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### Pressure Vessel Pipe Shell Design Tool

Pressure Vessel Calculators

Circumferential Stress (Longitudinal Joints).

Use this calculator (per. UG-27) when the thickness does not exceed one-half of the inside radius, or P does not exceed 0.385SE, the following basic formulas apply:

Note: Longitudinal Stress (Circumferential Joints) design should be design checked as well

 Wall thickness (t) Pressure (P)  Variables: D [in] - outside diameter tn [in] - nominal wall thickness Ca [in] - corrosion allowance S [psi] - allowable material stress El -  Weld seam efficiency (circumferential stress) U1 [%] - undertolerance allowance (typ. 12.5%) P [psi] - internal pressure maximum Required Thickness: tr [in] = Thickness Check Maximum Pressure: Po [psi] = Operating Pressure Check Variables (See  nomenclature below): U2 [in] = t*U1 = nt [in] = t-Ca-U2 = Ri [in] = Do/2-nt =

Where:

E = joint efficiency for, or the efficiency of, appropriate joint in cylindrical or spherical shells, or the efficiency of ligaments between openings, whichever is less.
For welded vessels, use the efficiency specified in UW-12. For ligaments between openings, use the efficiency calculated by the rules given in UG-53.

P = internal design pressure (see UG-21)

R = inside radius of the shell course under consideration. (For pipe, the inside radius R is determined by the nominal outside radius minus the nominal wall thickness.)

S = maximum allowable stress value (see UG-23 and the stress limitations specified in UG-24)

t = minimum required thickness of shell

U1 = Undertolerance allowance  (%) typically 12.5%

U2 = Adjusted thickness by Undertolerance (U1 x t)

nt =  Nominal thickness adjusted for corrosion and undertolerance, (= t - Ca - U2)

R = Radius, (=D/2 - t)

tr = Required design thickness

References: ASME Boiler and Pressure Vessel Code

Contributed by:

Harsh Murugesan
Pune, Maharashtra India