Strategy for Cross-Bores in High Pressure Containers

1969 ◽  
Vol 11 (2) ◽  
pp. 151-161 ◽  
Author(s):  
B. N. Cole
Keyword(s):  
High Pressure ◽  
Fatigue Life ◽  
Cross Section ◽  
Pressure Vessel ◽  
Working Pressure ◽  
Circular Section ◽  
Centre Line ◽  
Cylindrical Pressure Vessel ◽  
Von Mises ◽  
Safe Working

It is frequently necessary to drill a cross-bore through the wall of a cylindrical pressure vessel, and it tends to be taken for granted that the cross-bore—itself of circular section— should lie along a diameter of the main cross-section. The weakening effect of such a hole is well known, and reduces the safe working pressure down to 2/5 of the value for the undisturbed cylinder in the case of a Tresca material, or nearly down to 1/3 in the case of a von Mises material. The paper shows how it is possible to reclaim a large proportion of the ‘lost’ pressure capacity by use of a cross-bore which is either elliptical in section, or, more conveniently, round but offset from a diametral centre-line. Such procedure could thus also greatly improve the fatigue life of the pressure vessel.

Strength of Cylinders Containing Radial or Offset Cross-Bores

1976 ◽  
Vol 18 (6) ◽  
pp. 279-286 ◽  
Author(s):  
B. N. Cole ◽  
G. Craggs ◽  
I. Ficenec
Keyword(s):  
Fatigue Life ◽  
Pressure Vessel ◽  
Cyclic Stress ◽  
Stress Conditions ◽  
Bursting Pressure ◽  
Centre Line ◽  
Cylindrical Pressure Vessel ◽  
The Cross ◽  
Static Conditions ◽  
Radial Centre

The introduction of a small transverse opening or cross-bore into the wall of a cylindrical pressure vessel is sometimes necessary. Under static conditions such a cross-bore may have little effect on the bursting pressure of a plain cylinder, but under cyclic stress conditions, the fatigue life of the vessel is severely reduced. If the cross-bore axis is offset from the radial centre-line of the cylinder, then the fatigue life of such a vessel is shown to be substantially greater than that of a similar vessel containing a radial cross-bore.

Modeling and Optimization of Ultra High Pressure Vessel With Self-Protective Flat Steel Ribbons Wound and Tooth-Locked Quick-Actuating End Closure

2008 ◽  
Author(s):  
Xin Ma ◽  
Zhongpei Ning ◽  
Honggang Chen ◽  
Jinyang Zheng
Keyword(s):  
High Pressure ◽  
Fatigue Life ◽  
Pressure Vessel ◽  
Design Method ◽  
Structural Parameters ◽  
Three Dimensional ◽  
Peak Stress ◽  
High Pressure Vessel ◽  
Ultra High Pressure ◽  
Flat Steel

Ultra-High Pressure Vessel (UHPV) with self-protective Flat Steel Ribbons (FSR) wound and Tooth-Locked Quick-Actuating (TLQA) end closure is a new type of vessel developed in recent years. When the structural parameters of its TLQA and Buttress Thread (BT) end closure are determined using the ordinary engineering design method, Design by Analysis (DBA) shows that the requirement on fatigue life of this unique UHPV could hardly be satisfied. To solve the above problem, an integrated FE modeling method has been proposed in this paper. To investigate the fatigue life of TLQA and BT end closures of a full-scale unique UHPV, a three-dimensional (3-D) Finite Element (FE) solid model and a two-dimensional (2-D) FE axisymmetric model are built in FE software ANSYS, respectively., Nonlinear FE analysis and orthogonal testing are both conducted to obtain the optimum structure strength, in which the peak stress in the TLQA or BT end closure of the unique UHPV is taken as an optimal target. The important parameters, such as root structure of teeth, contact pressure between the pre-stressed collar and the cylinder end, the knuckle radius, the buttress thread profile and the local structure of the cylinder, are optimized. As a result, both the stress distribution at the root of teeth and the axial load carried by each thread are improved. Therefore, the load-carrying capacity of the end closure has been reinforced and the fatigue life of unique UHPV has been extended.

The Fatigue Life Analysis of Prestressed Wire-Wound Super-High Pressure Vessel Based on ANSYS

2014 ◽  
Vol 552 ◽  
pp. 8-14 ◽  
Author(s):  
Jun Fei Wu ◽  
Jun Bin Lan ◽  
Kai Hu ◽  
Qing Ling Li
Keyword(s):  
High Pressure ◽  
Fatigue Life ◽  
Pressure Vessel ◽  
Design Theory ◽  
Safety Hazard ◽  
Fatigue Design ◽  
Potential Safety ◽  
Fatigue Life Analysis ◽  
Winding Wire ◽  
Bearing Structure

With the the development of super-high pressure technology such as the super-high biological treatment processing, the wire-wound prestressed vessel was widely used as the main pressure bearing structure. It’s proved that the stress was well-distributed along thickness direction and the carrying capacity was improved comparing with traditional pressure vessel. But the deign of wire-wound pressured vessel so far only checks out the fatigue strength margin of winding wire according to the design theory, and lacking of fatigue design of inner cylinder could causes potential safety hazard. So a stress analysis was carried out for prestressed wire-wound vessel with the help of ANSYS, and the fatigue life of the whole prestressed vessel was validated by means of theoretical calculation and the Fatigue Tool .

Toroidal uniformly stressed pressure vessel shell formed by the meridian and ring filament winding

2021 ◽  
Author(s):  
M.A. Komkov
Keyword(s):  
High Pressure ◽  
Cross Section ◽  
Pressure Vessel ◽  
Filament Winding ◽  
Industrial Workers ◽  
Equilibrium Equations ◽  
Emergency Situations ◽  
Breathing Apparatus ◽  
Composite Pressure Vessel ◽  
Toroidal Shells

The paper outlines the prospects for the use of composite toroidal high-pressure cylinders for the breathing apparatus of the Ministry of Emergency Situations, fire brigades, industrial workers, which are more ergonomic in comparison with their cylindrical counterparts. Relying on the analytical solution of the equilibrium equations, we determined the shape of the cross-section of toroidal shells reinforced along the meridians and representing intersecting loop-like curves that form an infinitely long corrugated pipe. The study introduces a solution for a toroidal composite pressure vessel formed by the intersection of the upper and lower branches of the shell, reinforced along the meridians, and a profiled ring layer of filaments installed at the point of their intersection. The parameters of the toroidal uniformly stressed pressure vessel shell made by ring and meridian filament winding are calculated.

Fatigue Life of Commercial High Pressure Tubing

2002 ◽  
Author(s):  
Michael D. Mann
Keyword(s):  
High Pressure ◽  
Fatigue Life ◽  
Pressure Vessel ◽  
Pressure Vessels ◽  
Thick Wall ◽  
Pressure Tubing ◽  
Safety And Reliability ◽  
Section Viii ◽  
Critical Components ◽  
Axial Fatigue

Design guidance for high pressure components, has undergone a dramatic change with the release of ASME Section VIII division 3 pressure vessel code. For the first time, a thorough design criteria is available for design of thick wall pressure vessels. The most critical components of a design are safety and reliability. Ultra high-pressure vessels, in most cases, do not have an “infinite” life. The design must therefore be “leak before break” and a design cycle life must be specified. This paper looks at the effects of fatigue on commercial high-pressure tubing under tri-axial fatigue. The tubing investigated is 316 stainless steel 9/16″ and 3/8″ diameter 4100 bar (60,000 psi) tubing. The testing was performed using a tri-axial fatigue machine originally designed by Dr. B. Crossland, Dr. J. L. M. Morrison and Dr. J. S. C. Perry in 1960 and upgraded by the Author. This investigation compares the fatigue life prediction per KD3 in the ASME pressure vessel code Section VIII division 3 and actual test results from the fatigue machine. This verification gives important reliability data for commercial hardware used in high-pressure piping.

Calculation of Working Pressure for Cylindrical Vessel Under External Pressure

2010 ◽  
Author(s):  
Gurinder Singh Brar ◽  
Yogeshwar Hari ◽  
Dennis K. Williams
Keyword(s):  
Monte Carlo ◽  
Cylindrical Shell ◽  
Pressure Vessel ◽  
External Pressure ◽  
Working Pressure ◽  
Geometric Imperfections ◽  
The Monte Carlo Method ◽  
Cylindrical Pressure Vessel ◽  
Section Viii ◽  
Initial Geometric Imperfections

Initial geometric imperfections have a significant effect on the load carrying capacity of asymmetrical cylindrical pressure vessels. This research paper presents a comparison of a reliability technique that employs a Fourier series representation of random asymmetric imperfections in a defined cylindrical pressure vessel subjected to external pressure. Evaluations as prescribed by the ASME Boiler and Pressure Vessel Code, Section VIII, Division 2 rules are also presented and discussed in light of the proposed reliability technique presented herein. The ultimate goal of the reliability type technique is to statistically predict the buckling load associated with the cylindrical pressure vessel within a defined confidence interval. The example cylindrical shell considered in this study is a fractionating tower for which calculations have been performed in accordance with the ASME B&PV Code. The maximum allowable external working pressure of this tower for the shell thickness of 0.3125 in. is calculated to be 15.1 psi when utilizing the prescribed ASME B&PV Code, Section VIII, Division 1 methods contained within example L-3.1. The Monte Carlo method as developed by the current authors and published in the literature is then used to calculate the maximum allowable external working pressure. Fifty simulated shells of geometry similar to the example tower are generated by the Monte Carlo method to calculate the nondeterministic buckling load. The representation of initial geometric imperfections in the cylindrical pressure vessel requires the determination of appropriate Fourier coefficients. The initial functional description of the imperfections consists of an axisymmetric portion and a deviant portion that appears in the form of a double Fourier series. Multi-mode analyses are expanded to evaluate a large number of potential buckling modes for both predefined geometries and the associated asymmetric imperfections as a function of position within a given cylindrical shell. The method and results described herein are in stark contrast to the dated “knockdown factor” approach currently utilized in ASME B&PV Code.

Design and Analysis of a High Pressure Laboratory Vessel for Testing Well Cement

2020 ◽  
Author(s):  
Milind Prabhu ◽  
Ksenia Eliseev ◽  
Pedro Vargas ◽  
John Krener ◽  
Venkata Nadakuditi ◽  
...  
Keyword(s):  
High Pressure ◽  
Pressure Vessel ◽  
Thermal Gradients ◽  
Test Protocol ◽  
Working Pressure ◽  
High Pressure High Temperature ◽  
Division 1 ◽  
Section Viii ◽  
Overall Performance ◽  
Well Cement

Abstract The Steam Permeameter Cell is a laboratory-scale pressure vessel used to perform high pressure, high temperature testing on well cement slurries. Initial sizing of the concentric, two chamber vessel was based on design by rule concepts in the ASME Boiler and Pressure Vessel Code, Section VIII Division 1. However, based on the complex transient loading expected during the specified testing protocol, additional engineering design and analysis was performed to understand the effects of thermal gradients on the overall strength and fatigue performance of the vessel. The objective of the engineering assessment was to show compliance with design margins in the Code when non-listed materials are utilized in the construction. Using detailed analytical modeling of transient, thermo-mechanical loading, the assessment demonstrated that the test vessel was safe to operate based on engineering judgement and established best practices in vessel design by analysis. Furthermore, several design modifications were identified to improve functionality and overall performance of the vessel. The Steam Permeameter Cell design had sufficient static capacity to contain the maximum allowable working pressure (MAWP) of 3,500 psig at a design temperature of 700°F, and fatigue capacity to withstand the intended test protocol over the service life.

Pressure-vessel support brackets: Stresses due to dead loads

1967 ◽  
Vol 2 (1) ◽  
pp. 1-16 ◽  
Author(s):  
R Kitching ◽  
B E Olsen
Keyword(s):  
Spherical Shell ◽  
Strain Gauge ◽  
Pressure Vessel ◽  
Elastic Shell ◽  
Design Methods ◽  
Centre Line ◽  
Conventional Design ◽  
Cylindrical Pressure Vessel ◽  
Support Reaction

The investigation is concerned with the elastic shell stresses occurring when vertical loads are transmitted through discrete support brackets welded to the lower hemispherical end of a cylindrical pressure vessel having its axis vertical. Three sizes of bracket were examined, and the largest was compared with a similar arrangement having an internal bracket continuous with the external one. Strain-gauge results indicated that shell stresses may be calculated by assuming that the radial deflection of the spherical shell is linearly distributed along the line of contact between bracket and shell. Conventional design methods employed in stress calculations tended to underestimate the shell stresses. It is shown that the line of application of the support reaction in relation to the centre line of the bracket is most important.

Fatigue Life of Commercial High Pressure Needle Valves and Tee Assemblies

2007 ◽  
Author(s):  
Mario L. Rovere ◽  
Michael D. Mann ◽  
William R. Culley
Keyword(s):  
High Pressure ◽  
Stainless Steel ◽  
Fatigue Life ◽  
Cycle Life ◽  
Test Results ◽  
Working Pressure ◽  
Design Cycle ◽  
Commercial Sources ◽  
Actual Test ◽  
Axial Fatigue

This paper investigates the design cycle life of commercially available 9/16 inch needle valves and 9/16 inch tees under tri-axial fatigue. The valves and tees investigated were manufactured from 316 stainless steel and are rated to 4100 bar (60,000 psi) maximum allowable working pressure. The testing was performed using a tri-axial fatigue machine originally designed by Dr. B. Crossland, Dr. J.L.M. Morrison and Dr. J.S.C. Perry in 1960 [1] and upgraded by Michael D. Mann of KMT Waterjet Systems, Inc. This investigation compares the fatigue life of the 9/16 inch needle valves and 9/16 inch tees from two different commercial sources via actual test results from the fatigue machine.

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