CalQlata's pressure vessel calculator determines the minimum permissible wall thickness(es) or maximum permissible pressure(s) for spherical or cylindrical pressure vessels and their heads (Fig 1) that ...

... are subject to internal pressure, or

... subject to external pressure, and

... conforms to ASME VIII, Division 1 design code

CalQlata's pressure vessel calculator does not include non-circular pressure vessels

The minimum required wall thickness of pressurised spheres and cylinders could be determined using classical theory but this is not normally considered appropriate for the safety of pressure vessels, which usually contain considerable levels of stored energy⁽¹⁾ and are frequently in close proximity to operating personnel. Moreover, physical collapse due to external pressure is always as a result of elastic instability and far too difficult to predict using general mathematical principles. ASME's considerable long-term experience provides far greater confidence in minimising the likelihood of unexpected collapse, given certain design criteria and limitations.

Fig 1. Pressure Vessel

The cross-section of any internally or externally pressurised vessel (container) should be circular for maximum pressure-carrying capacity and/or stability. Moreover, it should have no irregularities, corners or flat surfaces.

A pressure vessel is a container of any size and shape that will maintain its integrity (but not necessarily its size and shape) against an internally or externally pressurised fluid. A properly designed pressure vessel is one that will do so with no risk of damage, and the ASME VIII design code is generally considered to be the most appropriate means of achieving this.

Any longitudinal container will naturally try to form a cylinder under sufficient internal pressure. Its length will have no effect on stresses induced in an internally pressurised vessel other than those induced by its support.

Pressure Vessels calculates the wall thickness of plain cylinders of same material and equal wall thickness throughout. If you wish to evaluate cylindrical pressure vessels of different diameter and material the wall thickness of each section should be calculated separately. Conical Head calculations may be used to evaluate conical transitions between each diameter variation, along with any necessary reinforcement.

ASME VIII only considers membrane stresses (longitudinal and circumferential) in a cylindrical vessel, i.e. radial stresses are ignored, which is considered reasonable given that the maximum radial stress (equal to the internal pressure) is insignificant compared to membrane stresses in a thin-walled cylinder.

Cylindrical vessels will always need a thicker wall than a sphere for any given diameter and design pressure.

Fig 2. Typical Heads

Any bulk container will naturally try to form a spherical shape under sufficient internal pressure.

Pressure Vessels calculates the wall thickness of plain spheres of same material and equal wall thickness throughout.

ASME VIII only considers membrane stresses (circumferential) in a spherical vessel, i.e. radial stresses are ignored, which is considered reasonable given that the maximum radial stress (equal to the internal pressure) is insignificant compared to membrane stresses in a thin-walled cylinder.

Spherical vessels will always need a thinner wall than a cylinder for any given diameter and design pressure, which is why very large pressure vessels tend to be spherical.

A cylindrical vessel head is a closure, lid or cap (Fig 2) of consistent material and wall thickness throughout except as described in **Skirt** and **Knuckle** below

**Skirt** is a cylindrical section that forms the interface to the cylinder or connection flange, the wall thickness of which should be at least the same as the vessel to which it is attached. All head volumetric calculations include a skirt length equal to the minimum value recommended by ASME of;

3 x wall thickness + half an inch.

**Knuckle** is a radiused transition between the head and the skirt of diameter at least 6% of the skirt diameter. Whilst the minimum calculated material thickness for transition knuckles according to the ASME VIII design code is generally less than the calculated minimum wall thickness for the head and cylindrical vessel, Pressure Vessels assumes this wall thickness to be the same as its head for volumetric calculations.

**Hemispherical** is a hemisphere with the same diameter as its skirt. No knuckle is required for these heads.

**Ellipsoidal** is half an ellipse where the head depth (minor axis) is equal to one quarter of the skirt diameter (major axis). No knuckle is required for these heads.

**Torispherical** has a crown (segment of a sphere) radius equal to the skirt diameter and a transition knuckle.

**Toriconical** is a simple cone with a knuckle transition at its skirt. ASME VIII does not limit the included angle of internally pressurised toriconical heads⁽²⁾

**Conical** is a simple cone that finishes at the vessel with a sharp transition. No knuckle is required for these heads but reinforcement may be required inside the interface. ASME VIII recommends that the included angle of internally pressurised conical heads does not exceed 60°⁽²⁾

The design pressure of any pressurised container is the difference between the internal and external pressure. For example; if a pressure vessel is exposed to an internal pressure of 100psi and an external pressure of 35psi, the design pressure for the vessel will be an internal pressure of 65psi (65 = 100 - 35)

Internal and external pressures should include the effects of head-pressure (pressure due to fluid depth), especially if the pressurising fluid is a liquid, and as head-pressure varies with depth the design pressure at the top of a liquid container need not be as great as that at its base.

For example; if a 500 inch diameter vessel is 90% filled with a fluid of density 0.0362lb/in³ and an over-pressure of 30psi is applied at the surface of the liquid, the maximum pressure at the top of the vessel will be 30psi whilst the maximum pressure at its base will be 46.29psi

(46.29 = 90% x 500 x 0.0362 + 30)

A shell or cylinder of constant material quality and wall thickness exposed to internal pressure will always equalise hoop, radial and longitudinal stresses throughout⁽³⁾, and failure will occur due to the combined effect of these stresses exceeding UTS.

Maximum possible pressure without inducing permanent deformation will occur immediately prior to the combined stress reaching yield.

Maximum allowable pressure is that which induces an allowable stress (σₐ), which is a specified fraction (< 1.0) of yield stress and generally referred to as material utilisation.

A shell or cylinder of constant material quality and wall thickness exposed to external pressure will always deform as a result of elastic instability⁽⁴⁾. Failure will occur when a change in shape is sufficient to concentrate stresses such that yield stress is exceeded locally prior to expectations.

In all vessel shapes, the level of instability is entirely due to the ovality of the manufactured section. The greater the out-of-roundness, the quicker⁽⁵⁾ the shell will collapse.

Fig 3. Three I-Beam Stiffening Rings

Internal and/or external stiffening rings (Fig 3) increase elastic stability and are often installed at regular intervals in externally pressurised vessels to minimise wall thickness. You can minimise total vessel weight by optimising stiffener; material, section and longitudinal spacing. However, to eliminate galvanic corrosion and improve weldability the pressure vessel calculator assumes stiffener material to be the same as that of the vessel wall.

Stiffeners are added to internally pressurised vessels only to accommodate localised loading due to supports, closures, openings, etc., they will not affect wall thickness.

Reinforcement stiffeners are not included in vessel volume calculations.

As all pressure vessels must to be welded using certified materials and coded welders, weld joint factors (WJF) between 0.9 and 1.0 are the norm in their design.

Whilst there is little to be gained from varying the wall thickness of small pressure vessels and those that contain gas, the weight and cost of large vessels and those that contain liquids can be lessened significantly by reducing the wall thickness with head-pressure (see **Pressure** above). Moreover, the lower centre of gravity of large pressure vessels with a wall thickness that reduces with height will improve stability during an earthquake. This technique may be applied to both cylindrical and spherical vessels.

The world's most recognised design code for pressure vessels comprises two Divisions;

Division 1 (mandatory rules): For all pressure vessels including those covered by Division 2, and;

Division 2 (alternative rules): For fixed pressure vessels

The ASME VIII code provides design, manufacture and inspection rules for all pressure vessels and their head(s) along with the requirements for shape variations, nozzles, closures, openings and reinforcement.

CalQlata's pressure vessel calculator includes cylindrical and spherical shells and heads according to Division 1, Part UG and Appendices 1 & 5.

Included in the code is a single 3D plot (Dₒ/t vs L/Dₒ vs A for externally pressurised vessels) used to identify ASME's Factor A, along with about 60 material charts (Appendix 5, Fig 5-UCS-28.1 to UCD-28) that identify ASME's Factor B (and elastic moduli) for various materials at specific temperatures.

For maximum accuracy, CalQlata has mathematically modelled each plot on every chart, all of which have been included in the pressure vessel calculator along with interpolation.

This sub-section (Fig 5) applies only to pressure vessels exposed to external pressure.

Refer to **Mandatory Appendix 5, Fig 5 (material charts)** below for material chart titles

Fig 4. ASME VIII Fig 5 UCS-28.6 @ 300°F

Fig 5 titles refer to the following materials:

UCD: Sub-section C, Ductile Cast Iron

UCI: Sub-section C, Cast Iron

UCS: Sub-section C, Carbon Steel

UHA: Sub-section C, Austenitic Stainless Steel

UHT: Sub-section C, Heat-Treated Carbon Steel

UNF: Sub-section C, Non-Ferrous Metal

The plots included in this group of ASME figures are logarithmic interpretations of a modified version of the stress-strain curve for each metal concerned. The horizontal axis (A) is base 10 and the vertical axis is a natural base

Logarithmic and non-logarithmic versions of the plot for UCS-28.6 @ 300°F are provided in Fig 4 for comparison purposes, where it can be seen that above a relatively low stress (B) a minor increase is expected to induce a significantly greater strain (A) than would otherwise be expected for the same material in tension or linear compression. ASME expects the maximum permissible stress in an externally pressurised vessel manufactured from this metal to be approximately a ¼ of that for an internally pressurised vessel.

I.e. 'A' is nominally defined by ASME as; 0.125÷(Dₒ/t)⁽⁶⁾. The relationship 'Dₒ/t' is the reciprocal of strain in a curved vessel wall (e = y/R), where 'Dₒ' is the outside diameter of the vessel, 'R' is its radius, 't' is its wall thickness and 'y' represents half the wall thickness or the distance from the neutral axis to the outer fibre of the vessel wall. Therefore, 'A' represents ⅛ᵗʰ the expected strain.

Twice the value of Factor 'B' is used in the allowable stress calculations⁽⁶⁾. Therefore applying one eighth of the strain with twice the stress means that ASME expect elastic instability to occur at one quarter of the material's tensile yield stress.

You are permitted to use any portion of each plot. The maximum value indicated for 'B' on any plot is regarded by ASME as the yield stress associated with elastic instability. Any further increase in 'B' and you can expect elastic instability to increase the risk of localised plastic strain with little increase in stress (see Fig 4)

The maximum allowable stresses are similarly reduced for all ASME VIII-Fig 5 metals used in the manufacture of externally pressurised vessels.

Fig 5. UCS-28.6 @ 300°F

You can verify CalQlata's mathematical modelling of ASME's plots for factor 'B' (Division 1, Appendix 5, Figs UCS-28.1 to UCD-28) using the co-ordinates provided below the 'Output Data' in the Data Listing window (Fig 5). One plot is provided where interpolation has been unnecessary, otherwise two plots are provided; one at the temperature above that entered and one below.

Verification using your preferred spreadsheet (e.g. Microsoft's Excel) can be performed as follows:

1) Scan-Copy the appropriate Fig-5 chart from ASME VIII and Insert into a worksheet

2) Copy one set of co-ordinates from the pressure vessel calculator

3) Paste the co-ordinates into the same worksheet as the copied chart image (1 above)

4) Select the co-ordinates

5) Select menu item "Insert" > "Chart" > "Scatter" > "with straight lines" (generate the chart)

6) Set the horizontal axis to logarithm base 10

7) Set the vertical axis to logarithm base 2.7

8) Drag the plot over the copied chart image (1 above)

9) Resize the generated chart (5 above) to fit the axes of the copied chart image (1 above)

You may repeat the above procedure for the second set of co-ordinates when provided.

An example verification plot is provided in Fig 5 where the verification plot (pale-blue dotted line) is overlaid ASME's plot (pink line).

What wall thickness(es) would be acceptable for an 800 inch diameter spherical vessel manufactured from SA-283-D (Table UCS-23) that contains water (ρ = 0.03613lb/in³) up to a maximum depth of 750 inches with an over-pressure of 2bar (29.4psi, 0.2N/mm²)?

Head pressure = 750 x 0.03612729 = 27.1psi)

Total pressure: at the bottom of the vessel = 27.1 + 29.4 = 46.5psi

Total pressure: at the top of the vessel = 29.4psi

Fig 6. Large Sphere

If manufactured from 160in (high) steel plate, weld seams will occur at the heights indicated in Fig 6 and the following Table:

The depth of liquid at the bottom of each plate is calculated thus:

d = D - R.{1 - Cos(L/R)}

and the total pressure at each depth 'd' is calculated thus:
p = ρ.d₃ + pₒ

where:

D = total liquid depth (750ins)

R = vessel radius (400ins)

L = arc length of plate(s) from base (160ins)

ρ = fluid density (0.03613lb/in³)

d = liquid head (depth at bottom plate)

pₒ = over-pressure (29.4psi)

p = total pressure (46.5psi)

Fig 6 shows the calculation dimensions for the 3rd plate-level

You will need to calculate the plate thickness for each pressure level assuming the entire vessel is exposed to the pressure concerned. The following calculations (per level) are based upon an allowable stress of 12,700psi:

Plate | Arc length | Liquid depth | Total pressure | Plate thickness | |
---|---|---|---|---|---|

level | (L) ins | (d) ins | (p) psi | (t) ins | |

top | 8 | 1256.64 | -50^{#} |
29.4 | 0.087 |

7 | 1120 | -26.89^{#} |
29.4 | 0.087 | |

6 | 960 | 55.04 | 31.389 | 0.093 | |

5 | 800 | 183.54 | 36.031 | 0.107 | |

4 | 640 | 338.32 | 41.624 | 0.123 | |

3 | 480 | 494.94 | 47.282 | 0.140 | |

2 | 320 | 628.68 | 52.114 | 0.154 | |

bottom | 1 | 160 | 718.42 | 55.357 | 0.164 |

# Overpressure (pₒ) only apply to these plates as the surface of the liquid falls below the bottom of the plates concerned.

You could alter the plate thickness for each stratum or multiples thereof. However, the thickness selected for each level must be suitable for the bottom of its lowest plate. The above table also shows that if the vessel were to be manufactured from a single plate thickness it must be no less than 0.164inches (4.2mm).

Whilst the above calculation procedure may also be applied to externally pressurised vessels, plate thickness variations may exacerbate elastic instability.

A typical practical use for externally pressurised vessels is mid-water support buoys. These use their buoyancy to support a weight, e.g. risers, cables, measuring equipment, etc. above the seabed.

Question: A cylindrical buoy of minimal mass is required to lift 4000lbf (total capacity) and operate in seawater at a depth of 325ft. What would be the dimensions of a suitable steel buoy (ignore the effect of vessel heads for this example calculation)?

Assuming the buoy is manufactured from the same material as used in **Example 1** (above), the maximum allowable stress will be 12,700psi.

The external pressure at this depth would be 144.4psi, which is also the differential pressure as it is assumed that atmospheric pressure (1 bar) is inside the vessel.

Fig 7. Vessel Strata Dimensions

The buoy's lift force can be calculated thus:

Fᴸ = ρʷ x Vₒ - ρˢ x (Vₒ - Vᵢ)

Enter this formula into your preferred spreadsheet referencing the appropriate output data you copy and paste from Pressure Vessels.

A typical calculation procedure is listed below (Fig 7):

Step 1. Enter your preferred material thickness (t)

{e.g. 0.512 inches}

Step 2. Alter the internal diameter (Øᵢ) until you have exceeded the pressure (p) required for the depth

{e.g. 166.6 psi}

Step 3. Alter the length (L) and iterate until you have exceeded the required lift force (4000lbf)

{e.g. 74 ins} see **Anomaly 1** below

Step 4. Iterate the number off and cross-sectional area of the ring stiffener until you achieve an acceptable alternative wall thickness

{e.g. 0.252 ins} see **Anomaly 2** below

Step 5. If you prefer to use a cylinder with stiffening rings, then recalculate the mass of the buoy with your preferred stiffening rings and modify the lift force accordingly.

The lift force of the cylinder in Fig 7 is ≈4,218lbf (you may continue to iterate to optimise all properties if you wish)

You may notice some anomalies in your results when making small changes to the input data in Pressure vessels:

**Anomaly 1**: Small increases to the diameter (Øᵢ) without increasing thickness or length may result in an unexpected
*increase* in design pressure.

This is due to the fact that whilst a minor increase in 'Dₒ/t' will reduce Factor 'A' in Fig UG-28-0, the coincident reduction in 'L/Dₒ' will increase it and you may find that 'L/Dₒ' has a greater effect on your results than 'Dₒ/t'. This is not an error in the code, it is simply due to the way in which the code works. According to the design code, the resultant higher design pressure is perfectly reasonable.

**Anomaly 1**: Adding stiffeners to a vessel increases the wall thickness.

This is due to the significant difference between '4 x B' and '2 x E x A' in UG-28 (c) Steps 6 & 7 either side of a temperature boundary in the Fig 5 plots. You will usually find that increasing the cross-sectional area and/or number of stiffening ring(s) will reduce the modified wall thickness (tᵣ) to an acceptable value.

It is usual to fill and pressurise buoys with an inert gas, such as N₂ so that the buoy operates at zero stress; i.e. differential pressure is zero and its external pressure carrying capacity is normally designed for transient conditions.

A warning will be displayed if any wall thickness exceeds the maximum value (relative to shape radius) recommended by the design code or if the wall thickness falls below 0.0625 inches as ASME VIII does not cover pressure vessels with wall this thin.

Input data are required in Imperial: inches (ins), pounds (lbf) and degrees Rankine (°R) in order to ensure no conflict with the design code. All input and output data are converted to metric units.

A 'conical' head requires no knuckle so if a value is entered for the knuckle radius (i.e. rᵢᵏ > 0) the pressure vessel calculator will assume you are looking for a 'toriconical' head and calculate the wall thickness accordingly. If you are looking for the wall thickness of a plain 'conical' head, you must set the knuckle radius to zero (i.e. rᵢᵏ = 0).

Unless special analysis demonstrates to the contrary, ASME VIII does not recommend plain conical heads with an included angle greater than 60° (see **Heads** above), therefore if you enter a knuckle radius (rᵢᵏ) of 0 and half the included angle ('α') > 30, the pressure vessel calculator will display a warning message that only toriconical cone heads are valid for this angle. In such a case, you must either modify the angle to less than 30 or a enter a value for the knuckle radius in order to generate a valid 'tᶜ' value.

When a value of zero is entered for the knuckle radius (i.e. rᵢᵏ = 0) the pressure vessel calculator will always check to see if reinforcement is required for wall thickness 'tᶜ'. If it is required, the cross-sectional rea of the reinforcement is provided alongside the 'tᶜ' result {A=?}. The sectional shape and position of the reinforcement is up to you, however, ASME recommend a maximum permissible distance from the transition (between the cylinder and the cone) for the centroid of area of this reinforcement. The formula for calculating this distance is provided in the Technical Help page of the program.

Vessels and heads are calculated slightly differently dependent upon the applied pressure whether it is internal or external.

You enter the desired pressure rating ('p') and Pressure Vessels calculates the minimum permissible wall thickness ('t') according to the ASME design code.

You enter the expected wall thickness ('t') and Pressure Vessels calculates the maximum permissible pressure ('p') according to the ASME design code. This method may require one or two iterations to achieve the desired pressure rating.

Ṯ (temperature): of the pressurising fluid

Aᵣ (cross-sectional area): of the ring stiffener in cylindrical vessel

№ (number): of stiffeners in cylindrical vessel, spacing will be based upon full pitches between all stiffeners. Pitch = L ÷ (№ + 1)

This calculator works by sizing the stiffneres (Iᵣ & tᵣ) according the number you require (enter).

L (length): cylinder length, excluding heads

Øᵢ (outside diameter of vessel): the maximum value including ovality

σₐ (maximum allowable stress): for the selected material according to ASME VIII, Division 1, Sub-section C, Tables UCS-23 to UHT-23

WJF (weld joint factor): between 0.9 and 1.0 should be used unless unknown or inferior welding procedures are used in the vessel's manufacture

α (half included angle ): of conical and toriconical heads

rᵢᵏ (knuckle radius-inside): for torispherical and toriconical heads

t (wall thickness): minimum permissible value for a cylindrical or spherical vessel

tᵉ (wall thickness): minimum permissible value for an ellipsoidal head

tᵗ (wall thickness): minimum permissible value for a torispherical head

tʰ (wall thickness): minimum permissible value for a hemispherical head

tᶜ (wall thickness): minimum permissible value for a conical head

tᵏ (wall thickness): minimum permissible value for a transition knuckle

p (external pressure): maximum permissible value for the vessel

pᵉ (external pressure): maximum permissible value for an ellipsoidal head

pᵗ (external pressure): maximum permissible value for a torispherical head

pʰ (external pressure): maximum permissible value for a hemispherical head

pᶜ (external pressure): maximum permissible value for a conical head

A (ASME factor): equivalent strain interpolated

B (ASME factor): equivalent stress interpolated

σ₅ (yield stress): of the vessel, head and stiffener materials based upon ASME VIII, Division 1, Appendix 5, Figs UCS-28.1 to UCD-28 at the design temperature ('Ṯ')

Iᵣ (second moment of area): minimum value for the ring stiffener for the vessel dimensions and material (excluding vessel wall)

tᵣ (cylinder wall thickness): minimum value for the vessel wall thickness based upon the number (№) and properties (Iᵣ & tᵣ) of the internal stiffening rings

E₅ (Young's modulus): of the vessel, head and stiffener materials based upon ASME VIII, Division 1, Appendix 5, Figs UCS-28.1 to UCD-28 at the design temperature ('Ṯ')

Vᵢ (internal volume): of a cylindrical or spherical vessel (excluding reinforcement stiffening rings)

Vₒ (external volume): of a cylindrical or spherical vessel (excluding reinforcement stiffening rings)

Vᵢᵉ (internal volume): of an ellipsoidal head including skirt

Vₒᵉ (external volume): of an ellipsoidal head including skirt

Vᵢᵗ (internal volume): of a torispherical head including knuckle and skirt

Vₒᵗ (external volume): of a torispherical head including knuckle and skirt

Vᵢʰ (internal volume): of an hemispherical head including skirt

Vₒʰ (external volume): of an hemispherical head including skirt

Vᵢᶜ (internal volume): of a conical or toriconical head including knuckle (toriconical only) and skirt

Vₒᶜ (external volume): of a conical or toriconical head including knuckle (toriconical only) and skirt

Factor 'A' is *calculated* for ellipsoidal, torispherical and hemispherical heads so no verification plot is listed for these head calculations.

This pressure vessel calculator has been based upon versions of the ASME design code prior to ASME pulling Mandatory Appendix 5 for a rewrite. Therefore, the titles of each material chart associated with Fig 5 are provided below for your information (see Fig 7).

Fig. 5-UGO-28.0 Geometric chart for cylindrical vessels under external or compressive loadings (for all materials)

Ductile Cast Iron: | |
---|---|

Fig. 5-UCD-28 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of cast ductile iron with a specified minimum yield strength of 40,000psi |

Cast Iron: | |
---|---|

Fig. 5-UCI-28 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of cast iron |

Carbon Steel | |
---|---|

Fig. 5-UCS-28.1 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of carbon or low alloy steels (specified minimum yield stress 24,000psi to but not including 30,000psi) |

Fig. 5-UCS-28.2 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of carbon or low alloy steels (specified minimum yield stress 30,000psi and over except for materials within this range where other specified charts are referenced) and Type 405 and Type 410 stainless steels |

Fig. 5-UCS-28.3 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of carbon steel, low alloy steels or steels with properties enhanced by heat treatment (specified minimum yield stress over 38,000psi for materials where other specific charts are not referenced) |

Fig. 5-UCS-28.4 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of SA-537 |

Fig. 5-UCS-28.5 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of SA-508 CL. 2 and 3, SA-533 CL. 1 Grades A, B, and C, SA-533 CL. 2 Grades A, B, C and D or SA-541 Grades 2 and 3 |

Fig. 5-UCS-28.6 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of SA-562 or SA-620 carbon steel |

Austenitic Stainless Steel | |
---|---|

Fig. 5-UHA-28.1 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of austenitic steel (18Cr-8Ni, Type 304) |

Fig. 5-UHA-28.2 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of austenitic steel [18Cr-8Ni-Mo, Type 316; 18Cr-8Ni-Ti, Type 321; 18Cr-8Ni-Cb, Type 347; 25Cr-12Ni, Type 309 (through 1100°F only); 25Cr-20Ni, Type 310 and 17Cr, Type 430B stainless steel (through 700°F only)] |

Fig. 5-UHA-28.3 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of austenitic steel (18Cr-8Ni-0.03 maximum carbon, Type 304L) |

Fig. 5-UHA-28.4 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of austenitic steel (18Cr-8Ni-0.03 maximum carbon, Types 316L and 317L) |

Fig. 5-UHA-28.5 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of Cr-Ni-Mo alloy (S31500) SA-669 |

Quenched and Tempered Carbon and Low Alloy Steel | |
---|---|

Fig. 5-UHT-28.1 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of quenched and tempered low alloy steel, SA-517 all grades and SA-592 Grades A, E and F where t ≤ 2½ in |

Non-Ferrous Metals and Alloys | |
---|---|

Fig. 5-UNF-28.1 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of low carbon nickel |

Fig. 5-UNF-28.2 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 3003 in 0 and H112 tempers |

Fig. 5-UNF-28.3 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 3003 in 0 and H14 tempers |

Fig. 5-UNF-28.4 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 3004 in 0 and H112 tempers |

Fig. 5-UNF-28.5 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 3004 in 0 and H34 tempers |

Fig. 5-UNF-28.6 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel |

Fig. 5-UNF-28.7 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed nickel-copper alloy |

Fig. 5-UNF-28.8 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed nickel-chromium-iron alloy |

Fig. 5-UNF-28.9 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed copper Type DHP |

Fig. 5-UNF-28.10 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed copper-silicon alloys A and C Type DHP |

Fig. 5-UNF-28.11 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed 90-10 copper-nickel alloy |

Fig. 5-UNF-28.12 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed 70-30 copper-nickel alloy |

Fig. 5-UNF-28.13 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5154 in 0 and H112 tempers |

Fig. 5-UNF-28.14 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium bronze alloy 614 |

Fig. 5-UNF-28.15 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum alloy B |

Fig. 5-UNF-28.17 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 1060 in 0 temper |

Fig. 5-UNF-28.18 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5052 in 0 and H112 tempers |

Fig. 5-UNF-28.19 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5086 in 0 and H112 tempers |

Fig. 5-UNF-28.20 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5456 in 0 temper |

Fig. 5-UNF-28.22 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of unalloyed titanium, Grade 3 |

Fig. 5-UNF-28.23 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5083 in 0 and H112 tempers |

Fig. 5-UNF-28.24 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum-chromium-iron alloy |

Fig. 5-UNF-28.25 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-iron-chromium-molybdenum-copper alloy |

Fig. 5-UNF-28.27 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-iron-chromium alloy 800 (annealed) |

Fig. 5-UNF-28.28 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of unalloyed titanium, Grade 2 |

Fig. 5-UNF-28.29 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-iron-chromium alloy 800H (annealed) |

Fig. 5-UNF-28.30 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of welded aluminium alloy 6061-T6, T6510 and T6511 when welded with 5356 or 5556 filler metal all thicknesses; 4043 or 5554 filler metal, thickness ≤ ⅛ in |

Fig. 5-UNF-28.31 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of welded aluminium alloy 6061-T4, T451, T4510 and T4511 when welded with 4043, 5554, 5356 or 5556 filler metal all thicknesses; and of welded aluminium alloy 6061-T6, -T651, -T6510 and -T6511 when welded with 4043 or or 5554 filler metal, thickness > ⅜ in |

Fig. 5-UNF-28.32 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of aluminium alloy 5454 in 0 and H112 tempers |

Fig. 5-UNF-28.33 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum-chromium alloy C-276 |

Fig. 5-UNF-28.34 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of solution treated nickel-chromium-iron-molybdenum-copper (alloys G and G-2) |

Fig. 5-UNF-28.35 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of zirconium alloy 702 |

Fig. 5-UNF-28.36 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of wrought chromium-nickel-iron-molybdenum-copper-columbium stabilized alloy SB-462, SB-463, SB-464, SB-468 and SB-473 |

Fig. 5-UNF-28.37 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-iron-chromium-silicon alloy 330 |

Fig. 5-UNF-28.38 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-chromium-molybdenum, alloy Grade C-4 |

Fig. 5-UNF-28.39 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum alloy X |

Fig. 5-UNF-28.40 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum alloy B-2 |

Fig. 5-UNF-28.41 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of zirconium alloy 705 (R60705) |

Fig. 5-UNF-28.42 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of titanium, Grade 1 |

Fig. 5-UNF-28.43 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed to welded copper-iron alloy tube C19400 (SB-543 welded) |

Fig. 5-UNF-28.44 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of annealed nickel-chromium-molybdenum-columbium alloy N06625 (SB-443, SB-444 and SB-446 in alloy 625) |

Fig. 5-UNF-28.45 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum-chromium-iron-copper (Grade G-3) alloy G-3 whose thickness is ¾ in and under, having a minimum yield strength of 35ksi |

Fig. 5-UNF-28.46 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of nickel-molybdenum-chromium-iron-copper (Grade G-3) alloy G-3 whose thickness is greater than ¾ in and under, having a minimum yield strength of 30ksi |

Fig. 5-UNF-28.47 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of work-hardened nickel |

Fig. 5-UNF-28.48 | Chart for determining shell thickness of cylindrical and spherical vessels under external pressure when constructed of SB-75 and SB-111 light drawn seamless copper tubes, alloys C10200, C12000, C12200 and C14200 |

This calculator applies to any internally or externally pressurised thin-wall cylindrical pressure vessel with formed head(s) according to the rules provided in ASME VIII, Division 1.

Accuracy is according to the rules provided in the ASME VIII, Division 1 design code

A couple of our customers have commented on the fact that CalQlata's ‘pressure vessels’ calculator is based upon a pre-2000 version of ASME VIII and therefore question its validity.

You must remember, we (at CalQlata) provide calculators *only*, we do not provide design codes. And ASME hasn't changed its formulas for internal or external pressure vessel capacity since the specification was introduced in the early 20th century. They were perfectly valid then and remain perfectly valid today. Just like all mathematical models (e.g. Fans; Charles Innes; 1916 and Orbits; Isaac Newton; ≈1700), mathematical validity does not change with time.

Like all design codes, recommended practices and specifications, ASME VIII is regularly updated to account for new materials and government regulations. This calculator does not include the specifications, other than those designated by the original mathematicians and engineers that created this specification, and they remain unchanged today.

CalQlata has stuck with the pre-2000 specification because its stress/strain curves (see Figs 4 & 7) are more accurate than the interpolation tables that accompanied them at that time. These curves, however, are quite difficult to generate and interpolate digitally, so ASME abandoned them when they decided to generate digital versions of their Design Code. CalQlata, on the other hand, has managed to generate these curves for all of ASME's materials (at that time) and that is why they have been included in this calculator.

Therefore, if you are looking for ASME's version of these curves in a later version of their code you won't find them. As with all of our calculators, CalQlata prefers to maximise accuracy in its calculators, even if it means more work for our contributors!

- Stored energy is a measure of the amount of energy that would be released in the event of a catastrophic failure
- ASME VIII recommends that all externally pressurised conical and toriconical heads with an included angle greater than 120° should be treated as flat heads, which are not included in Pressure Vessels
- Excluding nozzles and openings
- Elastic instability is amplified local deformation (strain) due to irregular shape
- The lower the stress at which failure will occur for a given external pressure
- ASME VIII, Division 1, Part UG

Factor 'A': Paragraph UG-23, (b) Step 1

Factor 'B': Paragraph UG-28, (c) Step 6; Pa =**4**.B (where B is ASME yield stress) & Step 7; Pa =**2**.A.E (where A is the strain factor and E is the Young's modulus {yield stress = A.E})

You will find further reading on this subject in reference publications^{(47)}