ASME-CODE – compliant to PED

Project – BOM

The Project module summarizes operational and test data, as well as the main parts of a pressure vessel including main geometrical data and used material in one working sheet. For the final calculation, the specified modules are adjusted and their data are connected to the working sheet.

The Project module determines which calculation code is used and according to which standard the material definition should be done.

Test pressure according to ASME VIII UG-99 and UG-100

Module UG99 can be used to calculate the maximum allowable test pressure according to ASME VIII-1 UG-99 for a calculation project with several chapters. After starting, two options can be selected:

1. Test pressure and material characteristics according to UG-99/UG-100:
2. Maximum allowable working pressure acc. to UG-99/UG-100

UG-27 Thickness of cylindrical and spherical shells under internal pressure

Under internal overpressure, cylindrical and spherical shells are subjected to tensile stresses. The wall must be sufficiently dimensioned so that this stress does not lead to the failure of a component.

The Ug27 module determines the required wall thickness and the allowable overpressure for the existing wall thickness. For the calculation of sections according to UG37, the required wall thickness at 100 % utilisation is also given.

UG-28 Thickness of shells and tubes under external pressure

Under external overpressure, cylindrical or spherical shells can fail due to plastic or elastic buckling. The ASME code contains material-temperature curves for the various material groups which can be used to determine the permissible external overpressure.

Module UG28 can be used to calculate the allowable external overpressure for cylindrical and spherical shells. The required wall thickness is determined iteratively.

UG-29 Reinforcement rings at cylindrical shells under external overpressure

The calculation of the necessary moments of inertia of the reinforcements for vessels under external overpressure is carried out for both cases taking into account

• the moments of inertia of the wall and the reinforcement
• the moment of inertia of the reinforcement alone.

In the module a comparison between the existing and the required moment of inertia is carried out, a violation of the strength condition is displayed.

The existing moments of inertia of reinforcement rings can be automatically transferred from the BIEG module.

UG-32 Dished ends under internal overpressure

Spherical, elliptical, torispherical or conical geometries can be used for heads or reducers. The deviation from the spherical shape is taken into account by form factors in the ASME code in the case of internal overpressure. For cones, the wall thickness at the widest diameter and the cross-section of the corner connection must also be checked.

The UG32 module determines the required wall thickness of elliptical, torispherical or hemispherical heads under internal pressure. In the case of dished heads (Kloepper type and Korbbogen type) the geometry is specified accordingly by the program.

For cones, the shell and the knuckle as well as the corner connection at the wide and narrow end can be calculated.

UG-33 Dished ends under external overpressure

Spherical, elliptical, torispherical or conical geometries can be used for heads or reducers. The deviation from the spherical shape is taken into account in the ASME code via a geometry factor for evaluation of the material-temperature curve in the case of external overpressure. For cones, the cross-section and, in the case of effective reinforcements, the area moment of inertia of the corner connection must also be checked.

The UG33 module determines the required wall thickness of the heads under external pressure. In the case of dished heads (Kloepper type and Korbbogen type) the geometry is specified accordingly by the program. For cones, the cross-section and the effective stiffening of the corner connection at the wide and narrow end can also be calculated.

UG-34 Flat ends or plates with flange moment

The different designs of flat ends or plates are taken into account in the calculation using coefficients. The special types are illustrated graphically. For bolted plates, the flange moment must also be taken into account.

UG-37 Openings in shells and heads

The Ug37 module can be used to design inserted or set-on nozzles with or without a reinforcing disc. For the calculation of adjacent openings, the values of the single nozzles are to be taken over.

In the case of openings in pressure vessels, the missing pressure-bearing shell surface must be replaced by surface reserves in the shell and nozzle or by a reinforcing plate. If the run-out lengths of two adjacent nozzles overlap, the existing area must still be sufficient to replace the cut-out area.

Flanges incl. Flange tables (AFLT – ANSI / ASME B16.5)

Flange connections must be leak-proof in installation / operating condition. The required bolt forces load the flange with a bending moment. For the different flange types, the stresses occurring can be determined from measurement curves on the basis .

The AFL module can be used to calculate inserted integral flanges and loose flanges / loose flanges with collar or without tapered shoulder. For the installation condition a design for the max. bolt force is possible. The required auxiliary variables are displayed.

ANSI

The ANSI standard B36.10 defines the dimensions of steel pipes. The pipes are designed to withstand static loads caused by internal pressure in accordance with ASME/ANSI B31.3.

The ANSI module determines the pipe dimensions according to ANSI B36.10 and the required wall thickness according to ASME/ANSI B31.3. Pipe bends are taken into account.

APY – flat face flanges with metal-to-metal contact outside the bolt circle according ASME BPVC Appendix Y

Flange Class I, A=16 in. = 406.4 mm, B = 10 in. = 254 mm, C = 14 in. = 355.6 mm, G = 11 in. = 279.4 mm, g0 = g1 = 0.375 in. = 9.525 mm, allowable stress Szul = 131 MPa, Internal pressure P = 700 psi = 4.826 MPa

Y1/Y2 = (A-B+g0)/(A-C+g0) = (406.4–254+9.525) / (406.4-355.6+9.525) = 162/ 60.3 = 2.7

Required flange thickness:

acc. to APY: t = 28.58 mm = 1.125 in

acc. to AD-B8: t=45 mm (Y1/Y2 = 2.7)

ATB spherical dished heads according to Appendix 1 – 6

In the case of spherically dished heads, the greatest stress lies in the transition area to the spherical dome and in the flange. Appendix 1-6 to the ASME Code sets out calculation equations for the various forms of design

The ATB module determines the required wall thickness of spherical dished heads and the required flange thickness for internal and full face gaskets. With dished heads without additional flange rings, clamp bolts are also considered.

TEB2 Calculation of pipe bends and T-pieces according to ANSI / ASME B31.3

The module calculates the stress profile of a pipe bend or a T-piece according to ASME.

The material database is used to compare the calculated stresses with the allowable stresses of the selected material.

Design of tube sheets according to ASME BPVC UHX

The module package UHX is divided into three modules for U-tube, fixed and floating tubesheet heat exchangers acc. section UHX of the ASME BPVC Part VIII-1. The package comprises:

• UHXa module: U-tubesheets acc. UHX-12
• UHXb module: Fixed tubesheets acc. UHX-13
• UHXc module: Floating tubesheets acc. UHX-14
• The required calculation cases 1-7 for shell or tube side pressure and thermal expansion.
• Input of the configuration (a-f) for fixed tubesheets and (A-D) for floating tubesheets.
• Calculation of the operation and test cases
• Detailed help file in Adobe PDF format including all examples acc. ASME-UHX-20