Strength of Cylinders Containing Radial or Offset Cross-Bores

Cole, B. N.; Craggs, G.; Ficenec, I.

doi:10.1243/jmes_jour_1976_018_045_02

Cited by 12 publications

(14 citation statements)

References 12 publications

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“…The geometric discontinuities act as stress raisers, thus creating regions of high stress concentration especially near the intersection of the main bore and the cross bore [7]. Regrettably, at these regions of high stress the elemental stress equations cease to apply [8].…”

Section: Introductionmentioning

confidence: 99%

“…Stress Concentration Factor (SCF), also known as the Effective Stress Factor (ESF) [9], is determined using the relationship given in Equation (1) as detailed in Masu and Craggs [7] and Kharat and Kulkari [8]; Cole et al [10] reported that high values of SCF act as points of weakness leading to reduction in the vessel strength as well as its fatigue life. This weakness reduces the pressure carrying capacity of the pressure vessel by up to 60 % [11] when compared to a plain vessel without a cross bore.…”

Section: Introductionmentioning

confidence: 99%

“…This weakness reduces the pressure carrying capacity of the pressure vessel by up to 60 % [11] when compared to a plain vessel without a cross bore. It is worth noting that failures of pressure vessel are usually catastrophic and may lead to loss of life, damage of property or pose a health hazard [4,8].…”

Section: Introductionmentioning

confidence: 99%

“…Stress concentrations in high pressure vessels with a cross bore depend on the geometric configuration of the cross bore [8]. The major geometric configuration parameters of the cross bore are the size ratio (cross bore to main bore ratio), location, shape, obliquity angle and thickness ratio.…”

Section: Introductionmentioning

confidence: 99%

“…Various cross bore sizes and shapes have been used in the design of pressure vessels. The cross bore size ranges from small drain nozzle to large handholds and manholes such as tee junctions [8]. While, the most common cross bore shapes are circular and elliptical [12].…”

Section: Introductionmentioning

confidence: 99%

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An Optimal Location of Elliptical Cross Bore in Elastic Pressurized Thick Cylinders

Nziu¹,

Tjprc²

2019

IJMPERD

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Finite Element Analysis (FEA) was performed on elastic pressurized thick walled cylinder to determine the optimal location for an elliptical shaped cross bore. Preliminary investigations were performed on a radial elliptical shaped cross bore to establish an optimum diameter ratio in a cylinder with thickness ratio of 2.0.The cross bore diameter with size ratio of 2.0 gave the lowest Stress Concentration Factor (SCF) at 1.89.Henceforth,only the optimal diameter size ratio was used for further optimal analyses. The optimization process was then done on cross bored cylinders of thickness ratios of 1.4 up to 3.0 at various offset locations along the radial X axis of the cylinder. The study covered offset locations between the radial position of the cylinder and the offset ratio of 0.9. The authors established that offsetting of an elliptically shaped cross bores increases the magnitude of SCFs. Overall, lowest SCF occurred at radial position when K=2.5 with a magnitude of 1.733. This lowest SCF magnitude indicated a reduction of pressure carrying capacity of 42.3% in comparison to a similar plain cylinder without a cross bore.

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Section: Introductionmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

Section: Introductionmentioning

confidence: 99%

See 3 more Smart Citations

An Optimal Location of Elliptical Cross Bore in Elastic Pressurized Thick Cylinders

Nziu¹,

Tjprc²

2019

IJMPERD

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High‐Pressure Technology

Vetter

Karl²

2000

Ullmann's Encyclopedia of Industrial Chemistry

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The article contains sections titled: 1. Applications of High‐Pressures 2. Pressure Vessels 2.1. Solid‐Wall Vessels 2.2. Multiwall Vessels 2.2.1. Designs with a Purely Mechanical Joint 2.2.2. Welded Designs (Layered‐Wall Vessels) 2.3. Strength Calculations 2.3.1. Cylindrical Wall 2.3.1.1. Stresses Due to Internal Pressure 2.3.1.2. Initial Stresses in Shrink Joints 2.3.1.3. Residual Stresses Due to Autofrettage 2.3.1.4. Thermal Stresses 2.3.1.5. Avoiding Brittle Fracture 2.3.2. Cylindrical Wall with Radial Bore 2.3.3. End Pieces 2.4. Corrosion in High‐Pressure Plant 2.5. Material Selection 2.6. Design Details 2.6.1. Corrosion Protection 2.6.2. Covers and Their Attachment 2.6.3. Cover Seals 2.6.4. Seals for Piping 2.7. Example of the Design of Pressure Vessels 3. High‐Pressure Machinery for Chemical Plants 3.1. Special Features of High‐Pressure Machines 3.2. Creation of Pressure by Pumps and Compressors 3.3. Pumps 3.3.1. Reciprocating Displacement Pumps 3.3.1.1. Metering Pumps 3.3.1.2. Transfer Pumps 3.3.2. Rotary Displacement Pumps 3.3.3. Centrifugal Pumps 3.3.3.1. Multistage Centrifugal Pumps 3.3.3.2. High‐Speed Centrifugal Pumps 3.3.3.3. Hermetic Centrifugal Pumps 3.4. Compressors 3.4.1. Piston Compressors 3.4.2. Diaphragm Compressors, Laboratory High‐Pressure Compressors 3.4.3. Turbo Compressors 3.5. Other High‐Pressure Machines 3.6. Special Problems Involving High‐Pressure Machines 3.6.1. Strength of the Components 3.6.2. Seals 3.6.3. Wear and Vibration 4. Piping and Fittings

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Fatigue of thick‐walled pipes from soft martensitic and semi‐austenitic chrome‐nickel steels under pulsating internal pressure

1992

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Thick-walled components subjected to pulsating internal pressure are widely applied in high-pressure technology and in manufacturing processes such as fluid-jet cutting and highpressure cleaning, mainly in conjunction with reciprocating pumps. Corrosive fluids require high-strength and tough chrome-nickel steels with soft martensitic or semi-austenitic structure. This contribution reports on the fatigue of thick-walled plain and cross-bored pipes made from high alloy chrome-nickel steels such as X5CrNiMoCu 21 8 and X5CrNiMo 16 5. The specimens, uniaxial standard form and thick-walled pipes, were cut from forged blocks in the three axial directions. For loading with pulsating pressure, a suitable, high-frequency piston pulsation machine has been developed. The fatigue tests on pipe specimens show typical Woehler characteristics with only slight scatter and relatively good isotropy. The surprisingly large admissible pulsating pressure can be explained for the applied steels by dynamic generation of residual stresses as a result of shake-down effects. Presentation in a Smith digram explains the occurring dynamic shake-down and its favourable results in comparison to the more brittle highly tensile steels. It also reveals that heat treatment to higher tensile strength does not always yield an increase in the admissible pulsating pressure. It will be shown that static autofretting and shake-down affect the fatigue strength of thick-walled pipe specimens in the same way. Tests with internal liners in the tube specimens provide indications on the sensitivity of material failures towards fluids. The investigation aids the understanding of the fatigue behaviour and the design of components made of modern high-strength corrosion resistant steels.

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Strength of Cylinders Containing Radial or Offset Cross-Bores

Cited by 12 publications

References 12 publications

An Optimal Location of Elliptical Cross Bore in Elastic Pressurized Thick Cylinders

An Optimal Location of Elliptical Cross Bore in Elastic Pressurized Thick Cylinders

High‐Pressure Technology

Fatigue of thick‐walled pipes from soft martensitic and semi‐austenitic chrome‐nickel steels under pulsating internal pressure

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