136 137 138 139
2.3561945 2.37364 78 2.39110 11 2.40855 44 2.4260077
15 16 17 18 19
0.00436 33 0.0046542 0.00494 51 0.00523 60 0.00552 69
15 16 17 18 19
0.0000727 0.00007 76 0.00008 24 0.00008 73 0.00009 21
20 21 22 23 24
0.34906 59 0.36651 91 0.38397 24 0.4014257 0.41887 90
80 81 82 83 84
1.39626 34 1.41371 67 1.4311700 1.44862 H 1.46607 66
140 141 142 143 144
2.44346 10 2.46091 42 2.47836 75 2.49582 08 2.5132741
20 21 22 23 24
0.00581 0.00610 0.00639 0.00669 0.00698
78 87 95 04 13
20 21 22 23 24
0.00009 0.00010 0.00010 0.00011 0.00011
25 26 27 28 29
0.43633 23 0.45378 56 0.4712389 0.48869 22 0.5061455
85 86 87 88 89
1.48352 99 1.5009832 1.51843 64 I. 53588 97 1.55334 30
145 146 147 148 149
2.53072 2.54818 2.56563 2.58308 2.60054
74 07 40 73 06
25 26 27 28 29
0.0072722 0.00756 31 0.00785 40 0.0081449 0.00843 58
25 26 27 28 29
0.0001212 0.00012 61 0.00013 09 0.00013 57 0.0001406
30 31 32 33 34
0.5235988 0.5410521 0.55850 54 0.5759587 0.59341 19
90 91 92 93 94
1.57079 63 1. 58824 96 1.6057029 1.62315 62 1.64060 95
150 151 152 153 154
2.61799 2.63544 2.65290 2.67035 2.68780
39 72 OJ 38 70
30 31 32 33 34
0.00872 66 0.00901 75 0.00930 84 0.00959 93 0.0098902
30 31 32 33 34
0.0001454 0.00015 03 0.00015 51 0.0001600 0.0001648
35 36 37 38 39
0.61086 52 0.62831 85 0.64577 18 0.66322 51 0.6806784
95 96 97 98 99
1.6580628 1.67551 61 1.69296 94 1.7104227 1.72787 60
155 156 157 158 159
2.70526 03 2.72271 36 2.74016 69 2.7576202 2.7750735
35 36 37 38 39
0.01018 0.01047 0.01076 0.01105 0.01134
II 20 29 38 46
35 36 37 38 39
0.0001697 0.0001745 0.0001794 0.0001842 0.00018 91
40 41 42 43 44
0.69813 17 0.71558 50 0.7330383 0.75049 16 0.76794 49
100 101 102 103 104
1.7453293 1.76278 25 1.78023 58 1.79768 91 1.81514 24
160 161 162 163 164
2.79252 2.80998 2.82743 2.84488 2.86234
68 01 34 67 00
40 41 42 43 44
0.0116355 0.0119264 0.01221 73 0.0125082 0.01279 91
40 41 42 43 44
0.00019 39 0.00019 88 0.0002036 0.00020 85 0.00021 33
45 46 47 48 49
0.78539 0.80285 0.82030 0.83775 0.85521
82 15 47 80 13
105 106 107 108 109
1.83259 1.85004 1.86750 1.88495 1.90240
57 90 23 56 89
165 166 167 168 169
2.87979 H 2.89724 66 2.9146999 2.9321531 2.9496064
45 46 47 48 49
0.01309 00 0.01338 09 0.01367 17 0.01396 26 0.0142535
45 46 47 48 49
0.00021 82 0.00022 30 0.00022 79 0.0002327 0.00023 76
50 51 52 53 54
0.8726646 0.89011 79 0.90757 12 0.92502 45 0.94247 78
IIO III 112 113 II4
1.91986 22 1.93731 55 1.9547688 1.9722221 1.9896753
170 171 172 173 174
2.96705 2.98451 3.00196 3.01941 3.03687
97 30 63 96 29
50 51 52 53 54
0.0145444 0.01483 53 0.01512 62 0.01541 71 0.01570 80
50 51 52 53 54
0.00024 24 0.00024 73 0.0002521 0.00025 70 0.00026 18
55 56 57 58 59
0.95993 II .09773844 0.99483 77 1.01229 10 1.02974 43
II5 116 II7 II8 119
2.007/2 2.02458 2.04203 2.05948 2.07694
86 19 52 85 18
175 176 177 178 179
3.05432 3.07177 3.08923 3.10668 3.12413
62 95 28 61 94
55 56 57 58 59
0.01599 89 0.01628 97 0.0165806 0.01687 15 0.0171624
55 56 57 58 59
0.00026 0.00027 0.00027 0.00028 0.00028
60
1.0471976
120
2.0943951
180
3.14159 27
60
0.01745 H
60
0.00029 09
10 II 12 13
HI
44 53 62
7I
85 33 82 30 79
70 18 67 15 64
66 15 63 12 60
442
CONVERSION TABLE - DEGREE RADIANS TO DEGREES
=
1 RADIAN Radians
1 2 3 4 5 6 7 8 9
57° 17' •• ".8 11.°35'29".6 171°51'14".4 229 ° 10' 59".2 286°28'44".0 343°46'28".8 401 ° 4'13",6 458°21'58" •• .515°39'.3",3
1:0 = 57.29578 DEGREES
Tenths
Hundredths
Thousandths
5°41'46".5 11°27'JJ".0 17°11'19".4 22°55'05".9 28 ° 38' 52 ",4 34°22'38",9 40° 6'25".4 45°50'11".8 51°33'58".3
0°3. '22".6 1 ° 8'.5",1 1°41'Q7",.9 2° 17'10".6 2°51'53".2 3°26'15",9 4° 0'38".5 4°35'01".2 5° 9'23",8
0° 3'26".3 0° 6'52".5 0°10'18".8 0°0'45".1 0° 17' II ".1 0°20'17",6 0°24'03".9 0°27'30".1 0°30"6",.
EXAMPLES 1.
Change 87 0 26' 34" to radian Solution: From table on opposite page 87 0 26' 34"
= = =
87 0 26' 34" 2.
1.5184364 0.0075631 0.0001648
radians radians radians.
1.5261643
radians
Change 1.5262 radians to degrees Solution: From table above 1 radian 0.5 0.02 0.006 0.0002 1.5262
= = = = = = =
57 0 17' 44.8" 28 0 38' 52.4" 10 8' 45.3" 0 0 20' 37.6" 0 0 0' 41.3" 86 0 83' 221.4" 87 0 26' 41.4"
Tenthousandths
0° 0'20",6 0° 0'.1 ".3 0° 1'01 ".9 0° 1'22".5 0° 1'41".1 0° 2'03".8 0° 2'24".4 OC 2'45".0 0°3'05".6
443 CONVERSION TABLE - DEGREE MINUTES AND SECONDS TO DECIMALS OF A DEGREE 0
0 1 2 3 4
5
6 7 8 9
10 11 12 13 14
15 16 17 18 19
20 21 22 23 24
25 26 27 28 29
30 31 32 33 34
35 36 37 38 39
40 41 42 43 44
45 46 47 48 49
50 51 52 53 54
55 56 57 58 59
60 ,
0.0000 0167 0333 0500 0667 0.0833 1000 1167 1333 1500 0.1667 1833 2000 2167 2333 0.2500 2667 2833 3000 3167 0.3333 3500 3667 3833 4000 0.4167 4333 4500 4667 4833 0.5000 5167 5333 5500 5667 0.5833 6000 6167 6333 6500 0.6667 6833 7000 7167 7333 0.7500 7667 7833 8000 8167 0.8333 8500 8667 8833 9000 0.9167 9333 9500 9667 9833 1.000 0
DECIMALS OF A DEGREE TO MINUTES AND SECONDS
0
"
'and"
0
0.000
60
0.00000 028 056 083 III 0.00139 167 194 222 250 0.00278 306 333 361 389 0.00417 444 472 500 528 0.00556 583 611 639 667 0.00694 722 750 778 806 0.00833 861 889 917 944 0.00972 01000 028 056 083 0.01111 139 167 194 222 0.01250 278 306 333 361 0.01389 417 444 472 500 0.01528 556 583 611 639 0.01667
"
0
0
0 1 2 3 4
5 6 7 8 9
10 11 12 13 14
15 16 17 18 19
20
21 22 23 24
25 26 27 28 29
30 31 32 33 34
35 36 37 38 39
40 41 42 43 44
45 46 47 48 49
50 51 52 53 54
55 56 57 58 59
001 002 003 004
0.005 006 007 008 009
0.00 01 02 03 04
0.05 06 07 08 09
0.10 11 12 13 14
0.15 16 17 18 19
0.20 21 _22 23 24
0.25 26 27 28 29
0.30 31 32 33 34
0.35 36 37 38 39
0.40 41 42 43 44
0.45 46 47 48 49
0.50
0' 0' 0' 0' 0' 0' 0' 0' 0' 0' 0' 0' I' I' 2' 3' 3' 4' 4' 5' 6' 6' 7' 7' 8' 9' 9' 10' 10' II' 12' 12' 13' 13' 14' IS' IS' 16' 16' 17' 18' 18' 19' 19' 20' 21' 21' 22' 22' 23' 24' 24' 25' 25' 26' 27' 27' 28' 28' 29' 30'
0" 4" 7" 11 " 14" 18" 22" 25" 29" 32" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0" 36" 12" 48" 24" 0"
• and"
0
'and ..
0.50
2.00
30' 0" 30' 36" 31' 12" 31' 48" 32' 24" 33' 0" 33' 36" 34' 12" 34' 48" 35' 24" 36' 0" 36' 36" 37' 12" 37' 48" 38' 24" 39' 0" 39' 36" 40' 12" 40' 48" 41' 24" 42' 0" 42' 36" 43' 12" 43' 48" 44' 24" 45' 0" 45' 36" 46' 12" 46' 48" 47' 24" 48' 0" 48' 36" 49' 12" 49' 48" 50' 24" 51' 0" 51' 36" 52' 12" 52' 48" 53' 24" 54' 0" 54' 36" 55' 12" 55' 48" 56' 24" 57' 0" 57' 36" 58' 12" 58' 48" 59' 24" 60' 0" 66' 0" 72' 0" 78' 0" 84' 0" 90' 0" 96' 0" 102' 0" 108' 0" 114' 0" 120' 0"
0
'and"
51 52 53 54
0.55 56 57 58 59
0.60 61 62 63 64
0.65 66 67 68 69
0.70 71 72 73 74
0.75 76 77 78 79
0.80 81 82 83 84
0.85 86 87 88 89
0.90 91 92 93 94
0.95 96 97 98 99
1.00 10 20 30 40
1.50 60 70 80 90
~ ~ ~
CONVERSION TABLE - TEMPERATURE CENTIGRADE - FAHRENHEIT 5 9 (FO + 40) -40 Degrees Cent., Co Degrees Fahr., FO (CO + 40) -40 9 NOTE: The numbers in boldface refer to the temperature either in degrees, Centigrade or Fahrenheit which it is desired to convert into the other scale. If converting from Fahrenheit to Centigrade degrees, the equivalent temperature will be found in the left column; while if converting from degrees Centigrade to degrees Fahrenheit, the answer will be found in the column on the right.
=-
Centigrade
Fahrenheit
Fahrenheit
Centigrade -15.6 -15.0
4 5
39.2 41.0
-14.4 -13.9 -13.3 -12.8 -12.2 -11.7 -11.1 -10.6
6 7 8 9 10 13
42.8 44.6 46.4 48.2 50.0 51.8 53.6 55.4
-10.0 -9.4 -8.9 -8.3 -7.8 -7.2 -6.7 -6.1
14 15 16 17 18 19 20 21
-73.3 -67.8 -62.2 -59.5 -56.7 -53.9 -51.1 -48.4
-100 -90 -80 -75 -70 -65 -60 -55
-148.0 -130.0 -112.0 -103.0 -94.0 -85.0 -76.0 -67.0
-45.6 -42.8 -40.0 -37.2 -34.4 -31.6 -28.8 -26.1
-50 -45 -40 -35 -30 -25 -20 -15
-58.0 -49.0 -40.0 -31.0 -22.0 -13.0 -4.0 5.0
-23.3 -20.6 -17.8 -17.2 -16.7 -16.1
-10 -5 0 1 2 3
14.0 23.0 32.0 33.8 35.6 37.4
-5.6 -5.0 -4.4 -3.9
11 12
22 23 24 25
="5
Fahrenheit
Centigrade
Centigrade
Fahrenheit
-3.3 -2.8 -2.2 -1.7
26 27 28 29
78.8 80.6 82.4 84.2
9.4 10.0 10.6 11.1
49 50 51 52
120.2 122.0 123.8 125.6
57.2 59.0 60.8 62.6 64.4 66.2 68.0 69.8
-1.1 -0.6 0.0 0.6 1.1 1.7 2.2 2.8 3.3 3.9 4.4 5.0 5.6 6.1 6.7
30 31 32 33 34 35 36 37 38 39 40 41 42 43 44
86.0 87.8 89.6 91.4 93.2 95.0 96.8 98.6 100.4 102.2 104.0 105.8 107.6 109.4 111.2
11.7 12.2 12.8 13.3 13.9 14.4 15.0 15.6
53 54 55 56 57 58 59 60
127.4 129.2 131.0 132.8 134.6 136.4 138.2 140.0
71.6 73.4 75.2 77.0
7.2 7.8 8.3 8.9
16.1 16.7 17.2 17.8 18.3 18.9 19.4 20.0
61 62 63 64 65 66 67 68
141.8 143.6 145.4 147.2 149.0 150.8 152.6 154.4
20.6 21.1
69 70
156.2 158.0
45 46 47 48
113.0 114.8 116.6 118.4
i
I
I
I
CENTIGRADE - FAHRENHEIT (con't.) Centigrade
Fahrenheit
Fahrenheit
Centigrade
Fahrenheit
54 60 65 71 76
130 140 150 160 170
266 284 302 320 338
226 232 238 243 249
440 450 460 470 480
824 842 860 878 896
83 88 93 99 100 104 110 115
180 190 200 210 212 220 230 240
356 374 392 410 413 428 446 464
185.0 186.8 188.6 190.4 192.2 194.0 195.8
121 127 132 138 143 149 154 160
250 260 270 280 290 300 310 320
482 500 518 536 554 572 590 608
254 260 265 271 276 282 288 293 299 304 310 315 321 326 332
490 500 510 520 530 540 550 560 570 580 590 600 610 620 630
914 932 950 968 986 1004 1022 1040 1058 1076 1094 1112 1130 1148 1166
92 93 94 95 96 97 98 99
197.6 199.4 201.2 203.0 204.8 206.6 208.4 210.2
165 171 177 182 188 193 199 204
330 340 350 360 370 380 390 400
626 644 662 680 698 716 734 752
100 110 120
212.0 230 248
210 215 221
410 420 430
770 788 806
21.7 22.2 22.8 23.3 23.9 24.4
71 72 73 74 75 76
159.8 161.6 163.4 165.2 167.0 168.8
25.0 25.6 26.1 26.7 27.2 27.8 28.3 28.9
77 78 79 80 81 82 83 84
170.6 172.4 174.2 176.0 177.8 179.6 181.4 183.2
29.4 30.0 30.6 31.1 31.7 32.2 32.8
85 86 87 88 89 90 91
33.3 33.9 34.4 35.0 35.6 36.1 36.7 37.2 37.8
:§
Centigrade
338 343 349 354 360 365 371 376
640 650 660 670 680 690 700 710
1184 1202 1220 1238 1256 1274 1292 1310
382 387 393 399 404
720 730 740 750 760
1328 1346 1364 1382 1400
MEASURES
Centigrade
Fahrenheit
410 415 421
770 780 790
1418 1436 1454
426 432 438 443 449 454 460 465
800 810 820 830 840 850 860 970
1472 1490 1508 1526 1544 1562 1580 1598
471 476 482 487 493 498 504 510
880 890 900 910 920 930 940 950
1616 1634 1652 1670 1688 1706 1724 1742
515 520 526 532 538 565 593 620
960 970 980 990 1000 1050 1100 1150
1760 1778 1796 1814 1832 1922 2012 2102
648 675 704 734 760 787 815
1200 1250 1300 1350 1400 1450 1500
2192 2282 2372 2462 2552 2642 2732
I
~ ~
VI
446
CONVERSION FACTORS (For conversion factors meeting the standards of the SI metric system, refer to ASTM E380-72) MULTIPLY BY TO OBTAIN centimeters ....................................... . 3.28083 x 10-2 feet centimeters ....................................... . inches .3937 6.102 x 10-2 cubic centimeters .............................. . cubic inches cubic feet .......................................... . 2.8317 x 10-2 cubic meters cubic feet .......................................... . 6.22905 gallons, British Imperial cubic feet ......................................... .. liters 28.3170 cubic inches ..................................... .. 16.38716 cubic centimeters cubic meters .................................... .. 35.3145 cubic feet cubic meters .................................... .. 1.30794 cubic yards cubic yards ....................................... .. .764559 cubic meters degrees angular ................................ . .0174533 radians foot pounds ...................................... .. .13826 kilogram meters feet ..................................................... centimeters 30.4801 .160538 gallons, British Imperial .................... . cubic feet gallons, British Imperial ................... .. 1.20091 gallons, U.S. 4.54596 liters gallons, British Imperial .................... . .832702 gallons, British Imperial gallons, U.S ...................................... . .13368 cubic feet gallons, U.S ...................................... . gallons, U.S ..................................... .. 3.78543 liters grams, metric ................................... .. 2.20462 x 10- 3 pounds, avoirdupois horse-power, metric .......................... . .98632 horse-power, U.S. 1.01387 horse-power, metric horse-power, U.S ............................. .. inches ................................................ . 2.54001 centimeters 2.20462 pounds kilograms ........................................... . kilograms per sq. centimeter ........... .. 14.2234 pounds per sq. inch .62137 miles, statute kilometers ......................................... . .26417 gallons, U.S. liters ................................................... meters .............................................. .. ,3.28083 feet 39.37 inches meters ................................................ meters ................................................ 1.09361 yards miles, statute .................................... . 1.60935 kilometer feet milimeters ......................................... . 3.28083 x 10-3 milimeters ......................................... . 3.937 x 10- 2 inches kilograms pounds avoirdupois ........................... . .453592 kilograms per sq. meter pounds per square foot .................... .. 4.88241 pounds per square inch .................... . 7.031 x 10-2 kilograms per sq. centimeter degrees angular radians ............................................... 57.29578 square centimeters ........................... . .1550 square inches 6.45163 square centimeters square inches ................................... . 1.19599 square yards square meters .................................. .. square kilometers square miles .................................... .. 2.590 .83613 square meters square yards .................................... .. 1016.05 kilograms tons, long .......................................... . 2240. pounds tons, long ......................................... .. 2204.62 pounds tons, metric ....................................... . .98421 tons, long tons, metric ...................................... .. tons, short tons, metric ....................................... . 1.10231 tons, short ......................................... . .892857 tons, long tons, metric tons, short ........................................ .. .907185 .914402 yards ................................................ .. meters
447
PART IV. DESIGN OF STEEL STRUCTURES 1.
Stress and Strain Formulas .. ..... .... .... .... .... .... .... .... .... .... .... ... ....... ..... ...... 448
2.
Properties of Sections ........................................................................... 450
3.
Center of Gravity .................................................................................. 452
4.
Beam Formulas ..................................................................................... 455
5.
Design of Welded Joints ....................................................................... 458
6.
Example of Calculations ....................................................................... 461
7.
Bolted Connections .... .... ............ .................... .... .... ........ ................ .... ... 463
448
STRESS AND STRAIN FORMULAS = Bending stress, psi = Shear stress, psi
DEFINITION OF SYMBOLS A = Cross sectional area, in 2• AR = Required cross sectional Area, in 2 1 =Moment of inertia, in 4 M = Moment, in-lb MA = Allowable moment, in-Ib P =Force, Ib PA = Allowable force. Ib S = Tensile or compressive stress, psi
= Allowable tensile or compressive stress, psi = Allowable bending stress, psi. = Allowable shear stress, psi. == Distance from neutral axis to extreme fiber, in = Section modulus, in3
TYPE OF LOADING
P..f. ~--8-P A' TENSION
0- P
tt P~"·U-·i--~ 4
A'
COMPRESSION
P
~~Single P/2.~
S =
AR
Double
A
= -P (.102) SA
~ (psi) A PA = ASA (Ib) P (. 2) AR == - m SA S =
Ss
=
.!.. (psi)
A PA = ASSA (lb) P (. 2) AR = - 10 SSA S
PA
P/2-
~ (psi)
PA = ASA (Ib)
S ~p
EXAMPLES
=.!.(psi) 2A = 2ASSA
(lb)
A =P- (.10 2)
M == PI (in-Ib) MA = ZSA (in-Ib) M (. 3) ZR = - 10 SSA
S
DIW LLb=cJ SECTION MODULUS
S = P = 5,000 = 10 000 psi A 0.5 '
To support a load of 11 ,000 lbs. in compression, the required area of steel bar made from SA 285C steel is:
AR =
1:... SA
= 11.000 = 0.5 in2 22,000
The required area of bolt made from SA-307 B steel to support a load of 15,000 lbs. in double shear:
AR
=L 2SA
= .
15.000 = 0.75 in 2 2x 10,000
2SSA
SHEAR
BENDING
The stress in a 2 x Y4 in. bar made from SA 285-C steel due to 5,000 lb. tensional load is: Area, A == 2 X Y4 = 0.5 in 2 ;
=
SA =
The maximum bending moment at the support of a cantilever beam due to a load of 1,000 lbs. acting at a distance of 60 inches from the support: M = PI == 1,000 x 60 = 60,000 in-lb.
M (psi) Z
~ (psi)
Section modulus
Zmin
If dimension b =2 in. and d=4 in, axis of moment on the base. 1=42.67. Z==lly == 42.67/4 = 1O.67in3 axis of moment through center, 1= 10.67, Z=lly = 10.67/2 = 5.335 in3
1 Z== Y
449
ALLOWABLE STRESSES FOR NON PRESSURE PARTS OF VESSELS AND OTHER STRUCTURES TYPE OF STRESS & JOINT
ALLOW ABLE STRESS
STEEL Bearing Shear
Compression Tension (except pin connection) Bending Shear Bearing (on projected area of bolts
in shear on connection)
1. 60 x} The values of 0.80 x tables UCS-23
0.60x } O.6Ox 0.66x 0.40x 1.5 x
Specified minimum yield stress Min. tensile strength
SOURCE CODE UCS-23 Notes
American Institute of Steel Construction
WELDED JOINT OF STEEL Full penetration groove weld tension, compression, shear Partial penetration groove weld 1. tension transverse to axis of weld, shear on throat 2. tension parallel to axis of weld or compression on throat
same as for the steel welded
13,600 psi same as for the steel welded
Fillet weld, shear on throat
13,600 psi (using throat dimension) 9,600 ('si (usmg leg dimension)
Plug or slot weld
same as fillet weld
American Welding Society
450
PROPERTIES OF SECTIONS DEFINITION OF SYMBOLS
r y
= Area, in. 1 = Moment of inertia, in.4
A I
fa /.
0
=
y
IIJ
I/~ 0
1= 0112
l = oj6
I.
./
= 0.289
r
y
=0
I
=
=
l
=
r
= 0.577
r
./
= bdy3
=
Y~
r
=
A
I.
0.2890 b2
02_
1.=0!;4- b )/12
Z
=(04- b4 )/6a
r
=
0.289.J 0 2 + b 2
= '~
=(04 -
b~)/ 12
=(O.118a4-b4Vo
, = 0.289,j A
= bd
~ /.
Z
r
= =
bd/6 0.289 d
./
02 + b 2
d[ffJ? I..
j
b
.S\' ' .
:'
~
d
Y
hk.1 bd - hk
bd
2
bd /24
=
= 0.236 d
Y
=d
I
= bd 3/12 = bd112
Z
, = 0.408
d
A = d(a+ bJ/2 Y '" d(o + 2b)/3(a + b) d,1 (a 2 + -I ab + b 2) I = -3-6-(a +b)2
d (a 2 + -I ab + b 2) Z = ----:-;-12 (a+2b)
A
=..J/iA = 0.7854d 2
y =
d/2
.
...•.".".'::.'."'."'."..'...•' '••.............. .•..•..•.....'.'. : ...•.•.•. : .•... .•..::•..
......
I bdJ -
v'
r
r
~ : ~'."~;'\" ",
I = bd-;12
b
0.289
hk J )/6 d
1= bdo/36
.1
b
n
= 0.7070
l
hk 3 )/12
-
Y=¥:ld
Z
4
I
3
Z =(Pd] -
y='I2 0
Y
d
bd-hk
I =(bd
0.1180 3
=
A
.1
=d
Z
ai'3
I = 04/12
b
Y
bd
y = V2d
= 02 = 0.7070
y
I
=
1= bd/3
r=0.5770 A
ITa
b
= 0'l3
Z
1
0
0
A
A
{OJ I.
Z
Radius of gyration, viTIA Distance from neutral axis to extreme fiber, in. Section modulus, l/y, in. 3
I = 0.049 d
= , =
Z
0.098d
d/4
4
3
451
PROPERTIES OF SECTIONS DEFINITION OF SYMBOLS
r
A
y
I
Area, in.l Moment of inertia, in.·
Z
V
Radius of gyration, II A Distance from neutral axis to extreme fiber, in. J Section modulus, Jly, in.
""TT"I y'" D/2 I
=
Z
='
0.049 (d-d~
0.098(D~-d~)/D
r ",...[fii+Ci1/ 4
:f9
Section of thin walled cylinder when R > /01
A = 2R1Tt
Y=R I = R-'I7T Z = R'17T
1
r = 0.707R
A '" ((2 a-I)
~l.~I I.
Y
=a_
I
= 1,-)( ly 3+ a(a_y)3 - (a - I) (a -
a
A '" I(a+b-I)
=
.1
=
Z
1.5708 (Rl_ r/)
Y", b/2 1=(2 sb J +h(.1)/12
Z =(2 sb J +h(.1)/6 b
=.../T!A
r
r = V7[A
A '" bd-h(b-I)
y '" a
Y = d/2
I '" 0.7854 alb
I ",!Pd J -h.1(b-O]/12
z r A
= 0.7854 a'b
=
a/2
I
Z ",.[bdJ_hJ(b_I)]
, '"
= bs +
_ d y -
h(
d'( + s'(b-I) 2(bs+ hi)
=
VJ (ly.1+ b(d-yJl -(b-I)(d-y-s).1)
Z = f/y r
VTiA
A '" bd-h(b-I}
Ily
= 3.1416 ab
6d
r =
R+r,
A
I/y
bd'-hYb-l)
J
1= 0.1098 (R~-r,' _ 0.283 Ri 'l' (R-r, )
=
=
=.JliA
y = dl2
y = O. 424(RJ - r;)j(Ri - rn
Z
Z r
I '" [bd·~h.1(b-l)] /12
r = 0.132 d
A
1(2d + a) + d'
A = bd - h (b - I)
0.007 d 4
Z '" 0.024 d
b_
2(d+a) 1= y,(ly 3+ a(b_y).1 _(a_l)(b_y_I)')
y=O.l88d
I
=
Y
0.393 d '
A =
=VTiA
r
~ll~ a
y - In
Z =//y
til
I~
a'+al-(' 2(2 a-I)
=..JTTA
.j
/6d
bdJ-h)(b-O 12(M-h(b-l))
A = bd-h(b-t) Y - b -
2 b' s+ hi' 2 bd-2h(b-l)
I ={2sb 3 + h/J)!3 -A(b-y)·' Z r
=
lIy
=.J17A
452
CENTER OF GRAVITY The center of gravity of an area or body is the point through which about any axis the moment of the area or body is zero. If a body of homogenous material at the center of gravity were suspended it would be balanced in all directions. The center of gravity of symmetrical areas as square, rectangle, circle, etc. coincides with the geometrical center of the area. For areas which are not symmetrical or which are symmetrical about one axis only, the center of gravity may be determined by calculation. The center of gravity is located on the centerline of symmetry. (Axis y - y) To determine the exact location of it: 1. Divide the area into 3 rectangles and calculate the area of each. (A, B, C) 2. Determine the center of gravity of the rectangles and determine the distances a, band c to a selected axis (x-x) perpendicular to axis y-y. 3. Calculate distance y to locate the center of gravity by the formula: y = Aa+Bb+Cc A+B+C
y
,r-
-+ ~f +----,. C c.g.
x lflo....-A_--I-----'-t-->--'-x y
Assuming for areas of rectangles: A = 16, B = 14 and C = 12 square inches and for the distances of center of gravities: a= 1, b=5 and c=9 inches.
EXAMPLE #1
y = 16 xl + 14 x 5 + 12 x 9 = 4.62 in. 16+ 14+ 12 The area is not symmetrical about any axi:s. The center of gravity may be determined by calculating the moments wIth reference to two selected axes. To determine the distances of center of gravity to these axes: 1. Divide the area into 3 rectangles and calculate the areas of each. (A, B, C) 2. Determine the center of gravity of the rectangles and the distances, a, band c to axis x-x and the distances aJ, bJ, c, to axis y-y. 3. Calculate distances x and y by the formulas:
y
x = Aal + Bb l + CCl A+B+C
c
b X
X Y
y EXAMPLE #2
x
=
16x4+14x1+12x3 16+ 14+ 12
=
= Aa+Bb+Cc A+B+C
Assuming for areas of rectangles: A = 16, B = 14 and C = 12 square inches and for distances of center of gravities: a=l, b=5, c=9: a,=4, b,=l and c,=3 16 x 1 + 14 x 5 + 12 x 8 = 4.62 in. 2.71 in. y 16+14+12
453
CENTER OF GRAVITY TRIANGLE The center of gravity is at the intersection of lines AD and BE, which bisect the sides Be and A C. The perpendicular distance from the center of gravity to anyone of the sides is equal to onethird the height perpendicular to that side. Hence, a = h ..;- 3. TRAPEZOID The center of gravity is on the line joining the middle points of parallel lines AB and DE. h(a+2b) d=h(2a+b) c= 3 (a + b) 3 (a + b) a 2 + ab + b 2 e= 3 (a + b) SECTOR OF CIRCLE Distance b from center of gravity to center of circle is: 2 b = 2 rc = r c = 38 197 r sin 0: 31 3A . 0: in which A = area of sector, and 0: is expressed in degrees. For the area of a half-circle: b = 4 r";- 3 Tr = 0.4244 r For the area of a quarter circle: b= 4 X r ..;- 3 Tr = 0.6002 r For the area of a sixth of a circle: b 2 r";- Tr 0.6366 r
J2 =
=
SEGMENT OF CIRCLE The distance of the center of gravity from the center of the circle is: c3 2 r3 sin 3 0: b = 12 A = 3 X A in which A = area of segment. PART OF CIRCULAR RING Distance b from center of gravity to center of circle is: 3
Angle
0:
b = 38.197 (R3 - r ) sin 0: (R2 - r2) 0: is expressed in degrees.
FRUSTUM OF CONE For a solid frustum of a circular cone the formula: h (R2 + 2 Rr + 3 r 2) a= 4 (R2 + Rr+ r2) The location of the center of gravity of the conical surface of a frustum of a cone is determined by: h (R + 2 r) a=3(R+r)
454
CENTER OF GRAVITY EXAMPLES t--_ _ _ _ _ _ _ _ _I:.;:oo~·-.....;0:;....- - - - - - - _ + - 1 f + . 3 · -0"
A
70'-0" 2'-0"
80lbs 75000 Ibs
2·6.. -t--t-4------------...:..:..--------.....,1+-t--2· -0"
x
weight: 75000 Ib 80lb 1800 Ib 800lb 600lb 600 Ib 78880 Ib
75000
x
l<
50' + 80 x 2' + 1800 x 70' + 800 x
102' + 600 x 2'-6" + 600 x 97'-6"
78880 Ibs = 4,017,760 = 50,935' = 50' -11-1/4" 78,880
56'-0" U7000 Ibs)
"I
2'-0"
1000 Ibs
1400 Ibs
weight:
107'-0"
X
2400 x 3' + 24000 x 27' + 1000 x 49' + 17000 x 78' + 1400x lOT + 1900 x II'
=~~------~-.....:~--~--~--~~~~~~~~-------
47,700 Ibs. 2200,900 III = - - - = 46.14' = 46'-1 116" 47,700
2400 Ih 24000lh 1000 Ib 17000lb 1400 Ib 1900lb 477001b
455
BEAM FORMULAS DEFINITION OF SYMBOLS = Modulus of elasticity, = Moment of inertia, in. = Length, in. = Moment of force, in. lb. p = Force of concentrated load, lb. R = Reaction, lb.
W
fSi.
E I / M
v
= = =
w
==
V
x
10ad,lb. Total shear, lb. Unit shear, Ib.lin. unifonnly distributed load Ib.lin. Distance parallel to axis X, in. Deflection, in. Angle of deflection, radians
= = =
.:1
e
Cantilever fixed at one end - Concentrated load at free end p
l__________~ LUI r=
R
.I
=
=
V
P
At support, Mmax = PI Mx = Px
R
At free end, ~max
=
PI3 3EI
P 6EI
~x = - - (2P - 3f2x
+
x 3)
Cantilever fixed at one end - Concentrated load at any point
2
R = V = P
At support, Whenx>a
Mmax = Pb Mx = P(x - aj
At free end,
~max =
Whenx
3
I
.1
(31 - b)
~
_ P - xj2 (3b - I + x) 3EI
x -
Uniform load over entire span R = V = wi
~
Vx = wx
(IIIIIIIIIIIIIIIIIII~R
~
3
6EI Whenx>a
-
Cantilever fixed at one end -
wi
Pb
At support, A
At free end, '-lomax
=
Mmax
=
wi· 8EI
--
~
wf2
Mx=
2
_ ~ (r - 4Px x -
24EI
2
+ 3f4)
4 Cantilever fixed at one end - Load increasing uniformly from free end to support R = V= W
w=
A
2
Vx=W~ At support,
WP At free end, ~ max = 15EI Wf2
At free end, 0 = + - - 12EI
12 Mmax =
Mx =
Wx 3 3f2
WI 3
~x = ~ 60EIP
(.x'-5f4x+41')
456
BEAM FORMULAS s
Supported at both ends Concentrated load at mid-span RJ = R2 = V = PI2 PI Mx= Px At load, Mmax = - When x < I 12 RJ~----------~R2 4 2 PI' A d PI2 At load, ~max = 48EI ten, (JJ = - 16£1 = - (h A Px I 12 ~x = - - (312 - 4XZ) 48EI
<
When x
Supported at both ends Concentrated load at any point Pab Max when a < b RI = VI = Pb At load, Mmax = - -
6
P
M ax when a>b R2
=
V2
Whenx
I
..
I Pbx I Pa 2 b 2 At load, A = - 3EII
I
= -~-
RJ ~---.&..- R2 when a> b
=
Mx
Whenx
At ends, 7
RI
Supported at both ends Two unequal concentrated loads, equally spaced from ends R = V =P Mmax = Pa Whenx<.a Mx = Px Pa At center, A max = 24EI (3P - 4a 2)
~_...._____.. R2
~ x = Px (31a - 3a2
When x
6EI Pa 6EI (31x -
Whenx>a ~ _ but x «I-a) x At ends, 6
-
r) 2
3r - a)
Pa 2EI (I - a)
=
8 Supported at both ends Two equal concentrated loads, unequally spaced from ends RI = VI PI(I- a) + P2b R2 = V2=Pla + P2(/ - b)
P
P
I
R/~---......-
.. R2
When x>a but x
'/
When xa but x < (I - b) 9
Supported at both ends
R =V
=
I
Max when RI
= RI X
= R2 b
(x - a)
+-
Uniform load over entire span
V =w(
;1
wP
At center, Mmax =-8 5w/ J
At center, ~max = 384EI At ends,
-
= RI a
6
=
wf3 24EI
x )
wx Mx = - ( 1 - x) 2
~x =
2
2;;1 (P - 21x + xl)
457
BEAM FORMULAS 10
Supported at both ends Uniform load partially distributed over span' wb Max when ac R2 = V = wb (2a + b) 21 When x>a but x «a + b) Vx = RI - w(x - a) Mmax = RI
(a+~ 2w)
When x
Atx = a
+~ w
Mx =RlX W
Whenx>a butx«a+b) Mx =Rlx- 2" (x - aj2 When x>(a+ b) Mx = R'l(1 - x) 11 Fixed at both ends Concentrated load at mid-span I t----'--_+--1-/2---<~ R =V = P At center and Mmax = ~ .~ 0.2 at ends, 8
2f
~
R0; j - - -....~ x 'I I
~
......
.1
I.
11
R
2
When x <112
Mx
0::
At center,
A max
=
P (4x - I)
8
= -PP-
Ax =
192£1
Pr (31 - 4x)
48EI
Fixed at both ends Uniform load over entire span V
= ~l
I1111111111 i I! 11111 t§R I~~ ~ ~ A tend s,
lYlmaX
'-
~
~
I
I
t - - - - - ' - - -..~
13
x
a
II'
=
AI
Vx =
=W
12/2
W /
1
po
a
(
~
A
-
x)
t center,
Mx = W /12 (61x - 12 - 6x2). A _ wi t center, ~ max 384£1
Both ends are overhanging Uniform load R = VI + V2 = w(a + 112) WXl 2 For overhang, Mxl = - 2 Between supports, Mx = III III ill I III
n II
R
M -_ wll /24 r/
2
"x __ ~
....
24EI
(I
_
x)
2
over entire beam Vxl = WXI Vx = w(x - 112) wa 2 At support, M = - 2 w
2
(Ix -
X2
-
At center, Me.= ~ (12 - 4 a 2) 8 When a = .207 x total length or A = .3541 wf2 M=Mc. = 16
a 2)
458
DESIGN OF WELDED JOINTS FOR STRUcruRAL MEMBERS GROOYE-WELD Groove welds are usually a continuation of the base metal. For groove welds the same strength is ascribed as for the members that they join. FlLJ.,ETWELD Size of weld
I ~h~at
The size of an equal-leg fillet weld is the leg dimension of the largest 450 right triangle inscribed in the cross section of the weld.
eg
The size of an unequal-leg fillet weld is the shortest distance from the root to the face of the fillet weld.
~~
~root
Throat dimension
= 0.707
x leg dimension
Minimum Weld size·
Thickness of the thicker plate, in.
Y2
¥4
Y2
Minimum fillet weld size, in.
¥16
Y4
0/16
2Y4 3fs
6 Y2
over 6 5fs
* Weld size need not to exceed the thickness of the thinner part joined Economy of fillet welding 1. Use the minimum size of fillet weld required for the desired strength. Increasing the size of a fillet weld in direct proportion, the volume (and costs) of it will increase with the square of its size. 2. Locate weld to avoid eccentricity, to be readily accessible, and in down-welding position. 3. Apply fillet weld transversely to the force to achieve greater strength.
~ PARALLEL
P'
WELD
~
TRANSVERSE ~ WELD
Allowable Load The strength of the welds is a function of the welding procedure and the electrode used. For carbon steel joints commonly used maximum allowable static load 9,600 (9.6 kips) Ibs per 1 square inch of the fillet weld leg-area, or 600 Ibs on a Y16" leg x 1" long fillet weld. For example: the allowable load on a Y4" x 1" long fillet weld 4 x 600 = 2,400 lbs. Combined Loads Shear stress and bending or torsional stresses due to eccentric loadings may be combined vectorially. It is based on the elastic theory and provides a simplified and conservative method.
459
DESIGN OF WELDED JOINTS FOR STRUcrURAL MEMBERS subjected to bending moment, in 2 V = Vertical shear, kips w = Fillet weld leg dimension, in W = Load on fillet weld, kips per lineal inch of weld W,r = Average vertical shear on fillet weld, kips per lin. inch of weld Wb = Bending force on weld, kips per lin. inch of weld
DEFINmON OF SYMBOLS Aw = Length of weld, in. t = Allowable load on weld, 9.6 kips per in2 • le~-area M = Bending moment, kips P = Allowable concentrated axial load, kips Sw = Section Modulus of weld lines
FORMULAS FOR FORCES ON WELD
Ws
TENSION OR COMPRESSION
VERTICAL
RESULTANT FORCE: W = YW,2 +
wi
= -V
Aw
SH~AR
BENDING
+ W/
EXAMPLE #1 Determine the required size of fillet weld. The length of the weld is all around 8.5 inches and the tensional load 20 kips. 20,000 lbs.
W
= ~ ='~=
w
= ~ = 29~: = 0.24; use~"
Aw
8.5
2.35 kips per lin. in.
fillet weld
EXAMPLE #2 Determine the required size of fillet weld. The length of the weld 12 inches (6" each side) and the load 9 kips. 9,000 lbs
Section modulus, (from table) Bending Force,
~
=
Sw
Shear Force Ws =
~ 12
Sw
Fillet weld size,
W
62
12 in'
= 2.25 kips per lin. inch
~w = ~ = 0.75 kips per lin. inch
Resultant force, W =oJWb2 + W/
vi
tf
= 3"= 3"=
= 2.37 kips per lin.
+
=
=2.37 = .247"; use W' fillet weld
W
t
0.752
=
2.25 2
9.6
inch.
460
DESIGN
OF
WELDED
JOINTS
PROPERTIES OF WELD OUTLINES
d~t_-x
cf
Sw = -6
d2 SW = 3
Sw
Sw (top)
= bd d (4b
=
6
+ d)
d 3 (4b+d) Sw (bottom) = 6 (2b + d)
(max.stress at bottom)
S
w
=
d2 bd -+6
_ d (2b + d) Sw ( top ) 3 Sw
=
d2 (2b+ d) (bottom) 3 (b + d)
(max. force at bottom)
2 'TT d Sw =4-
461
EXAMPLE CALCULATIONS EXAMPLE #1 A platform is supported by 3 equally spaced channels bolted to lugs. The floor load is 125 Ibs per square feet. The other design data are shown in the figures. Determine the stresses in the channels and bolts. One half of the total load is supported by the middle channel, thus the stress conditions only of this channel shall be investigated. Area supported by the middle channel:
~ .7854 (li-5 2 )= 15.577 sq. ft. 360
=
Load: 15.577 x 125
1947 lbs
Center of gravity (see page 434): 3
b = 38.197 (R -,J) sin oc = (R2 -,z) oc 3
3
38.197 (6 - 2.5 ) 0.500 (62 - 2.5 2 ) 30
4.28
Moment: 1947 x 2.28 x 12 = 53,270 in-lb Moment of inertia: I xx
Ixx
4"1
_ bd 3 12
.b I d? _ 12-
_
-
2 X 123 12
= -- -
1.75 X 11.53 12
66.206
Section modulus:
Z
= : = 66 206 = 11.034
6
Stress in channel at the support:
53,270 S = 11.034 = 4828
- --
:: N
::
~
. pSI
Stress in bolts: (center on bolts pattern) load on one bolt:
53,270
8
.
try '/11
bolt; A =0.6013 in 2
6659
S
= 6659 lb.
= 0.6013 =
11074 psi.
462
EXAMPLE CALCULATIONS EXAMPLE #2 A vertical vessel is supported by two beams. The weight of the vessel is 20,000 lbs I = 120 in Assume pin joint The load on one beam: Moment: M == PI = 10,000 x 120 = 4 4
10'·0"
300,000 in.lb
Required section modulus:
--
Z=M
SA Assuming for allowable stress, SA: 20,000 psi, Section modulus:
I
I
I
I
Z
= 300,000
= 15 in 3
20,000 The section modulus of a wide flange WF 8 X 20 is 17 in3 Moment of inertia: 69.2 Stress at the center of wide flange:
S
10,0001bs
..
!
=M Z
= 300,000 = 17,647 psi 17
Deflection: .6.
= PP
==
48£1
3
10,000 X 120 48 x 29,000,000 x 69.2
.1794 in -
3/16
in.
463
BOLTED CONNECTIONS FOR STRUCTURAL MEMBERS
REQUIRED LENGTH OF BOLTS NOMINAL REQUIRED BOLT LENGTH = BOLT GRIP + DIMENSIONS BELOW, inches DIAMETER NO WASHERS 1 WASHER 2 WASHERS m. 718 11!J6 Ih I 5/8 V8 IV16 IY16 I ~ 15/16 I Vi6 718
IV8 IV4 IV2 1%
I 1V8 IV4 IVs IV2
15fI6 ]7/16 I 1V16
r-
IV16
'-
10/)6 1Vi6 11Sf16
I~
113/16 115/16
IVs
2V16
2Y16
~~~b --~B~~~~GRIP
21!J6
MINIMUM EDGE DISTANCE AND SPACE The minimum distance from the center of bolt hole to any edge BOLT DIAMETER in
MINIMUM EDGE DISTANCE AT SHEARED EDGES
AT ROLLED OR GAS CUT EDGES
718
~
~
IYs IV,
V8
IV2
Vs I I Vs IV4 IIh 1% P/8
V2 VB
I
lY4
IYs IV,
2 2l,4
IIh
2%
vvl"" ('<") ('<")
0 Z
-ill-
- - t-O
~II-
QS --t-tf) ('<")
('<")
-1,.-. 1"'--l-
-t-
-i LEDGE DISTANCE
BOLT HOLES shall be Y16" larger than bolt diameter. ALLOWABLE LOADS in kips SA 307 unfinished bolts and connected material: SA 283C, SA 285C, SA 36 Nominal Diameter of Bolt
%
Tensile Stress Area, in
718
I
IV8
1l,4
IVs
I V2
0.2260 0.3345 0.4617 0.6057 0.7633 0.9691 1.1549 1.4053
Allowable Loads in Tension Allowable Loads in Shear
~
4.52
6.69
9.23
12.11
15.27
19.38
23.10
28.11
Single
3.07
4.42
6.01
7.85
9.94
12.27
14.85
17.67
Double
6.14
8.84
12.03
15.71
19.88
24.54
29.70
35.34
-------------NOTES
465
PARTV. MISCELLANEOUS 1.
Abbreviations......... ............................................................................... 466
2.
Codes, Standards, Specifications .......................................................... 470
3.
Boiler and Pressure Vessel Laws.......................................................... 474
4.
List of Organizations Sponsoring or Publishing Codes, Standards or Specifications Dealing with Pressure Vessels ................. 476
5.
Literature............................................................................................... 479
6.
Definitions ................................. ............................... .... ........ .... ............ 483
7.
Index ..................................................................................................... 494
466
ABBREVIATIONS COMPILED: From 1. ASA Z32.13-1950 ABBREVIATIONS FOR USE ON DRAWINGS 2. ASA ZlO.1-1941 ABBREVIATIONS FOR SCIENTIFIC & ENGINEERING TERMS ADDED:
AB AISC
ALLOW ANSI ASA API APPROX ASB ASME
ASTM AVG bbl BC BEV BLD BOP BOT BRKT btu BW BWG
C CA
ABBREVIATIONS GENERALLY USED ON VESSEL & PIPING DRAWINGS Anchor Bolt American Institute of Steel Construction Allowance Allowable American National Standards Institute American Standard Association American Petroleum Institute Approximately Asbestos American Society of Mechanical Engineers American Society for Testing Mat'ls. Average Barrel Bolt Circle Bevel Blind Bottom of Pipe Bottom Bracket British Thermal Unit Bevel Weld Birmingham Wire Gauge Degree Centigrade Corrosion Allowance
CCW cfm CFW CG CG cm
CO CONC CPLG CORR ALLOW COUP CRS CS C to C CTR cu cu. ft. CW CWT DC DEH DET DIA DIAM DIM DP
Counter Clockwise Cubic Foot per Minute Continuous Fillet Weld Commercial Grade Center of Gravity Centimeter Centerline Centerline to Centerline Company Concentric Coupling Corrosion Allowance Coupling Cold Rolled Steel Carbon Steel Cen ter to Cen ter Center Cubic Cubic Foot Clockwise Hundred Weight Downcomer Double Extra Heavy Detail Diameter Diameter Dimension Design Pressure
467
ABBREVIATIONS (cant.)
i
DT'L DWG EA EH EL ELEV ELL ELLIP EQ ETC EXT F F-F F&D FF FIG FIN FLG FS ft FT3 FW g GA GALV gal GG GOL gpd gpm GR HVY HD HEMIS HEX HH HL
Detail Drawing Each Extra Heavy Elevation Elevation Elbow Ellipse, Elliptical, Ellipsoid Equal, Equally Et Cetera External Fahrenheit Face to Face Flanged & Dished Flat Face Figure Finish Flange Far Side, Forged Steel Foot, Feet Cubic Foot Fillet Weld Gram Gage Galvanized Gallon Gage Glass Gage of Outstanding Leg Gallon per Day Gallon per Minute Grade Heavy Head Hemispherical Hexagonal Handhole Hole
HLA HLL HLSD HR HT ID in INCL INS INT JE kg I
lb lbf lbs LC LeV LG LG Lin. ft. LLA LLC LLSD LR LS LWN m MB MK MAT'L MAWP MAX MH MIN MK'D
High Level Alarm High Liquid Level High Level Shut Down Hot Rolled Heat Treatment Inside Diameter inches Including, Included hlspection Internal J oint Efficiency Kilogram Liter Pound Pound Force Pounds Level Control Liquid Control Valve Long Level Gage Lineal Foot (Feet) Low Level Alarm Liquid Level Control Low Level Shut Down Long Radius Low Stage Long Welding Neck Meter Machine Bol t Mark Material Maximum Allowable Working Pressure Maximum Manhole Minimum Marked
468
ABBREVIATIONS (cont.)
mm MMSCF MSCF MW N N&C NLL NO NOM NPS
NPT NS NTS OA OD OR OSHA oz ozs P PBE PC PeS PCV PI
It PROJ PSE psi psia psig
Millimeter Million Standard Cubic Feet Thousand Standard Cubic Feet Manway North New & Cold Normal Liquid Level Number Nominal National Pipe Size American National Taper Pipe Thread Near Side Not to Scale Overall Ou tside Diameter Ou tside Radius Occupational Safety and Health Administration Ounce Ounces Pressure Plain Both Ends Pressure Control Pieces Pressure Control Valve Pressure Indicator Plate Projection Plain Small End Pound per Square Inch Pound per Square Inch Absolute Pound per Square Inch Gage
RAD REF REINF REPAD REQ'D RF
RJ RTJ RV S
SIC SCF SCH SCR SCR'D SDV SERV Sht. SF SHT SM SMLS SO SPA SPEC SPGR SQ SR SS S-S
SIS STD STL STR SUPT SYM T&B TC TBE
Radial Reference Reinforcing Reinforcing Pad Required Raised Face Ring Joint Ring Type Joint Relief Valve Schedule Shop Coat Standard Cubic Foot Schedule Screw Screwed Shu tdown Valve Service Sheet Straight Flange Sheet Seam Seamless Slip On Spacing Specification Specific Gravity Square Short Radius Stainless Steel Seam to Seam Standard Steel Straddle Support Symmetrical Top & Bottom Temperature Control Threaded Both Ends
469 ABBREVIATIONS (cont.)
PSV R TEMA
THD THK TI TLE TOC TOS TS TSE T-T TW TW
Pressure Safety Valve Radius Tubular Exchanger Manufacturers Association Threaded, Thread Thick Temperature Indicator Threaded Large End Top of Concrete Top of Steel Tube Sheet Threaded Small End Tangent to Tangent Tack Weld Thermowell
TYP USAS VA VOL
WI WG
WN W/OUT WP
WT XH
XXH XXSTG
Typical United States of America Standards Institute Valve Volume With Water Gallon Welding Neck Without Working Pressure Weight Extra Heavy Double Extra Heavy Double Extra Strong
470
CODES, STANDARDS, SPECIFICATIONS
PRESSURE VESSELS, BOILERS ASME I II III IV V VI
VII VIII IX X XI
Boiler and Pressure Vessel Code, 2001 Power Boilers Materials Nuclear Power Plant Components Heating Boilers Nondestructive Examination Recommended Rules for Care and Operation of Heating Boilers Recommended Rules for Care of Power Boilers Pressure Vessels - Division 1, Division 2 and 3 Alternate Rules Welding and Brazing Qualifications Fiberglass-Reinforced Plastic Pressure Vessels Rules for Inservice Inspection of Nuclear Power Plant Components
British Standards Institution (BSI) 1500 - Fusion Welded Pressure Vessels for Use in the Chemical, Petroleum and Allied Industries 1515 -Fusion Welded Pressure Vessels for Use in the Chemic.al, Petroleum and Allied Industries (advanced design and con struction) Canadian Standards Association (CSA) B-51-MI991- Code for the Construction and Inspection of Boilen and Pressure Vessels TANKS American Petroleum Institute (API) Spec 12B Specification for Bolted Tanks for Storage of Production Liquids, 1990 Spec 12D Specification for Field Welded Tanks for Storage of Production Liquids, 1982
471 CODES, STANDDARDS, SPECIFICATIONS
(Continued)
Spec 12F Specification for Shop Welded Tanks for Storage of Production Liquids, 1988 Std. 620 Recommended Rules for Design and Construction of Large Welded, LowPressure Storage Tanks, 1990 Std. 650 Welded Steel Tanks for Oil Storage, 1988 Underwriters Laboritories, Inc. (UL)
No. 142 No. 58
Steel Aboveground Tanks for Flammable and Combustible Liquids Steel Underground Tanks for Flammable and Combustible Liquids
American Water Works Association (A WW A)
No. 30 No. 58 No. 59
Flammable & Combustible Liquids Code Liquified Petroleum Gases, Storage and Handling Liquified Petroleum Gases at Utility Gas Plants
PWING American National Standards Institute (ANSI)
831.1-1998 831.2-1968 831.3-1999 831.4-1998 831.5-2000 83l.8--1999
Power Piping Fuel Gas Piping Chemical Plant and Petroleum Refinery Piping Liquid Petroleum Transportation Piping Systems Refrigeration Piping with 1978 Addenda Gas Transmission and Distribution Piping Systems
HEAT EXCHANGERS Expansion Joint Manufacturers Association, Inc.
Standards, 5th Edition with 1985 Addenda and Practical Guide to Expansion Joints PWES American National Standarsa Institute (ANSI)
ANSI 836.19-1976 Stainless Steel Pipe ANSI! ASME 836.1 OM- 1985 Welded and Seamless Wrought Steel Pipe
472
CODES, STANDARDS, SPECIFICATIONS
FITI1NGS, FLANGES, AND VALVES American National Standards Institute (ANSI) ANSI B16.25-1992 Buttwelding Ends ANSI B 16.1 0-1992 Face-to-Face and End-to-End Dimensions of Ferrous Valves ANSI B16.9-1993 Factory-Made Wrought Steel Buttwelding Fittings ANSI B 16.14-1991 Ferrous Pipe Plugs, Bushings, and Locknuts with Pipe Threads ANSI B16.11-1991 Forged Steel Fittings, Socket-Welding and Threaded ANSI B16.5 1988 Pipe Flanges and Flanged Fittings, Steel, Nickel' Alloy and Other Special Alloys ANSI B16.20-1993 Ring-Joint Gaskets and Grooves for Steel Pipe Flanges MATERIALS The American Society for Testing and Materials (ASTM) 1989 Annual Book of ASTM Standards, Section 1 Iron and Steel Products Volume Ol.OllSteel Piping, Tubing and Fittings, 131 Standards Volume 01.03/Steel Plate, Sheet, Strip, and Wire, 95 Standards Volume 01.04/Structural Steel, _Concrete Reinforcing Steel, Pressure Vessel Plate and Forgings, Steel Rails, Wheels, and Tires - 135 Standards MISCELLANEOUS International Conference of BuDding Officials (ICBO) Uniform Building Code - 1991 Steel Structures Painting CouncU (SSPC) Steel Structures Painting Manual Volume 1, Good Painting Practice Volume 2, Systems and Specifications Uniform BoUer and Pressure Vessel Laws Society Synopsis of Boiler and Pressure Vessel Laws, Rules and Regulations by States, Cities, Counties and Provinces (United States and Canada) -1990,
473
CODES, STANDARDS, SPECIFICATIONS Environment Protection Code of Federal Regulations, Protection of Environment, 1988 40-Parts 53 to 60 (Obtainable from any Government Printing Office). American Society of Civil Engineers (ASCE) Minimum Design Loads for Buildings and Other Structures
ANSIIASCE 7-95 (Formerly ANSIIASCE 7-93)
474 TABULATION OF THE
BOILER AND PRESSURE VESSEL LAWS OF THE UNITED STATES AND CANADA JURISDICTION
r
ill N
Alabama Alaska Arizona Arkansas California Colorado Connecticut Delaware Florida'Y Georgia Hawaii Idaho Illinois Indiana Iowa Kansas Kentucky Louisiana Maine Maryland Massach usetts Michigan Minnesota Mississippi Missouri Montana Nebraska Nevada New Hampshire New Jersey New Mexico New York North Carolina North Dakota Ohio Oklahoma Oregon Pennsylvania Puerto Rico Rhode Island South Carolina South Dakota Tennessee Texas Utah Vermont Virginia
Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y N Y Y Y Y Y Y
Y Y Y Y N Y Y Y Y Y Y Y Y Y Y Y N Y Y Y N Y Y Y Y Y Y Y Y Y Y Y Y Y N Y Y Y Y Y Y Y Y Y Y Y N Y Y Y N Y N Y N Y N Y Y Y N Y N Y Y Y N Y Y Y N Y Y Y Y Y Y Y Y Y N N N Y Y Y Y Y Y Y N Y Y Y
~II(l) ~III(2)
Y N N Y Y Y N Y N Y Y Y Y Y Y Y Y N Y Y Y y*
Y Y Y N
Y Y Y Y N Y Y Y Y Y Y Y Y Y N N Y N Y Y Y
Y Y N Y Y Y3 N Y3 N Y Y Y3 Y Y Y3 Y3 Y N Y3 Y3 N N Y N Y3 N Y3 Y Y Y N N Y Y3 Y Y Y Y Y Y N N Y3 N Y3 Y Y
XI
Y N N Y Y Y N Y N Y N Y Y Y N Y N N Y Y Y Y Y N Y N N N Y Y N N Y N Y N Y Y Y Y N N Y Y Y N Y
EXPLANATION
The column headings indicate the Sections and Divisions of ASME Boiler and Pressure Vessel Code. I -Power Boilers H - Nuclear Components
IV VIII(1) Vill(2) IX
-Heating Boilers -Pressure Vessels -Pressure Vessels -Inservice Inspection Nuclear Y - Design and construction shall conform to the appropriate code section. Y3 - Denotes Section VIII, Division 2 and 3. N - Design and construction is not covered by law. * - Only portions of code. SOURCE:
This condensed tabulation of data is taken from the Synopsis of Boiler and Pressure Vessel Laws, Rules and Regulations, Copyright 1998, Uniform Boiler and Pressure Vessel Laws Society. It dies not list all the exemption and variances in the many laws and regulations. More detailed information is available under the Society's Synopsis. Further information may be obtained from the jurisdictional authority or from the society.
I
475 TABULA TION OF THE
BOILER AND PRESSURE VESSEL LAWS OF THE UNITED STATES AND CANADA (Continued)
I
JURISDICTION Washington West Virginia Wisconsin Wyoming Alberta British Columbia Manitoba New Brunswick New Foundland & Labrador Northwest Territories Nova Scotia Ontario Prince Edward Island Quebec Saskatchewan Yukon Territory Albuquerque Buffalo Chicago Denver Des Moines Detroit Los Angeles Miami Milwaukee New Orleans New York Omaha St. Joseph Seattle Spokane Tacoma Tucson Tulsa University City Dade County Jefferson Parish St. Louis County District of Columbia
I Y Y Y N Y Y Y Y
m
Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y
N N N Y Y Y Y N N Y Y Y N Y Y Y Y Y N N Y Y N Y N N N N Y Y Y
IV VIll(l) VIll(2) XI Y Y Y Y Y3 N Y Y N N Y Y Y Y Y3 N N Y N N Y Y Y Y Y Y Y Y Y3 Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y N Y Y Y Y Y Y Y Y Y Y Y Y
Y Y Y Y Y Y Y Y N Y Y Y N Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y Y
Y Y Y Y3 Y Y Y Y N N Y Y N
Y Y Y Y Y N N Y Y Y Y Y Y Y Y Y Y Y
N N N Y N N Y N N N Y Y N Y N N N Y N N N Y N N N N N N N N Y
EXPLANATION The column headings indicate the Sections and Divisions of ASME Boiler and Pressure Vessel Code. I -Power Boilers
n -NuclearComponents N VIII(l) VIII(2) IX
- Heating Boilers -Pressure Vessels -Pressure Vessels -Inservice Inspection Nuclear Y - Design and construction shall conform to the appropriate code section.
Y 3 - Denotes Section VIII, Division 2 and 3. N - Design and construction is not covered by law.
* - Only portions of code. SOURCE: This condensed tabulation of data is taken from the Synopsis of Boiler and Pressure Vessel Laws, Rules and Regulations, Copyright 1998, Uniform Boiler and Pressure Vessel Laws Society. It dies not list all the exemption and variances in the many laws and regulations. More detailed information is available under the Society's Synopsis. Further information may be obtained from the jurisdictional authority or from the society.
476
LIST OF ORGANIZATIONS SPONSORING OR PUBLISHING CODES AND STANDARDS OR SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS T = Telephone· F = Fax • E = e-mail· W = Website ABS American Bureau of Shipping Two World Trade Center, I 06th Floor New York, NY 10048 USA
T F E W
212-839-5016 212-839-5208 [email protected] www.eagle.org
AISG American Insurance Services Group, Inc. 85 John Street New York, NY 10038
T
212-669-0427
ANSI American National Standards Institute 11 West 42nd Street New York, NY 10026 API American Petroleum Institute 1220 L. Street Northwest Washington, D.C. 20005
F 212-669-0550 E [email protected] W www.aisg.org T
212-642-4900
F 212-302-1286 E [email protected] W www.ansi.org T
202-682-8375
F 202-962-4776 E [email protected] W www.api.org T
800-548-2723
ASCE The American Society of Civil Engineers 1801 Alexander Bell Drive Reston, V A 20191-4400
E [email protected] W www.pubs.asce.org
ASME
T
The American Society of Mechanical Engineers 3 Park A venue New York, NY 10016-5980
F 973-882-1717
ASTM American Society for Testing and Material 100 Barr Harbor Drive West Conshohocken, P A 19428 AWWA American Water Works Association 6666 West Quincy Avenue Denver, CO 80235 AWS American Welding Society P.O. Box351040 Miami, FL 33135 BSI British Standards Institution 389 Chiswick High Road London W44AL *British Standard Publications are available from The American National Standards Institute
F 703-295-6333
800-843-2763
E [email protected] W www.asme.org T
610-832-9500
F 610-832-9555 E [email protected] W www.astm.org T
303-794-7711
F 303-347-0804 E W www.awwa.org T
800-334-9353
F 305-443-7559 E W www.aws.org T 181-996-7474 F 181-996-7048 E W www.bsi.org.uklbsi
477
LIST OF ORGANIZATIONS SPONSORING OR PUBLISHING CODES AND STANDARDS OR SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS (Continued) CSA Canadian Standards Association 178 Rexdale Blvd. Etobicoce (Toronto) ON Canada M9W IR3
T 800-463-6727 F 416-747-2475 E [email protected] W
Commercial Union Insurance Company of America I Beacon Street Boston, MA 02108
T 617-725-7309 F 617-725-6094 E W www.cuusa.com
CGA Compressed Gas Association, Inc. 1725 Jefferson Davis Highway, Ste. 1004 Arlington, VA 22202
T F E W
703-412-0900 703-412-0128 [email protected] www.cganet.com
EJMA Expansion Joint Manufacturers Assoc. 25 North Broadway Terrytown, NY 10591
T F E W
914-332-0040 914-332-1541 [email protected] www.ejma.org
HEI Heat Exchange Institute, Inc. 1300 Summer Avenue Cleveland, OH 44115
T F E W
216-241-7333 216-241-0105 [email protected] www.taol.com/hei
ICBO International Conference of Building Officials 5360 Workman Mill Road Whittier, CA 90601
T 800-284-4406 F 888-329-4226 E W www.icbo.org
National Board of Boiler and Pressure Vessel Inspectors 1055 Crupper A venue Columbus, OH 43229
T F E W
614-888-2463 614-847-1147 [email protected] www.nationalboard.org
NFPA National Fire Protection Association P.O. Box 91 01, Batterymarch Park Quincy, MA 02269
T
800-344-3555 800-593-6372
F
E W
Occupational Safety & Health Administration 200 Constitution Avenue, N.W. Washington, D.C.
T 202-219-4667 F 202-219-9266 E W
PVRC Pressure Vessel Research Council (formerly: Welding Research Council) 3 Park A venue, 27th Floor New York, NY 10016
T 212-705-7956 F 212-371-9622 E [email protected] W www.forengineers.org/wrc
478
LIST OF ORGANIZATIONS SPONSORING OR PUBLISHING CODES AND STANDARDS OR SPECIFICATIONS DEALING WITH PIPING AND PRESSURE VESSELS (Continued) Steel Tank Institute 570 Oakwood Road Lake Zurich, IL 60047
T F E W
TEMA Tubular Exchanger Manufacturers 25 North Broadway Terrytown, NY 10591
T 914-332-0040 F 914-332-1541 E [email protected] W www.tema.org
SSPC The Society for Protective Coatings (formerly: Steel Structure Painting Council) 40 24th Street, 6th Floor Pittsburgh, PA 15222
T F E W
412-281-2331 412-281-9992 [email protected] www.sspc.org
lL Underwriters Laboratories, Inc. 333 Pfingsten Road Northbrook, IL 60062
T F E W
847-272-8800 847-509-6235 [email protected] www.ul.com
T UBPVLS Uniform Boiler and Pressure Vessel Laws Society F E 308 Evergreen Road, Ste. 240 W Louisville, KY 40243
502-244-6029 502-244-6030 [email protected] www.uboiler.com
847-438-8265 847-438-8766 [email protected] www.steeltank.com
United States Coast Guard 2100 Second Street S. W. Washington, D.C. 20593
T 202-267-2967 F 202-267-4816 E comd.uscg.mil W
US EPA Headquaarters Information Resources Center Public Access Ariel Rios Building 1200 Pennsylvania Ave., N.W. (3404) Washington, D.C. 20460
T 202-260-5922 F 202-260-6257 E E-pu bl [email protected] W www.epa.gov
479
LITERATURE 1.
S. Timoshenko, Strength of Materials, 1955, D. Van Nostrand Co., New York.
2.
S. P. Timoshenko, Theory ofPlates and Shells, 1959, McGraw-Hill Book Co., New York.
3.
R. J. Roark and W. C. Young, Formulas for Stress and Strain, 5th Edition, 1975, McGraw-Hill Book Co., New York.
4.
K. K. Mahajan, Design of Process Equipment, 2nd Edition, 1985, Pressure Vessel Handbook Publishing, Inc., Tulsa, OK.
5.
L. E. Brownell and R. H. Young, Process Equipment Design: Vessel Design,
1956, John Wiley and Sons, New York. (Out of print.) 6.
M. B. Bickel and C. Ruiz, Pressure Vessel Design and Analysis, 1967, Mcmillan Publishing Co., Inc., New York.
7.
H. H. Bednar, Pressure Vessel Design Handbook, 2nd Edition, 1986, Van Nostrand Reinhold Co., New York.
8.
S. S. Gill, The Stress Analysis of Pressure Vessels and Pressure Vessel Components, 1970, Pergamon Press, New York.
9.
J. F. Harvey, Theory and Design of Modern Pressure Vessels, 2nd Edition, 1974, Van Nostrand Reinhold Co., New York.
10. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Volume 1, Analysis, 1972, ASME. 11. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Volume II, Components and Structural Dynamics, 1972, ASME.
12. Pressure Vessels and Piping: Design and Analysis, (Collected Papers), Volume III, Materials and Fabrication, 1976, ASME. 13.
W. Soedel, Vibrations of Shells and Plates, 1981, Marcel Dekker, Inc., New York.
14.
W. Flligge, Stresses in Shells, 2nd Edition, 1973, Springer - Verlag, New York.
15.
R. Szilad, Theory and Analysis ofPlates, 1974, Prentice-Hall, Inc., Englewood Cliffs, NJ.
480 16. M. Hetenyi, Beams on Elastic Foundation, 1974, The University of Michigan Press, Ann Arbor. 17. Foundation Design Handbook (Collected Papers), 1968, Hydrocarbon Processing, Houston, TX. 18. Design of Flanges for Full Face Gaskets, Bulletin No. 45, Taylor Forge & Pipe Works, Chicago, IL.
19. M. L. Betterley, Sheet Metal Drafting, 1961, McGraw-Hill Book Co., Inc., New York. 20. M. H. Jawad & J. R. Farr, Structural Analysis and Design ofProcess Equipment. 1984, John Wiley & Sons, New York. 21. Kohan, Anthony Lawrence, Pressure Vessel Systems, 1987 , McGraw-Hill Book Company, New York, NY. 22. Moss, Dennis R., Pressure Vessel Design Manual, 1987, Gulf Publishing Co., Houston, TX.
481
SUBJECTS COVERED BY THE WORK(S) LISTED UNDER LITERATURE (The numbers refer to the work(s) dealing with the subject) Bending Of Cylindrical Shells -14 Bends, Analysis of Smooth - 6 Bins, Design of- 22 Blind Flanges with Openings - 22 Bolted Joints - 9 Brittle Fracture, Low Stress - 6 Buckling, - 6,10 of Flat and Curved Plates - Formulas-3 Buckling of Shells- 6 Cast Iron Pressure Vessels - 9 Collapse, Fatigue and Incremental- 6 Composite Materials - 12 Computer Analysis of Pressure Vessels- 8 Concrete for Pressure Vessels - 12 Cone, Conical Section when Half Apex Angle is Greater than 30° - 7 Conical Heads and Reducers - 6 Corrosion - 6,12 Corrosion Resistant Materials - 12 Cracks, Development of - 6 Creep Effects - 8 Cylindrical Shells, Analysis of, - 6 Dead Loads - 7 Deformations in Pressure Vessels, - 3 Design of Flanges - 4 Rectangular Tanks - 4 Tall Stacks - 4 Tall Towers - 7 Discontinuity Stresses - 7, 9 Division 2 of ASME Code Comparison to Division 1 - 4 Dynamic Stability - 11 Dynamic and Temperature Stress Formulas - 3 Earthquake Loads -7,22 Economics of Design andConstruction - 9 Elastic Stability - 8 Plates and Shells - Formulas - 3 Elastic Stress Analysis - 6 Elevated Temperature Effects -10,12 Elliptical Opening Stress Concentration - 9 Expansion Joints, Flanged and Flued - 4
Pipe Segment - 4 External Loads -10 External Pressure; Stress Analysis - 8 Fatigue - 9, 10, 12 Fatigue and Incremental Collapse - 6 Filament-Wound Pressure Vessels - 9 Flange Design - 4 Flange Design & Analysis - 8 Flanged and Flued Expansion Joints - 4 Flanges and Closures - 11 Flanges with Full Face Gasket -18 Flat Closure Plate - 6 Flat Plates - Formulas - 3 Stresses in,- 9 Floating Heads, Stress Analysis of, - 4 Foundation Design - 17 Fracture - 6 Fracture Mechanics -10 Fracture Properties of Materials -12 Heads, Stress Analysis of, - 8, 11 Heat Exchangers, Shell and Tube - 4 High Temperature Materials - 12 Hub Flanges, Rotation of, - 4 Hydrogen Embrittlement - 12 Large Openings in Flat Heads - 22 Large Openings in Cylindrical Shells - 22 Leg Support for Vertical Vessels - 4, 22 Ligament Stresses, Analysis of, - 8 Limit Analysis and Plasticity -10 Lobed Pressure Vessels - 9 Local Loading, Stress Analysis of, - 8, 11 Local Stresses in Vessels - 7, 22 Low Stress Brittle Fracture - 6 Low Temperature Materials -12 Lug Support for Vertical Vessels - 4, 22 Material Selection - 22 Materials for Vessels - 6,7,9 Membrane Stresses - 7, 9 Mitered Bends, Analysis of - 6, 8 Modular Construction - 9 Non-Bolted Closures - 9 Nozzles-11 Nozzles, Intersection Stress Analysis - 8
482
SUBJECTS (continued) Nozzle Thennal Sleeves - 9 Oblique Nozzles - 6 Perforated Plates and Shells - 11 Pipe Bends, Stress Analysis of, - 8 Pipe Segment Expansion Joints - 4 Pipe Supports at Intervals - Fonnulas - 3 Pipe Loads - 7 Piping Systems, Stress Analysis of, - 6, 11 Plasticity - 10 Plastic Collapse - 6 Plates, Theory and Analysis of - 18 Prestressed Concrete Vessels - 9 Rectangular Tanks, Design of, - 4 Reinforcement of Openings - 7 Ring Support - 22 Rotation of Hub Flanges - 4 Saddle, Design of, - 7 Seismic Analysis - 11 Seismic Design. Vessels Supported by Legs, Rings, Lugs, - 22 Selection of Materials - 6 Shallow Shells - 14 Sheet Metal Drafting - 19 Shell and Tub Heat Exchangers - 4 Shells of Revolution, Analysis of, - 6 Sliding Supports for Horizontal and Vertical Vessels - 7 Spherical Shells, Analysis of, - 6 Stress and Strain Due to Pressure on or Between Elastic Bodies - Fonnulas - 3 Stress Concentration - 9
Stress in Horizontal Vessels Supported by Two Saddles (Zick) - 7 Stresses in Flat Plates - 9 Stresses in Vessels - 8, 14 Fonnula - 3 Stacks, Designs of Tall, - 4 Structural Dynamics - 11 Support of Vessels by Legs - 4, 7 Support of Vessels by Lugs - 4, 7 Support Lugs, Stresses Exerted in Vessels by, - 24 Tall Stacks, Design of, - 4 Tall Towers, Vibration of, - 4 Tanks, Design of Rectangular, - 4 Temperature, Effects of Elevated, -10 Temperature Stresses - Fonnulas, - 3 Thennal Stresses, - 7, 9 Thick Cylinder - 9 Thick Shells, Analysis of, - 6 Tube Sheet Design, Fixed, - 4 Vertical Vessels Supported by Lugs - 4 Vibration -11,13 Analysis of Tall Towers - 4 Induced by Flow - 11 Weld Design - 7 Welded Joints, Design of, - 6,9 Welding, - 12 Wind-Induced Deflection of Towers - 7 Wind-Induced Vibration of Towers -7 Wind Loads - 7
483
DEFINITIONS
Abnsion - The removal of surface material from any solid through the frictional action of another solid, a liquid, or a gas or combination thereof. Absolute Pressure - The pressure above the absolute zero value of pressure that theoretically obtains in empty space or at the absolute zero of temperatre, as distinguished from gage pressure. Alloy - Any of a large number of substances having metallic properties and consisting of two or more elements; with few exceptions, the components are usually metallic elements. Angle Joint - A joint between two members located in intersecting planes between zero (a butt joint) and 90 deg. (a corner joint). (Code UA-60)
Angle Valve - A valve, usually of the globe type, in which the inlet and outlet are at right angles. Annealing - Annealing generally refers to the heating and controlled cooling of solid material for the purpose of removing stresses, making it softer, refining its structure or changing its ductility, toughness or other properties. Specific heat treatments covered by the term annealing include black annealing, blue annealing, box annealing, bright annealing, full annealing, graphitizing, maleabilizing and process annealing. Arc Welding - A group of welding processes wherein coalescence is produced by heating with an electric arc, with or without the application of pressure and with or without the use of filler metal.
Automatic Welding - Welding with equipment which performs the entire welding operation without constant observation and adjustment of the controls by an operator. The equipment mayor may not perform the loading and unloading of the work.
Ba«:king -
Material backing up the joint during welding to facilitate obtaining a sound weld at the root. Backing Strip is a backing in a form of a strip.
Brittle Fra«:ture - The tensile failure with negligible plastic deformation of an ordinary ductile metal. Brittleness - Materials are said to be brittle when they show practically no permanent distortion before failure. Bushing - A pipe fitting for connecting a pipe with a female fitting of larger size. It is a hollow plug with internal and external threads. Butt Weld -
on
A weld joining two members
lying approximately in the same plane. Butt welded joints in pressure vessel construction shall have complete penetration and fusion. Types of butt welded joints: Single or Double Beveled Joint, Square Butt Joint. Full Penetration, Partial Penetration Butt Joints. Butt Joints with or without backing strips.
484
Centroid of an Area (Center of Gravity of an Area) - That point in the plane of the area about any axis through which the moment of the area is zero; it coincides with the center of gravity of the area materialized as an infinitely thin homogeneous and uniform plate. Chain Intermittent Fillet Welds - Two lines of intermittent fillet welding in a tee or lap joint, in which the increments of welding in one line are approximately opposite to those in the other line. Check Valve - A valve designed to allow a fluid to pass through in one direction only. A common type has a plate so suspended that the reverse flow aid~ gravity in forcing the plate against a seat, shutting off reverse flow. Chipping - One method of removing surface defects such as small fissures or seams from partially worked metal. If not eliminated, the defects might carry through to the finished material. If the defects are removed by means of a gas torch the term "deseaming" or "scarfing" is used. Clad Vessel - A vessel made from plate having a corrosion resistant material integrally bonded to a base of less resistant material. (Code UA-60) Complete Fusion - Fusion which has occurred over the entire base-metal surfaces exposesd for welding. Complete Penetration - Penetration which extended completely through the joint. Corner Joint - A welded joint at the junction of two parts located approximately at right angles to each other. Corrosion - Chemical erosion by motionless or moving agents. Gradual destruction of a metal or alloy due to chemical processes such as oxidation or the action of a chemical agent. Corrosion Fatigue - Damage to or failure of a
metal due to corrosion combined with fluctuating fatigue stresses. Coupling - A threaded sleeve used to connect two pipes. They have internal threads at both ends to fit external threads un pipe. Creep - Continuous increase in deformation under constant or decreasing stress. The term is usually used with reference to the behavior of metals under tension at elevated temperatures. The similar yielding of a material under compressive stress is usually called plastic flow or flow. Damaging Stress - The least unit stress, of a given kind and for a given material and condition of service, that will render a member unfit for service before the end of its normal life. It may do this by producing excessive set, or by causing creep to occur at an excessive rate, or by causing fatigue cracking, excessive strain hardening, or rupture. Deformation (Strain) - Change in the form or in the dimension of a body produced by stress. Elongation is often used for tensile strain, compression or shortening for compressive strain, and detrusion for shear strain. Elastic deformation is such deformation as disappears on removal of stress; permanent deformation is such deformation as remains on removal of stress. Design Pressure - The pressure used in determining the minimum permissible thickness or physical characteristics of the different parts of the vessel. (Code UA-60) Design Temperature - The mean metal temperature (through the thickness) expected under operating conditions for the part considered. (Code UG-20) Discontinuity, Gross Structural - A source of stress or strain intensification which affects a relatively large portion of a structure and has a significant effect on the overall stress or strain pattern or on the structure as a whole. Examples of gross structural discontinuities are head-toshell and flange-to-shell junctions, nozzles, and junctions between shells of different diameters or thicknesses.
485
Discontinuity, Local Structural - A source of stress or strain intensification which affects a relatively small volume of material and does not have a significant effect on the overall stress or strain pattern or on the structure as a whole. Examples are small fillet radii, small attachments, and partial penetration welds. Double-Welded Butt Joint - A butt joint welded from both side. Double-Welded Lap Joint - A lap joint in which the overlapped edges of the members to be joined are welded along the edges of both members. Ductility - The ability of a metal to stretch and become permanently deformed without breaking or cracking. Ductility is measured by the percentage reduction in area and percentage elongation of test bar. Eccentricity - A load or component of a load normal to a given cross section of a member is eccentric with respect to that section if it does not act through the centroid. The perpendicular distance from the line of action of the load to either principal central axis is the eccentricity with respect to that axis. Efficiency of a Welded Joint - The efficiency of a welded joint is expressed as a numerical quantity and is used in the design of a joint as a multiplier of the appropriate allowable stress value. (Code UA-60) Elastic - Capable of sustaining stress without permanent deformation; the term is also used to denote conformity to the law of stress-strain proportionality. An elastic stress or elastic strain is a stress or strain within the elastic limit. Elastic Limit The least stress that will cause permanent set. Electroslag Welding - A welding process in which consumable electrodes aIt fed into a joint containing flux; the current melts the flux, and the flux in turn melts the faces of the joint and the electrodes, allowing the weld
metal to form a continuously cast ingot between the joint faces. Used in pressure vessel construction when back of the welding is not accessible. All butt welds joined by electroslag welding shall be examined radiographically for their full length. (Code UW-ll) (a) (6) Endurance Limit (Fatigue Strength) - By endurance limit of a material is usually meant the maximum stress which can be reversed an indefinitely large number of times without producing fracture. Erosion-Corrosion - Attack on a metal surface resulting from the combined effects of erosion and corrosion. Expansion Joint - A joint whose primary purpose is not to join pipe but to absorb that longitudinal expansion in the pipe line due to heat. Factor of Safety - The ratio of the load that would cause failure of a member or structure, to the load that is imposed upon it in service. Fatigue - Tendency of materials to fracture under many repetitions of a stress considerably less than the ultimate static strength. Fiber Stress - A term used for convenience to denote the longitudinal tensile or compressive stress in a beam or other member subject to bending. It is sometimes used to denote this stress at the point or points most remote from the neutral axis, but the term stress in extreme fiber is preferable for this pupose. Also, for convenience, the longitudinal elements or filaments of which a beam may be imagined as -composed are called fibers. Fillet Weld -
[¥:OU
1tks
A weld of approximately triangular cross section joining two surfaces approximately at right angles to each other. The effective stress-carrying area of a fillet weld is assumed to be the product of the throat dimension and the length of the weld. Fillet welds are specified by their leg dimension.
486 The throat dimension of an equal legged fillet weld is 0.707 times the leg dimension. Fillet welds may be employed as strength welds for pressure parts of vessels within the limitations given in Table UW-12 of the Code. The allowable load on fillet welds shall equal the product of the weld area (based on minimum leg dimension), the allowable stress value in tension of the material being welded, and a joint efficiency of 55010. (Code UW-18) The allowable stress values for fillet welds attaching nozzles and their reinforcements to vessels are (in shear) 49010 of stress value for the vessel material. (Code (UW-lS) Filler Metal - Material to be added in making a weld. Full Fillet Weld - A fillet weld whose size is equal to the thickness of the thinner member joined. Gage Pressure - The amount by which the total absolute pressure exceeds the ambient atmospheric pressure. GaIYanizinR - Applying a coating of zinc to ferrous articles. Application may be by hot dip process or electrolysis. Gas Welding - A group of welding processes wherein coalescence is produced by heating with a gas flame with or without application of pressure and with or without the use of filler metal. Gate Valve - A valve employing a gate, often wedge-shaped, allowing fluid to flow when the gate is lifted from the seat. Such valves have less resistance to flow than globe valves. Globe Valve - One with a somewhat globe shaped body with a manually raised or lowered disc which when closed rests on a seat so as to prevent passage of a fluid. Graphitization - Precipitation of carbon in the form of graphite at grain boundaries, as occurs if carbon steel is in service long enough above 775°F, and C-MQ steel above 875°F.
Graphitization appears to lower steei strength by removing the strengthening effect of finely disperse iron carbides (cementite) from grains. Fine-grained, aluminum-killed steels seem to be particularly susceptible to graphitization. Groove Weld -
A weld made by depositing filler metal in a groove between two members to be joined. Standard shapes of grooves: V, U and J. Each may be single or double. Stress values for groove welds in tension 74010 and in shear 60010 of the stress value of vessel material joined by the weld. (Code UW-lS)
Head - The end (enclosure) of a cylindrical shell. The most commonly used types of heads are hemispherical, ellipsoidal, flanged and dished (torispherical), coniCal and flat. Heat Treatment - Heat treating operation performed either to produce changes in mechanical properties of the material or to restore its maximum corrosion resistance. There are three principal types of heat treatment; annealing, normalizing, and post-weld heat treatment. High-Alloy Steel - Steel containing large percentages of elements other than carbon. Hydrogen Brittleness - Low ductility of a metal due to its absorption of hydrogen gas, which may occur during an electrolytic process or during cleaning. Also known as acid brittleness. Hydrostatic Test - The completed vessel filled with water shall be subjected to a test pressure which is equal to 1Y:z times the maximum allowable working pressure to be marked on the vessel or 1Y:z times the design pressure by agreement between the user and the manufacturer. (Code UG-99) Impact Stress - Force per unit area imposl.;d to material by a suddenly applied force. Impact Test - Determination of the degree of
487
resistance of a material to breaking by impact, under bending, tensile and torsion loads; the energy absorbed is measured by breaking the material by a single blow. Intermittent Weld - A weld whose continuity is broken by unwelded spaces. Isotropic - Having the same properties in all directions. In discussions pertaining to strength of materials, isotropic usually means having the same strength and elastic properties (modulus of elasticity, modulus of rigidity, Poisson's ratio) in all directions. Joint Efficiency - A numerical value expressed as the ratio of the strength of a riveted, welded, or brazed joim to the strength of the parent metal. Joint Penetration - The minimum depth a groove weld extends from its face into a joint, exclusive of reinforcement. Killed Steel - Thoroughly deoxidized steel, (for example, by addition of aluminum or silicon), in which the reaction between carbon and oxygen during solidification is suppressed. This type of steel has more uniform chemical composition and properties as compared to other types. Lap Joint ...
A welded joint in which two overlapping metal parts are .. '? joined by means of a fillet, plug or slot welds.
Layer or Laminated Vessel - A vessel having a shell which is made up of two or more separate layers. (Code UA-60) Leg -
See under Fillet Weld.
Letbal Substances - Poisonous gases or liquids of such a nature that a very small amount of the gas or of the vapor of the liquid is dangerous to life when inhaled. It is the responsibility of the user of the vessel to determine that the gas or liquid is lethal. (Code UW-2) Ligament - The section of solid material in a tube sheet or shell between adjacent holes. Lined Vessel - A vessel having a corrosion resistant lining attached intermittently to the
vessel wall. (Code UA-60) Liquid Penetrant Examination (PT). A method of nondestructive examination which provides for the detection of discontinuities open to the surface in ferrous and nonferrous materials which are nonporous. Typical discontinuities detectable by this method are cracks, seams, laps, cold shuts, and laminations. (Code UA-60) Loading - Loadings (loads) are the results of various forces. The loadings to be considered in designing a vessel: internal or external pressure, impact loads, weight of the vessel, superimposed loads, wind and earthquake, local load, effect of temperature gradients. (Code UG-22) Low-Alloy Steel - A hardenable carbon steel generally containing not more than about 1070 carbon and one or more of the following alloyed components: < (less than) 2070 manganese, < 4070 nickel, < 2070 chromium, 0.6070 molybdenum, and < 0.2070 vanadium. Magnetic Particle Examination (MT). A method of detecting cracks and similar discontinuities at or near the surface in iron and the magnetic alloys of Malleable Iron - Cast iron heat-treated to reduce its brittleness. The process enables the material to stretch to some extent and to stand greater shock. Material Test Report - A document on which the material manufacturer records the resufts of tests examinations, repairs, or treatments required by the basic material specification to be reported. (Code UA-60) Maximum Allowable Stress Value - The maximum unit stress permissible for any specified material that may be used in the design formulas given in the Code. (UG-23) Maximum Allowable Working Pressure - The maximum gage pressure permissible at the top of a completed vdisel in its operating position for a designated temperature. This pressure is based on the weakest element of the vessel using norminal thicknesses exclusive of allowances for corrosion and thickness required for loadings other than pressure. (Code UA-60)
488
Membrane Stress - The component of normal stress which is uniformly distributed and equal to the average value of stress .across the thickness of the section under consideration. Metal Arc Welding - An arc welding process in which the electrode supplies the filler metal to the weld. Modulus of Elasticity (Young's Modulus) The rate of change of unit tensile or compressive stress with respect to unit tensile or compressive strain for the condition of uniaxial stress within the proportional limit. For most, but not all materials, the modulus of elasticity is the same for tension and compression. For nonisotropic materials such as wood, it is necessary to distinguish between the moduli of elasticity in different directions. Modulus of Rigidity (Modulus of Elasticity in Shear) - The rate of change of unit shear stress with respect to unit shear strain, for the condition of pure shear within the proportional limit. Moment of Inertia of an Area (Second Moment of an Area) The moment of inertia of an area with respect to an axis is the sum of the products obtained by multiplying each element of the area by the square of its . distance from the axis. The Moment of Inertia (I) for thin walled cylinder about its transverse axis; I = 'If r't where r = mean radius of cylinder t = wall thickness Needle Valve - A valve provided with a long tapering point in place of the ordinary valve disk. The tapering point permits fine graduation of the opening. Neutral Axis - The line of zero fiber stress in any given section of a member subject to bending; it is the line formed by the intersection of the neutral surface and the section. Neutral Surface - The longitudinal surface of zero fiber stress in a member subject to bend-
ing; it contains the neutral axis of every section. Nipple - A tubular pipe fitting usually threaded on both ends and under 12 inches in length. Pipe over 12 inches long is regarded as cut pipe. Non-Pressure Welding - A group of welding processes in which the weld is made without pressure. Normalizing - Heating to about 100° F. above the critical temperature and cooling to room temperature in still air. Provision is often made in normalizing for controlled cooling at a slower rate, but when the cooling is prolonged the term used is annealing. Notch Sensitivity - A measure of the reduction in strength of a metal caused by the presence of a notch. Notch Strength - The ratio of maximum tensional load required to fracture a notched specimen to the original minimum crosssectional area." Notch Test - A tensile or creep test of a metal to determine the effect of a surface notch. Operating Pressure - The pressure at the top of a pressure vessel at which it normally operates. It shall not exceed the maximum allowable working pressure and it is usually kept at a suitable level below the setting of the pressure relieving devices to prevent their frequent opening. (Code UA-60) Operating or Working Temperature - The temperature that will be maintained in the metal of the part of the vessel being considered for the specified operation of the vessel (see UG-20 and UG-23). (Code UA-60) Oxidation or scaling of metals occurs at high temperatures and access of air. Scaling of carbon steels from air or steam is negligible up to l000°F. Chromium increases scaling resistance of carbon steels. Decreasing oxidation resistance makes austenitic stainless steels unsuitable for operating temperatures above 1500oF.
489
P-Number - The number of welding procedure-group. The classification of materials based on hardenability characteristic and the purpose of grouping is to reduce the number of weld procedures. (Code Section IX) All carbon steel material listed in the Code (with the exception of SA-612) are classified as P-No. I. Pass - The weld metal qeposited by one progression along the axis of a weld. Plasticity - The property of sustaining appreciable (visible to the eye) permanent deformation without rupture. The term is also used to denote the property of yielding or flowing under steady load. Plug Valve - One with a short section of a cone or tapered plug through which a hole is cut so that fluid can flow through when the hole lines up with the inlet and outlet, but when the plug is rotated 90°, flow is blocked. Plug Weld - A weld made in a circular hole in one member of a lap joint. The hole mayor may not be partially or comppletely filled with weld metal. For pressure vessel construction plug welds may be used in lap joints in rein~ forcements around openings, in non pressure structural attachments (Code UW-17) and for attachment of heads with certain restrictions. (Code Table UW-12)
r$J
condition of uniform and uniaxial longitudinal stress within the proportional limit. Porosity - Gas pockets or voids in metal. (Code UA-60) Postweld Heat Treatment - Heating a vessel to a sufficient temperature to relieve the residual stresses which are the result of mechanical treatment and welding. Pressure vessels and parts shall be postweld heat treated: When the vessels are to contain lethal substances, (Code UW-2) Unfired Steam Boilers (UW-2) Pressure vessels and parts subject to direct firing when the thickness of welded joints exceeds 5/8 in. (UW-2) When the carbon (P-No. I) steel material thickness exceeds 1Yl in. at welded connections and attachments (see Code Table UCS-56 for exceptions) . Preheating - Heat applied to base metal prior to welding operations. Pressure Relief Valve - A valve which relieves pressure beyond a specified limit and recloses upon return to normal operating conditions. Pressure Vessel - A metal container generally cylindrical or spheroid, capable of withstanding various loadings.
I
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"
Pneumatic Test - The completed vessel may be tested by air pressure in lieu of hydrostatic test when the vessel cannot safely be filled with water or the traces of testing liquid cannot be tolerated (in certain services). The pneumatic test pressure shall be 1.25 times the maximum allowable working pressure to be stamped on the vessel. (Code UG-H)() Poisson's Ratio - The ratio of lateral unit strain t4i) longitudinal unit strain, under the
Pressure Welding - A group of welding processes wherein the weld is completed by use of pressure.
Primary Stress - A normal stress or a shear stress developed by the imposed loading which is necessary to satisfy the simple laws of equilibrium of external and internal forces and moments. The basic characteristics of a primary stress is that it is not self-limiting. Primary stresses which considerably exceed the yield strength will result in failure or at least, in gross distortion. A thermal stress is not classified as a primary stress. Primary membrane stress is divided into .. general" and "local" categories. A general primary membrane stress is one which is so distributed in the structure that no redistribution of load occurs as a result of yielding. Examples of primary stress are: general
490
membrane stress in a circular cylindrical or a spherical shell due to internal pressure or to distributed live loads; bending stress in the central portion of a flat head due to pressure. Quench Annealing - Annealing an austenitic ferrous alloy by heating followed by quenching from solution temperatures. Liquids used for quenching are oil, fused salt or water, into which a material is plunged. Radiographing - The process of passing electronic radiations through an object and obtaining a record of its soundness upon a sensitized film. (Code UA-60) Radius of Gyration - The radius of gyration of an area with respect to a given axis is the square root of the quantity obtained by dividing the moment of inertia of the area with respect to that axis by the area. Random Lengths - A term indicating no specified minimum or maximum length with lengths falling within the range indicated. Refractory - A material of very high melting point with properties that make it suitable for such uses as high-temperature lining. Residual Stress - Stress remaining in a structure or member as a result of thermal or mechanical treatment, or both. Resistance Welding - A pressure welding process wherein the heat is produced by the resistance to the flow of an electric current.
teristic of a secondary stress is that it is self-limiting. Local yielding and minor distortions can satisfy the conditions which cause the stress to occur and failure from one application of the stress is not to be expected. Examples of secondary stress are: general thennal stress; bending stress at a gross structural discontinuity. Section Modnlu - The term pertains to the cross section of a beam. The section modulus with respect to either principal central axis i5 the moment of inertia with respect to that axis divided by the distance from that axis to the most remote point of the section. The section modulus largely determines the flexural strength of a beam of given material. Section Modulus (Z) of a thin walled cylinder (r>IOt) about its transverse axis: Z=r1Tt where r = mean radius of cylinder, in. t = wall thickness, in. SbeD - Structural element made to enclose some space. Most of the shells are generated by the revolution of a plane curve. In the terminology of this book shell is the cylindrical part of a vessel or a spherical vessel is called also a spherical shell. Shear Stress - The component of stress tangent to the plane of reference.
Scale - An iron oxide formed on the surface of hot steel, sometimes in the form of large sheets which fall off when the sheet is rolled.
Shielded Metal-Arc Welding An arc weldingprocess wherein coalescence is produced by heating with an electric arc between a covered metal electrode and the work. Shielding is obtained from decomposition of the electr6de covering. Pressure is not used and filler metal is obtained from the electrode.
Scarf - Edge preparation; preparing the contour on the edge of a member for welding.
Single-Welded Butt Joint - A butt joint welded from one side only.
Root of Weld - The bottom of the weld.
tightness.
Single-Welded Lap Joint - A lap joint in which the overlapped edges of the members to be joined are welded along the edge of one member.
Secondary Stress - A nonnal stress or a shear stress developed by the constraint of adjacent parts or by self-constraint of a structure. The basic charac-
Size of Weld penetration.
Seal Weld - Seal weld used primarily to obtain
Groove Weld: The depth of
491
Equal Leg Fillet Weld: the leg length of the largest isosceles right-triangle which can be inscribed within the fillet weld cross section. Unequal Leg Fillet Weld: The leg length of the largest right triangle which can be inscribed within the fillet weld cross section. Slag - A result of the action of a flux on nonmetallic constituents of a processed ore, or on the oxidized metallic constituents that are undesirable. Usually consist of combinations of acid oxides and basic oxides with neutral oxides added to aid fusibility. Slenderness Ratio - The ratio of the length of a uniform column to the least radius of gyration of the cross section. Slot Weld - A weld made in an elongated hole (slot) in one member of a lap joint, joining that member to that portion of the surface of the other member which is exposed through the hole. The hole f i ;. mayor may not be filled completely with weld metal.
Din I'
Specific GnYity - The ratio of the density of a material to the density of some standard material, such as water at a specified temperature, for example, 4°C or 60°F. or (for gases) air at standard conditions of pressure and temperature. Spot Welding - Electric-resistance welding in which fusion is limited to a small area directly between the electrode tips. Stability -of Vessels - (Elastic Stability) The strength of a vessel to resist buckling or wrinkling due to axial compressive stress. The stability of a vessel is severely affected by out of roundness. Stagsrered Intermittent Fillet Welds - Two lines of intermittent fillet weldin~ in a tee or lap joint, in which the increments of
welding in one line are staggered with respect to those in the other line. Static Head - The pressure of liquids that is not moving, against the vessel wall, is due solely to the "Static Head", or height of the liquid. This pressure shall be taken into consideration in designing vessels. Stmn - Any forced change in the dimensions of a body. A stretch is a tensile strain; a shortening is a compressive strain; an angular distortion is a shear strain. The word strain is commonly used to connote unit strain. Stress - Internal force exerted by either of two adjacent parts of a body upon the other across an imagined plane of separation. When the forces are parallel to the plane, the stress is called shear stress; when the forces are normal to the plane the stress is called normal stress; when the normal stress is directed toward the part on which it acts it is called compressive stress; when it is directed away from the part on which it acts it is called tensile stress. Stresses In Pressure Vessels - Longitudinal (meridional) S, stress Circumferential (hoop) S1 stress S, and S1 called membrane (diaphragm) stress for vessels having a figure of revolution Bending stress Shear stress Discontinuity stresses at an abrupt change in thickness or shape of the vessel. Stud - A threaded fastener without a head, with threads on one end or both ends, or threaded full length. (Code UA-60) Submerged Arc Welding - An arc welding process wherein coalescence is produced by heating with an arc or arcs between a bare metal electrode or electrodes and the work. The welding is shielded by a blanket of granular, fusible material on the work. Pressure is not used and filler metal is obtained from the electrode and sometimes from a supplementary
492 welding rod. Tack Weld - A weld made to hold parts of a weldment in proper alignment until the final welds are made. Tee Joint - A welded joint at the junction of two parts located approximately at right angles to each other in the form of aT.
(see UO-25). 3. The "nominal thickness" is the thickness selected as commercially availble, and as supplied to the manufacturer; it may exceed the design thickness. (Code UA-60) Throat - See under Fillet Weld.
Tensile Stress - Stress developed by a material bearing tensile load.
Tolerances - For plates the maximum permissible undertolerance is the smaller value of 0.01 in. or 6% of the design thickness. (Code UO-16) The manufacturing undertolerance on wall thickness of heads: pipes and pipefittings shall be taken into account and the next heavier commercial wall thickness may then be used.
Test - Trial to prove that the vessel is suitable for the design pressure. See Hydrostatic test, Pneumatic test.
U.M. Plate - Universal Mill Plate or plate rolled to width by vertical rolls as well as to thickness by horizontal rolls.
Tensile Strength - The maximum stress a material subjected to a stretching load can withstand without tearing.
Test Pressure - The requirements for determining the test pressure based on calculations are outlined in UO-99(c) for the hydrostatic test and in UO-lOO(b) for the pneumatic test. The basis for calculated test pressure in either of these paragraphs is the highest permissible internal pressure as determined by the design formulas, for each element of the vessel using nominal thicknesses with corrosion allowances included and using the allowable stress values for the temperature of the test. (Code UA-60) Thermal Fatigue - The development of cyclic thermal gradients producing high cyclic thermal stresses and subsequent local cracking of material. Thermal Stress - A self-balancing stress produced by a nonuniform distribution of temperature or by differing thermal coefficients of expansion. Thermal stress is developed in a solid body whenever a volume of material is prevented from assuming the size and shape that it normally should under a change in temperature. Thickness of Vessel Wan I. The "required thickness' is that computed by the formulas in this Division, before corrosion allowance is added (see UO-22). 2. The "design thickness' is the sum of the required thickness and the corrosion allowance
Ultrasonic Examination (UT) - a nondestructive means for locating and identifying internal discontinuitis by detecting the reflections they produce of a beam of ultrasonic vibrations (Code UA-60) Undercut - A groove melted into the base metal adjacent to the toe of a weld and left unfilled by weld metal. Unit Strain - Unit tensile strain is the elongation per unit length; unit compressive strain is the shortening per unit length; unit shear strain is the change in angle (radians) between two lines originally at right angles to each other. Unit Stress - The amount of stress per unit of area. Vessel- A container or structural envelope in which materials are processed, treated, or stored; for example, pressure vessels, reactor vessels, agitator vessels, and storage vessels (tanks). Weaving - A technique of depositing weld metal in which the electrode is oscillated from side to side. Weld - A localized coalescence of metal produced by fusion with or without use of filler metal, and with or without application of pressure.
493 Weld Metal - The metal resulting from the fusion of the base metal and the filler metal. Welding - The metal joining process used in making welds. In the construction of vessels the welding processes are restricted by the Code (UW -27) as follows: 1. Shielded metal are, submerged are, gas metal arc. gas tungsten are, plasma are, atomic hydrogen metal are, oxyfuel gas welding, electroslag, and electron beam. 2. Pressure welding processes: flash, induction, resistance, pressure thermit, and pressure gas. Welding Procedure - The materials, detailed methods and practices involved in the production of a welded joint. Welding Rod -
Filler metal, in wire or rod
form, used in the gas welding process, and in those arc welding processes wherein the electrode does not furnish the deposited metal. Wrought Iron - Iron refined to a plastic state in a puddling furnace. It is characterized by the presence of about 3 per cent of slag irregularly mixed with pure iron and about 0.5 per cent carbon. Yield Point - The lowest stress at which strain increases without increase in stress. For some purposes it is important to distingish between the upper yield point, which is the stress at which the stress-strain diagram first becomes horizontal, and the lower yield point, which is the somewhat lower and almost constant stress under which the metal continues to deform. Only a few materials exhibit a true yield point; for some materials the term is sometimes used as synonymous with yield strength.
494
INDEX Abbreviations ..................................... 466 Abrasion ............................................. 483 Absolute pressure .............................. 483 Access opening, tickness of.. ............. 140 Allowable load on saddle .................. 110 Allowable pressure ........................ 18-25 Allowable pressure, flanges ................ 28 Allowable stresses for non-pressure parts ........................ 449 Allowances of plate bending ............. 236 Alloy .................................................. 483 Anchor bolt design ........................ 77-84 Angle joint ......................................... 483 Angle valves ...................................... 366 definition ...................................... 483 Annealing ........................................... 483 API 650 tanks .................................... 204 API 12F tanks .................................... 203 Appurtenances, Preferred locations ....................... 241 Arc welding ....................................... 483 Area of circles .................................... 300 Planes ............................................ 258 Area of surface, Cylindrical shell head ................... 425 ASME flanged and dished head, allowable pressure .......... 20-24 Dimension of .............:.................. 335 External pressure ............................ 34 Internal pressure ....................... 20-24 Automatic welding ............................ 483 Backing .............................................. 483 Base ring design ............................ 79-83 Beam formulas ................................... 455 Bend allowances of steel plate ................................. 236 Bending of pipe and tube .................. 234 Bent pipe ............................................ 280 Boiler and pressure vessel laws .................................... 474 Bolted connections ............................ 463 Bolts, weight of ................................. 412 Brittle fracture ................................... 483 Brittleness .......................................... 483 Bushing .............................................. 483 Butt Weld ........................................... 483 Capacities of fabrication .................... 232 Carbon steel, properties of ................ 186 Center of gravity ................................ 452 Centigrade, conversion to fahrenheit .................................. 444 Centroid of an area ............................ 484 Chain intermittent fillet weld ...................................... 484
Check list for inspectors ................... 255 Check valves ..................................... 367 Definition ..................................... 484 Chemical plant piping ....................... 208 Chemical resistance of gaskets ..................................... 224 Metals ........................................... 224 Paints ........................................... 253 Chipping ............................................ 484 Circles, circumferences and areas of, ................................ 300 Circles, division of.. .......................... 289 Segments of ................................ 290 Circular plate, weight of ................... 404 Circumferences and areas of circles ...................................... 300 Circumferential stress ......................... 14 Clad vessel ........................................ 484 Code rules related to Services ....................................... 181 Thicknesses ................................. 182 Codes ................................................. 470 Combination of stresses ...................... 69 Combustible liquids .......................... 184 Common errors Detailing vessels .......................... 242 Complete fusion ................................ 484 Cone, allowable pressure, Internal .................................... 20, 24 External pressure ........................... 36 Frustrum of .................................. 276 To cylinder reinforcemenL ......... 159 Wall thickness for internal pressure ................. 20, 24 Conical section, Allowable pressure .................. 20, 24 External pressure ........................... 36 Wall thickness ......................... 20,24 Construction of vessels, Specification ................................ 195 Contraction of Horizontal vessels ......................... 99 Conversion, decimals of a degree ................................... 443 Degrees to radains ....................... 441 Factors ......................................... 446 Gallons to liters ........................... 439 Inches to millimeters ................... 431 Kilograms to pounds ................... 438 Liters to gallons ........................... 439 Millimeters to inches ................... 433 Pounds per sq. in. to kilograms per sq. centimeter ........ 440 Pounds to kilograms .................... 438 Radians to degrees ...................... 442
495
Sq. feet to sq. meters ................... 437 Sq. meters to sq. feet ................... 437 Corner joint ....................................... 484 Corrosion ................................... 215,484 Fatigue ......................................... 484 Corrosion resistant materials ............. 222 Creep .................................................. 484 Couplings .......................................... 468 Definition ..................................... 484 Length of .............................. 138, 139 Weight of ..................................... 413 Welding ........................................ 361 Cylinders, . partial volume of .................. 418,421 Cylindrical shell allowable Pressure .................................... 18,22 Area of surface ............................. 425 External pressure ........................... 32 Thickness for internal pressure ............................... 18, 22 Weight .......................................... 375 Damaging stress ................................ 484 Davit .................................................. 312 Decimals of a degree, conversion .................................... 443 Decimals of an inch ........................... 426 Decimals of a foot ............................. 426 Definitions ......................................... 483 Deflection ............................................ 68 Deformation, strain ........................... 484 Degrees to radians, conversion ......... 441 Description of materials .................... 192 Design pressure, definition ............... 484 internal ........................................... 15 external .......................................... 31 Design specification .......................... 195 steel structures ............................. 447 temperature .................................. 484 tall towers ....................................... 52 welded joints ........................ 174, 448 Detailing of pressure vessels ............. 240 Dimensions of heads ......................... 335 pipe ............................................... 330 Discontinuity .................. ........... 484, 485 Division of circles ............................. 289 Double welded butt joint ................... 485 lap joint ........................................ 485 Drop at intersection of nozzle and shell ....................................... 291 Ductility ............................................. 485 Earthquake ........................................... 61 map, of seismic zones .................... 64 Eccentric cone frustum ...................... 279 Eccentric load ...................................... 66
Eccentricity ........................................ 485 Efficiency of welded joint ................. 485 Elastic ................................................ 485 Elastic limit ........................................ 485 Elastic stability .................................... 67 Electroslag welding ........................... 485 Ellipsoidal head allowable pressure .................................... 18, 22 area of surface .............................. 425 dimensions of ............................... 335 external pressure ............................ 34 locating point on ...... .................... 293 partial volume of .......................... 422 wall thickness for internal pressure .................. 18, 22 Endurance limit ................................. 485 Engagement of pipe .................... ....... 235 Erosion ................................... ............ 485 Examination of welded joints ............ 177 Expansion joint .................................. 485 of horizontal vessels ...................... 99 of metals ....................................... 191 Extension of openings ....................... 128 External pressure ................................. 31 charts ........................................ 42-47 stiffening ring ................................. 40 Fabricating capacities ........................ 232 Fabrication tolerances ........................ 200 Factors, conversion ............................ 446 Factor of safety .................................. 485 Fahrenheit, conversion to centigrade ..................................... 444 Fatigue ............................................... 485 Fiber stress ......................................... 485 Filler metal ......................................... 486 Fillet weld .......................................... 486 Fittings ....................................... 126-127 welding ......................................... 361 dimensions ................................... 361 weight ........................................... 390 Flammable liquids ............................. 184 Flanged and dished head, allowable pressure .................... 20, 24 area of surface .............................. 425 dimensions of ............................... 335 external pressure ............................ 34 thickness for internal pressure ............................... 20, 24 Flanged fittings, pressuretemperature rating .......................... 28 Flange dimensions ................................... 341 pressure-temperature rating ........... 28 weight of ................................ ...... 395
496 Flat head wall thickness ...................... 26 Frustrum of concentric cone .............. 276 eccentric cone .............................. 279 Fuel gas piping .................................. 208 Full fillet weld ................................... 486 Gage pressure ..................................... 486 Gallons to liters, conversion .............. 439 Galvanized Sheet, weight of.. ............ 399 Galvanizing ........................................ 486 Gas transmission piping .................... 210 Gas welding ....................................... 486 Gaskets, chemical resistance of ......... 224 Gate valve .......................................... 486 dimensions ................................... 365 General specifications ....................... 243 Geometrical constructions ................. 268 formulas ....................................... 258 problems ....................................... 268 Girth seam formula .............................. 16 Globe valve ........................................ 486 dimensions ................................... 366 Graphitization .................................... 486 Groove weld ....................................... 486 Heads ................................................. 334 definition ...................................... 486 volume of ..................................... 416 weight of ...................................... 375 Heat treatment .................................... 486 Hemispherical head, allowable pressure .................................... 18, 22 area of surface .............................. 425 dimensions of ............................... 335 external pressure ............................ 34 wall thickness for internal pressure .................. 18, 22 High-alloy steel .................................. 486 Hinge .................................................. 314 Hydrogen brittleness .......................... 486 Hydrostatic test .................................. 486 Hydrostatic test presssure .................... 15 Hydrostatic test pressure for flanges ...................................... 28 Impact stress ...................................... 486 test ................................................ 486 Inches to millimeters, conversion .................................... 431 Inspection opening ............................ 123 Inspector's checklist ........................... 255 Insulation, weight of.. ........................ 414 Intermittent weld ................................ 487 Internal pressure ............................ 15, 18 Intersection of cone and cylinder .................................. 285 of cylinders ........................... 282-284
of cylinder and plane ................... 281 of cylinder and sphere ................. 286 of nozzle and shell, drop ............. 291 Isotropic ............................................ 487 Joint efficiencies ....................... 172, 174 definition ..................................... 487 Joint penetration ............................... 487 Junction of cone to cylinder ............. 159 Killed steel ........................................ 487 Kilogram to pounds, conversion ...... 438 Ladder ............................................... 315 Laminated vessel ............................... 487 Lap joint ............................................ 487 Laws, boiler and pressure vessel ...... 474 Layer or laminated vessel ................. 487 Leg support ..... ....... ................. ..... ..... 102 dimensions. ....... ......... ....... ........... 108 Length of arcs ................................... 297 Length of pipe and coupling for openings ......................... 138, 139 of stud bolts ................................. 237 Lethal substances .............................. 487 Lifting attachments ........................... 119 Lifting lug ......................................... 118 Ligament ........................................... 487 Lined vessel ...................................... 487 Liquid penetrant examination ........... 487 Liquid petroleum piping ................... 210 Literature ........................................... 479 Liters to gallons, conversion ............ 439 -Loadings ...................................... 13,487 Locating points on ellipsoidal heads .......................... 293 Locations of vessel components ....... 241 Long welding neck ............................ 341 Longitudinal stress .............................. 14 Low-alloy steel .................................. 487 properties of ................................ 187 Low temperature operations ............. 185 Lug, lifting ........................................ 118 Lug suppport ..................................... 109 Magnetic particle examination ......... 487 Malleable iron ................................... 487 Materials, description of ................... 192 properties of ................................ 186 test report ..................................... 487 of foreign countries ..................... 194 Maximum allowable pressure, flanges ........................................... 28 for pipes ....................................... 142 stress .............................................. 13 stress values ........... 16, 189, 190,487 working pressure ................... 15,487
497
wall thickness for internal pressure ...................... 148 weight of ...................................... 390 Pipe fitting symbols ........................... 369 Piping codes ....................................... 208 Plasticity ............................................ 489 Plate bending allowances .................. 237 Plate of unequal thickness, welding of .................................... 178 Plate thickness, relation to radiographic examination .............. 30 Plates, weight of ................................ 400 Platform ............................................. 318 Plug valve .......................................... 489 Plug weld ........................................... 489 Pneumatic test .................................... 489 Name plate ......................................... 317 Poisson's ratio .................................... 489 Needle valve ...................................... 488 Porosity .............................................. 489 Neutral axis ........................................ 488 Post weld heat treatment.. .................. 489 Surface ......................................... 488 Pounds per sq. inch to Nipple ................................................ 488 kilogram per sq. Non-pressure welding ....................... 488 centimeter, conversion ................. 440 Normalizing ....................................... 488 Pounds to kilogram, conversion ........ 438 strength ........................................ 488 Power piping code ............................. 208 test ................................................ 488 Preferred locations of vessel Nozzle details .................................... 244 components .................................. 241 Nozzle loadings ................................. 153 Power piping code ............................. 208 Nozzle neck thickness ............... 122.140 Preferred locations of vessel Nozzle weight of ............................... 413 components .................................. 241 Openings ............................................ 122 Preheating .......................................... 489 detailing of ................................... 244 _ Pressure of fluid .............. ..................... 29 extension of .................................. 128 Pressure-Temperature rating ............... 28 reinforcement of.. .................. 129-137 Pressure vessel ................................... 489 detailing ........................................ 238 weight of ...................................... 413 laws ............................................... 474 welding of .................................... 244 Operating pressure ....................... 15, 488 Pressure relief valve .......................... 489 temperature .................................. 488 Pressure welding ................................ 489 Optimum vessel size .......................... 272 Primary stress ..................................... 489 Organizations ..................................... 476 Properties of pipe ............ ................... 322 of sections .............................. ...... 450 Oxidation ........................................... 488 stainless stel ................................. 190 P-number ........................................... 489 of steel .......................................... 186 Packing, weight of ............................. 414 of tubes ......................................... 332 Painting of steel structures ................ 247 Partial volume of cylinders ....... 418,421 Quench annealing .............................. 490 heads ............................................ 422 Radians to degrees, conversion ......... 442 sphere ........................................... 422 Radiographing ................................... 490 Pass .................................................... 489 Radius of gyration ............................. 490 Petroleum refinery piping ................. 208 Radiographic examination ................. 174 Pipe bending .............................. 234, 280 relation to plate thickness .............. 30 dimensions of.. ............................. 330 Random length ................................... 490 engagement .................................. 235 Reaction of piping ............................. 153 length of for openings .......... 138, 139 Rectangular tanks .............................. 212 mitered ......................................... 280 Refractory .......................................... 490 properties of ................................. 322 Measures ............................................ 321 Measurement, metric system of.. ....... 427 Membrane stress ................................ 488 Metal arc welding .............................. 488 Metals, chemical resistance of .......... 224 Metric System of measurement ......... 427 Mist extractor .................................... 316 Mitered pipe ...................................... 280 Milimeters to inches, conversion .................................... 433 Minimum thicknss of shells and heads ........................... 182 Moduli of elasticity ................... 188, 478 Modulus of rigidity ........................... 488 Moment of inertia .............................. 488
498
Refrigeration piping .......................... 210 Reinforcement, Cone to cylinder ...... 159 Reinforcing of openings ........... 129, 137 Required wall thickness for internal pressure ................. 18-27 Residual stress ................................... 490 Resistance welding ............................ 490 Right triangles, solution of ................ 270 Ring joint flanges .............................. 356 Rings made of sectors ........................ 274 Root of weld ...................................... 490 Saddle design ....................................... 98 dimension ..................................... 100 Scale ................................................... 490 Scarf ................................................... 490 Schedule of openings ........................ 245 Screwed couplings ............................. 368 Seal weld ............................................ 490 Seamless head joint efficiency .......... 176 vessel section ............................... 176 Secondary stress ................................ 490 Section modulus ................................ 490 Sections, properties of ....................... 450 Segments of circles ............................ 290 Seismic load ......................................... 61 map of seismic zones ..................... 64 Services, Code rules .......................... 181 Shape of openings ............................. 122 Shear stress ........................................ 490 Sheet steel, weight ............................. 399 Shell, definition ................................. 490 volume of ..................................... 416 weights of ..................................... 375 Shielded metal arc welding ............... 490 Single-welded butt joint .................... 490 lap joint ........................................ 490 Size of openings ................................ 122 vessel ............................................ 272 weld .............................................. 490 Shop welded tanks ............................. 203 Skirt design .......................................... 76 openings ....................................... 319 Slag .................................................... 491 Slenderness ratio ................................ 491 Slot weld ............................................ 491 Solution of right triangles ................. 270 Specific gravities ............................... 415 Specific gravity definition ................. 491 Specification for design of vessels ...................................... 195 Specifications ..................................... 470 Sphere, allowable pressure ............ 18, 22 external pressure ............................ 34 partial volume of .......................... 412
wall thickness for internal pressure .............................. 18, 22 Spot welding ..................................... 491 Square feet to square meters, conversion ................................... 437 Square meters to square feet, conversion ................................... 437 Stability of vessels ............................ 491 Staggered intermittent fillet weld ..................................... 491 Stainless steel, properties of ............ 190 Stair ................................................... 313 Standards ........................................... 470 Static head ........................................... 29 definition ..................................... 491 Steel structures, design of.. ............... 447 Stiffening ring, external pressure ....... 40 construction ................................... 48 Strain .................................~ ............... 491 Stress and strain formulas ................. 448 Stress, definition ............................... 491 Stress values of materials.................. 189 Stresses, combination of ..................... 69 in cylindrical shell ......................... 14 in large horizontal vessels supported by saddles ................ 86 in pressure vessels ................. 13,491 Structures, design of ......................... 447 Structural members, welding of.. ...... 458 Stud ................................................... 491 Stud bolts, length of.. ........................ 237 Studding outlets ................................ 357 Subjects covered by literature .......... 481 Submerged arc welding .................... 491 Support of vessels, leg ...................... 102 lug ................................................ 109 saddle ............................................. 86 Swing check valves ........................... 367 Symbols for pipe fittings .................. 369 Tack weld .......................................... 492 Tall towers, design .............................. 52 Tanks, rectangular ............................. 212 Tanks, shop welded ........................... 203 for oil storage .............................. 204 Tee joint ............................................ 492 Temperature, conversion centigrade to Fahrenheit .............. 444 Tensile strength ................................. 492 stress ............................................ 492 Test .................................................... 492 Test pressure ..................................... 492 Test pressure, external ........................ 31 Thermal expansion of metals ............ 191 Thermal fatigue ................................. 492 Thermal stress ................................... 492
499
Thickness of vessel wall, definition ...................................... 492 code rules related to ..................... 182 for full vacuum ............................... 49 charts ........................................ 49-51 for internal pressure ................. 18-27 for nozzle neck ............................. 140 of pipe wall .................................. 148 Threaded and welded fittings ............ 126 Throat ................................................. 492 Tolerances, definition ........................ 492 Tolerances of fabrication ................... 200 Topics covered by literature .............. 481 Transition pieces ........................ 287-288 Transportation of vessels ................... 246 Tube, bending of ................................ 234 properties of ................................. 332 Types of welded joints ....................... 173 U. M. plate ......................................... 492 Ultrasonic examination ...................... 492 Undercut ............................................ 492 Unequal plate thickness welding of .................................... 178 Unit strain .......................................... 492 stress ............................................. 492 Valves ................................................ 365 Vessel, definition ............................... 492 Vessel, components, preferred locations ....................... 241 Vibration .............................................. 60 Volume of cylinders, partial ................................... 418, 421 of shells and heads ....................... 416 of solids ........................................ 264 Vortex breaker ................................... 320 Wall thickness for internal pressure .................................... 18-27
for pipes ....................................... 148 Weaving ............................................. 482 Weights ..................................... 321,374 bolts .............................................. 412 circular plates ............................... 404 couplings ...................................... 413 flanges .......................................... 395 galvanized sheet ........................... 399 insulation ...................................... 414 nozzles .......................................... 413 openings ....................................... 413 packing ......................................... 414 pipes and fittings .......................... 390 plates ............................................ 400 sheet steel ..................................... 399 shells and heads ........................... 375 vessels ............................................ 59 Weld, definition ................................. 492 metal ............................................. 493 sizes for openings ................ 124, 125 Welded joint categories ..................... 174 design of ....................................... 174 examination .................................. 177 locations ....................................... 174 Welded steel tanks ............................. 204 Welding, definition ............................ 493 fittings .......................................... 361 of nozzles ..................................... 244 procedure ...................................... 493 of pressure vessels ...................... 170 rod ................................................ 493 symbols ........................................ 179 Wind load ............................................ 52 Wind speed map ............................ 54, 57 Working temperature ......................... 488 Wrought iron ...................................... 493 Yield point ......................................... 493
