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Discussion
and References
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Information about Wall
thickness calculation of straight pipes under external pressure:
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ASME Section VIII Div 1
paragraphs UG-28, UG-29 and UG-30
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Tables and Standards
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ASME Section VIII Div 1 paragraph UG-28, Thickness of Shells and
Tubes under External Pressure
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ASME Section VIII Div 1 paragraph UG-29, Stiffening Rings for
Cylindrical Shells Under External Pressure
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ASME Section VIII Div 1 paragraph UG-30, Attachment of
Stiffening Rings
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ASME Sec. II
D Fig. G, Geometric Chart for Components Under External or Compressive
Loadings (All Materials)
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ASME Sec. II D Fig. CS, Chart for Determining Shell Thickness of
Components Under External Pressure Developed for Carbon or Low Alloy Steel
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ASME Sec. II D Fig. HA, Chart for Determining Shell Thickness of
Components Under External Pressure Developed for Austenitic Steel
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ASME Sec. II D Fig. HT, Chart for Determining Shell Thickness of
Components Under External Pressure Developed for Quenched and Tempered Low
Alloy Steel
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ASME Sec. II
D Table TM-1 ( Modulus of Elasticity,
E )
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ASME
B36.10M-Welded and Seamless Wrought Steel Pipe
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ASME
B36.19M-Stainless Steel Pipe
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Cylinders having Do/t
values ≥ 10
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Step 1. Assume a value for t and determine the ratios L/Do and
Do/t.
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Step 2. Enter Figure G in Subpart 3 of Section
II, Part D at the value of L/Do determined in Step
1. For
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values of L/Do greater than 50,
enter the chart at a value of L/Do = 50. For values of L/Do less
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than 0.05, enter the chart at a
value of L/Do = 0.05.
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Step 3. Move
horizontally to the line for the value of Do /t determined in Step 1. Interpolation may be
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made for
intermediate values of Do/t; extrapolation is not permitted. From this point
of
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intersection
move vertically downward to determine the value of factor
A.
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Step 4. Using
the value of A
calculated in Step 3,
enter the applicable material chart in Subpart 3 of
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Section II,
Part D for the material under consideration. (See
figures CS for Carbon and Low Alloy
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Steel and HT for Ferritic Steels with Properties Enhanced by
Heat Treatment). Move vertically to
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an
intersection with the material/temperature line for the design temperature
(see UG-20).
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Interpolation may be made between lines for intermediate temperatures.
If tabular values in
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Subpart 3 of
Section II, Part D are used, linear interpolation or any other rational
interpolation
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method may
be used to determine a B
value that lies between two adjacent tabular values for a
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specific
temperature. Such interpolation may also be used to determine a B value at an
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intermediate
temperature that lies between two sets of tabular values, after first
determining
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B values for each set of tabular
values.
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In cases
where the value of A falls to
the right of the end of the material/temperature line,
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assume an
intersection with the horizontal projection of the upper end of the material/
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temperature
line. If tabular values are used, the last (maximum) tabulated value shall be
used.
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For values
of A falling to the left of
the material/temperature line, see Step 7.
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Step 5. From the intersection
obtained in Step 4,
move horizontally to the right and read the value of
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factor B.
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Step 6. Using this value of B, calculate the value of the
maximum allowable external working pressure
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Pa using the following equation:
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Pa =
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4B
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3(Do/t)
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Step 7. For values of A falling to the left
of the applicable material/temperature line, the value of Pa can be
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calculated
using the following equation:
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Pa =
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2AE
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3(Do/t)
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If tabular values are used, determine B as in Step 4 and apply it to the equation in Step
6.
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Step 8. Compare the calculated value of Pa
obtained in Step 6 or
Step 7 with P. If Pa is smaller than P,
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select a
larger value for t and repeat the design procedure until a value of Pa is obtained that is
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equal to or
greater than P.
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The
parameters in the wall thickness calculation of straight pipes under external
pressure
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equations above are:
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A = factor determined from Figure G
in Subpart 3 of Section II, Part D and used to enter the
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applicable material chart in Subpart 3
of Section II, Part D. For the case of cylinders having
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Do/t values less than 10, see (c)(2).
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B = factor determined from the
applicable material chart or table in Subpart 3 of Section II,
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Part D
(Figures CS, HA, HT) for maximum design metal temperature [see
UG-20(c)]
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Do = outside diameter of
cylindrical shell course or tube.
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E = modulus of
elasticity of material at design temperature. For external pressure design in
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accordance with
this Section, the modulus of elasticity to be used shall be taken from the
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applicable
materials chart in Subpart 3 of Section II, Part D. (Interpolation may be
made
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made between lines
for intermediate temperatures.)
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L = total length, in. (mm), of a tube between
tubesheets, or design length of a vessel section
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between lines of
support (see Figure UG-28.1). A line of support is:
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(a) a circumferential
line on a head (excluding conical heads) at one‐third the depth of the
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head from the head
tangent line as shown on Figure UG-28;
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(b) a stiffening ring
that meets the requirements of UG-29;
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(c) a jacket closure of a
jacketed vessel that meets the requirements of 9-5;
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(d) a cone‐to‐cylinder
junction or a knuckle‐to-cylinder junction of a toriconical head or
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section that
satisfies the moment of inertia requirement of 1-8.
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P = external
design pressure [see Note in UG-28 (f)].
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Pa = calculated
value of maximum allowable external working pressure for the assumed
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assumed value of
t, [see Note in UG-28(f)].
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t = minimum
required thickness of cylindrical shell or tube, or spherical shell, in. (mm)
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