Experimental Investigation of Nozzle-Induced Cylindrical Shell Stresses Where R/T = 1264

1986 ◽  
Vol 108 (1) ◽  
pp. 98-107
Author(s):  
R. A. Whipple

Stresses and displacements for a nozzle connection typical of those found in large storage tanks or pressure vessels were measured for applied radial forces, circumferential moments and longitudinal moments. The test program was conducted on a 12 1/2-in-dia penetration, centered and welded into a 60 in. × 60 in. cylindrical panel with a radius to thickness ratio of 1264. The nozzle diameter to cylindrical shell diameter ratio was 0.05. The panel edges were bolted to a stiff rectangular frame. This report presents the measured radial deflections and nozzle rotations, the membrane stress resultants and shell bending moments in the vicinity of the penetration along with penetration membrane and bending stresses for the three loadings. A brief description of the model and the test procedure is also presented.

1983 ◽  
Vol 105 (3) ◽  
pp. 201-206 ◽  
Author(s):  
R. A. Whipple ◽  
J. Hagstrom ◽  
H. Dykstra

Stresses and displacements for a nozzle connection typical of those found in a large storage or pressure vessel were measured for applied radial forces, circumferential moments and longitudinal moments. The test program was conducted on a 2 1/2-in. φ penetration, centered and welded into a 60 in. × 60 in. cylindrical panel with a radius to thickness ratio of 1264. The nozzle diameter to cylindrical shell diameter ratio was 0.01. The panel edges were bolted to a stiff rectangular frame. This report presents the measured radial deflections and nozzle rotations, the membrane stress resultants and shell bending moments in the vicinity of the penetration for the three loadings. A brief description of the model and the test procedure is also presented.


1945 ◽  
Vol 12 (2) ◽  
pp. A107-A112
Author(s):  
G. J. Schoessow ◽  
L. F. Kooistra

Abstract Results are reported of a strain-gage test conducted on a 54-in-diam cylindrical shell to which was attached two 12-in-diam pipes. The pipes were subjected to direct axial-tension loading, direct axial-compression loading, and transverse bending moments. This construction simulates the conditions which exist in boiler drums, pressure piping, hydraulic penstocks, etc., where pipe connections are subject to forces and moments that develop strains in the shell to which the pipes are attached. Moderate loading applied to the pipes resulted in 20,000-psi bending stresses in the shell. These stresses are of a magnitude that demands the respect and attention of the designers. By publication of these data, the authors hope to stimulate interest in further experimental and analytical investigations of the problem, which eventually will establish a basis for predicting the magnitude of stresses in cylindrical shells. Such data are not now available.


Author(s):  
S C Palmer

Differential settlement around the circumference of the foundation below the shell of a vertical cylindrical storage tank is a particularly severe form of settlement, and can cause distortion and stressing of the tank. The resulting deflections and stresses in the shell and primary wind girder of a tank with a floating roof can be analysed, assuming the shell to behave as a membrane. The analysis is reviewed and the results are applied to present a new design chart for predicting the maximum shell membrane stress caused by settlement. For unanchored tanks, the stiffness of a tank may be such that the shell can ‘bridge’ across localized soft spots in the foundation. A simplified analysis of bridging is presented and a criterion for predicting the onset of bridging is proposed, supported by model test results. Expressions for the associated shell membrane stresses are derived. For unanchored floating-roof tanks, it is concluded that the occurrence of bridging will always limit the maximum shell membrane stress to an acceptable value. However, the bending stresses in the shell-to-base joint of a bridging tank require separate assessment in all cases. The settlement criteria contained in the current British and American codes of practice for in-service inspection of tanks are reviewed in the light of these findings.


1981 ◽  
Vol 16 (3) ◽  
pp. 171-186 ◽  
Author(s):  
P Stanley ◽  
T D Campbell

Very thin cylindrical pressure vessels with torispherical end-closures have been tested under internal pressure until buckles developed in the knuckles of the ends. These were prototype vessels in an austenitic stainless steel. The preparation of the ends and the closed test vessels is outlined, and the instrumentation, test installation, and test procedure are described. Results are given and discussed for three typical ends (diameters 54, 81, and 108in.; thickness to diameter ratios 0.00237, 0.00158, and 0.00119). These include measured thickness and curvature distributions, strain data and the derived elastic stress indices, and pole deflection measurements. Some details of the observed time-dependent plasticity (or ‘cold creep’) are given. Details of two types of buckle that developed eventually in the vessel ends are also reported.


2006 ◽  
Vol 13-14 ◽  
pp. 127-132 ◽  
Author(s):  
Gerold Lackner ◽  
Peter Tscheliesnig

Acoustic emission testing (AT) is in Europe an already well established non-destructive testing (NDT) method. Qualification requirements as well as certification of testing personnel are laid down in European standard EN 473. A widespread application of AT deals with testing of unfired pressure vessels for re-qualification after a certain period of service (repetition test). The advantages of applying AT compared to the traditional procedure of hydrostatic test plus visual inside inspection are numerous. Just to name the most important: reduction of downtime, omitting of residual humidity and no risk of product contamination with water. It is a fact that AT provides much more useful information concerning the condition of the pressure vessel under test than a simple ‘passed’ or ‘not passed’ obtained usually by a hydrostatic test. This contribution gives two examples of practical experience, where severe corrosion defects have been detected by AT. The defects have been found in both cases on the vessel’s shell under the thermal insulation, where they have been hidden undetected for years. It can be assumed that even the vessel with the most severe damage (loss of more than 50% of the nominal wall thickness) would have passed the traditional repetition test procedure and that failure within the following service period would have occurred. In contrary to this scenario, AT enabled the vessel operator to perform appropriate repair in time.


Author(s):  
G G Chew ◽  
I C Howard ◽  
E A Patterson

It is proposed that, in appropriate circumstances, membrane structures can experience bending moments. On uniformly inflating a thin sheet structure, which has a shape consisting of multiple curvatures, the structure will deform in such a way that the final shape will have a single radius of curvature, assuming that failure does not occur. It is the large change of shape from a multicurvature surface to a single curvature surface that causes bending moments to exist within a membrane. The validity of the hypothesis has been demonstrated using four finite element models, including an elliptical cylinder, an ellipsoid, a ‘double’ cone and a trileaflet heart valve.


Author(s):  
Takayasu Tahara

Pressure equipment in refinery and petrochemical industries in Japan has been getting old, mostly more than 30 years in operation. Currently, the Japanese regulations for pressure equipment in service are the same as those in existence during the fabrication of the pressure equipment. Accordingly, there is an immediate need for an up to date more advanced “Fitness For Service” (FFS) evaluation requirements for pressure equipment. In order to introduce the latest FFS methodologies to Japanese industries, the High Pressure Institute of Japan (HPI) has organized two task groups. One is a working group for development of a maintenance standard for non-nuclear industries. Its prescribed code “Assessment procedure for crack-like flaws in pressure equipment” is for conducting quantitative safety evaluations of flaws detected in common pressure equipment such as pressure vessels, piping, storage tanks. The other is a special task group to study of API RP579 from its drafting stage as a member of TG579. The FFS Handbook, especially for refinery and petrochemical industries, has been developed based on API RP579 with several modifications to meet Japanese pressure vessel regulations on April 2001. [1] It is expected that both the Standard and FFS handbook will be used as an exemplified standard with Japanese regulations for practical maintenance. This paper presents concepts of “Assessment procedure for crack-like flaws in pressure equipment” HPIS Z101, 2001 [2].


Author(s):  
Fa´bio de Castro Marangone ◽  
Ediberto Bastos Tinoco ◽  
Carlos Eduardo Simo˜es Gomes

Coke drums are thin-walled pressure vessels that experience severe thermal cycling condition which consists of heating, filling and rapidly cooling the drum in a short period of time. After some years under operation, cracks at the vessel may occur, especially at high stress concentration areas such as the skirt support to shell attachment. During the filling phase of the cycle, when the empty and cooled coke drum is filled with hot oil, the shell and cone temperatures increase rapidly compared to the skirt temperature and the last is pushed outward, since its bottom is at lower temperature and fixed at a concrete base. During quenching (sudden cooling) phase, the coke drum is filled with water at about 80°C and tends to cool faster than the skirt, which is pulled inward until equilibrium is obtained. The skirt expansion and contraction movement results in bending stresses in axial direction on the top of skirt. As lower the switch temperature is, more severe is the bending effect. One of PETROBRAS delayed coke unit presented some operational problems at pre-heating phase, resulting in lower switch temperatures. This paper presents an analysis showing the influence of the switch temperature on coke drum fatigue life. At first, the transient loading conditions were established from thermocouple measurements at skirt attachment weld (hot box region). Later, a transient thermal analysis was performed with FEA and the temperature gradient at the skirt attachment during entire thermal cycle was obtained. The thermal results were then converted to a structural model which was solved for linear elastic stress including other loads such as pressure. Finally, the maximum stress components for both filling and quenching phases were determined and a complete stress range was calculated as per ASME Section VIII, Div 2. The procedure described above was applied for different switch temperatures scenarios in order to show its influence on the fatigue life of the coke drum.


1991 ◽  
Vol 113 (3) ◽  
pp. 380-384
Author(s):  
P. B. Crosley ◽  
E. J. Ripling

Safety of structures can be assured, even if cracks initiate in localized regions of abnormally low toughness, and/or abnormally high stress (LT/HS), if the materials from which they are fabricated have a high enough crack arrest fracture toughness. When this requirement is met, fast-running cracks that initiate in LT/HS regions arrest when their tip encounters material having normal toughness and stresses. The work described in this paper was carried out to determine the crack arrest capability of LNG storage tanks by determining the longest LT/HS region in which a crack could initiate and still arrest when it leaves this region. The determination consisted of relating a fracture analysis with the measured full-thickness crack arrest fracture toughness of three 9-percent Ni plates which were reported in reference [1]. The calculations used a residual stress pattern, produced by welding, superimposed on a typical membrane stress. The residual stress was selected as an example of a localized high stress region. It was found that tanks built from the poorest of the three tested plates could arrest cracks about 3/4 m long, while tanks built from the two tougher plates could arrest cracks almost 2 m long.


1969 ◽  
Vol 4 (1) ◽  
pp. 57-64
Author(s):  
R W T Preater

Three different assumptions are made for the behaviour of the junction between the cylindrical shell and the end closure. Comparisons of analytical and experimental results show that the inclusion of a ‘rigid’ annular ring beam at the junction of the cylider and the closure best represents the shell behaviour for a ratio of cylinder mean radius to thickness of 3–7, and enables a prediction of an optimum vessel configuration to be made. Experimental verification of this optimum design confirms the predictions. (The special use of the term ‘rigid’ is taken in this context to refer to a ring beam for which deformations of the cross-section are ignored but rigid body motion is permitted.)


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