ASME Boiler & Pressure Vessel Code VIII/Div.1compliant to Pressure Equipment Directive (PED) 
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Pressure vessel design according ASMEThe internationalization of industry and economy requires also the application of foreign calculation standards. For the design of pressure vessels, the American standard ASME VIII, Div 1 (Boiler & Pressure Vessel Code) is worldwide approved. For heat exchangers, the standards of the Tubular Exchanger Manufactures Associations are often used. Since 2005 section UHX of ASME BPVC part VIII1 is used. The program packages provides the user with the strength calculation of pressure vessel components, as cylindrical, spherical and, conical shells, heads, plates and flanges according to ASME VIII, Div. 1, as well as the calculation of heat exchanger tube sheets according to UHX or TEMA. A large material data base is included. 

It comprises more than 4400 materials of American and German standards, which are specified in detail in the calculation modules. Furthermore, a project sheet is available, in which all items for the calculations can be saved. The documentation ensues with the authoritative equations, so that each calculation can be reconsidered. The LVExcel AddIn enables you to transfer values from an EXCEL sheet to an LV module or calculation results from the LV program to an EXCEL sheet. You can use existing EXCEL calculations, while integrating a complete vessel calculation. 
The LV package comprises the following modules:
Project sheet AD, UG27  UG28  UG29  UG32  UG33  UG34  UG37  UHXa  UHXb  UHXc  TEB2  AFL AFLT  ATB  material data base
Additional information concerning calculation, tips, hints and notes about deficiencies of the code can be displayed dynamically by pressing the InfoBrowser button. 
Ug 99 module Try Buy  
Test pressure according ASME VIII UG99
Module UG99 calculates the maximum allowable test pressure acc. ASME VIII1 UG99 for a calculation project with multiple chapters. After start, two options can be selected:


Work sheet / Project list With the AD module, the operating and test conditions as well as the essential components of a pressure vessel, with its principal dimensions and the employed materials, can be collected in a form. For the calculation, the required modules will be implemented and connected with data of the form. 
Cylinders and spheres under internal pressure Cylindrical and spherical shells under internal overpressure are loaded by tensile stress. In order to avoid failure of the component, the wall must be sufficiently dimensioned. The UG27 module determines the required wall thickness of cylindrical or spherical shells under internal pressure as well as the allowable overpressure for a given wall thickness. For the calculation of openings, the required wall thickness for a usage factor of 100% is presented. 

Cylinders and spheres under external pressure Cylindrical or spherical shells under external overpressure can fail by plastic or elastic buckling. Materialtemperaturecurves for different material groupings are indicated in the ASMECode, which permit to determine the allowable external overpressure. The allowable external overpressure for cylindrical and spherical shells can be calculated with the module UG28. The required wall thickness is determined by iteration. 
Reinforcement rings at cylindrical shells It serves for the calculation of the necessary moments of inertia of reinforcements for vessels under external overpressure. The calculation is performed for the following two cases:
With this module, a comparison of the actual and the necessary moment of inertia will be carried out, and a violation of the strength condition will be reported. The actual moments of inertia of reinforcement rings can automatically be transferred from the BIEG module. 

Dished ends under internal overpressure For heads or reductions, spherical, elliptical, torispherical or conical geometries can be used. In the ASME code, the deviation from the spherical form is considered by form factors. For cones, the wall thickness of the largest diameter and the cross section of the angle joint must be verified. The UG32 module determines the required wall thickness of elliptical, torispherical or semispherical heads under internal pressure. For torispherical and semiellipsoidal heads, the geometric relations for a spherical torus are included. For cones, the shell and the knuckle as well as the angle joint can be calculated at the large and small end. 
Dished ends under external overpressure For heads or reductions, spherical, elliptical, torispherical or conical geometries can be used. In the ASME code, the deviation from the spherical form for external overpressure is considered by geometry factors for the evaluation of the materialtemperature curves. For cones, the cross section and for effective reinforcements the moment of inertia of the angle joint must be checked. The UG33 module determines the required wall thickness of elliptical, torispherical or semispherical heads under external overpressure. For torispherical and semiellipsoidal heads, the geometric relations for a spherical torus are included. For cones, the cross section and the effective reinforcement of the angle joint at the large and small end can be calculated. 

Flat ends or plates with flange moment The different types of flat ends or plates are considered by factors in the calculation. For bolted plates, the flange moment must also be included. The UG34 module determines the required wall thickness of flat ends and plates with and without moments. The form factor is determined by specification of the type. The special types are illustrated graphically. 
Openings in shells and heads For openings in pressure vessels, the missing pressuresupporting shell area must be replaced by an extension at the shell or the nozzle or by a reinforcement pad. When the runout lengths of two adjacent nozzles overlap, the existing area must still be sufficient to replace the opening area. With the UG37module, inserted and seton nozzles with and without stiffening ring can be designed. For the calculation of adjacent openings, the values of the single nozzles can be used. 

Flanges incl. flange tables acc ANSI / ASME B16.5 (AFLT) Flange joints must be tight under installation as well as operating conditions. The required bolt forces for this purpose apply a bending moment to the flange. For the different flange types, the existing stresses can be determined by empirical curves using the geometric relations. With the AFL module , slipon integral flanges and loose flanges as well as lapped type flanges or flanges without conical hub can be calculated. For the installed condition, a design for the maximum bolt force is possible. All necessary design values for the calculation are listed. 
Spherical dished heads acc. appendix 1  6 For dished heads, the maximum stress occurs in the transition region of the spherical shell and in the flange. In appendix 16 of the ASME standard, calculation formulas are given for different design types. The ATB module determines the required wall thickness of spherical dished heads and the required flange thickness for internal and full face gaskets. For dished heads without additional flange rings, clasp bolts are also considered. 

Calculation of the maximum allowable test pressure. Calculation of allowable load cycles. 

Calculation of pipe bends and tees according to ANSI/ASME B31.3 Part B31 of the ASME standard enables the user to design and construct pipework systems safely. Chapter TEB 2 includes pipe bends and tees under influence of external moments. The calculated stresses are compared with the allowable stress of the chosen material with help of the material data base. 
Design of Tubesheets acc. ASME BPVC UHX The module package UHX is divided into three modules for Utube, fixed and floating tubesheet heat exchangers acc. section UHX of the ASME BPVC Part VIII1. The package comprises:


Selection and documentation of materials for the design of pressure vessels The program determines the allowable material properties dependent on temperature, workpiece geometry, regulation standard and delivery standard. All values are displayed on screen and may be printed, copied into the clipboard, saved as a file (e.g. for further processing in Microsoft WORD) or forwarded to any of our calculation modules like AD 2000 / EN / TRD / ASME. 
The program is bilingual. You can switch from German to English and vice versa. 

ASME VIII Div.1 module package incl. material data basePackage price (1 licence) : see price listFor listing of all included modules see price list Printing in German and English included 

Modul APY Try Buy  
Calculation of flat face flanges with metaltometal contact outside the bolt circle according ASME BPVC Appendix Y ExampleFlange 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 = (AB+g0)/(AC+g0) = (406.4–254+9.525) / (406.4355.6+9.525) = 162/ 60.3 = 2.7 Required flange thickness:


Seismic loading per Uniform Building Code 1997 The UBC module determines the following forces and moments for columns (as well as vertical storage tanks, chimneys, etc.) caused by earthquakes:
