Technical Progress in Chinese Standard of Ultra-High Pressure Vessels

2019 ◽  
Author(s):  
Zhiwei Chen ◽  
Tao Li ◽  
Guoyi Yang ◽  
Jinyang Zheng ◽  
Guide Deng
Keyword(s):  
High Pressure ◽  
Nondestructive Testing ◽  
Technical Progress ◽  
Pressure Vessel ◽  
Pressure Vessels ◽  
National Standard ◽  
High Pressure Vessel ◽  
Ultra High Pressure ◽  
Chinese Standard ◽  
Design Pressure

Abstract GB/T 34019-2017 “Ultra High Pressure Vessels” is the most important national standard that applies to pressure vessel which design pressure value is greater than or equal to 100MPa (14.5ksi). There is no standard for Ultra-high Pressure Vessel, Then this standard fills the gap in the standard system of pressure equipment in China. This paper mainly introduces the concept and main content of the new national standard, including the materials, design methods and nondestructive testing of ultra-high pressure vessel.

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.

Investigation on the Strength of Ultra High Pressure Vessel Cylinder With Self-Protective Flat Steel Ribbons Wound

2008 ◽  
Author(s):  
Xin Ma ◽  
Jinyang Zheng ◽  
Zhongpei Ning ◽  
Honggang Chen
Keyword(s):  
High Pressure ◽  
Pressure Vessel ◽  
Ultimate Load ◽  
Design Criterion ◽  
Potential Hazard ◽  
Unique Type ◽  
High Pressure Vessel ◽  
Ultra High Pressure ◽  
Load Carrying ◽  
Flat Steel

A unique type of self-protective Ultra-High Pressure Vessel (UHPV) cylinder with helically wound Flat Steel Ribbons (FSR) is proposed. The shielding properties of its self-protection in the hoop and axial directions of a FSR cylinder in the case of fracture failure, as well as quick-actuating of the tooth-locked end closure of this new vessel structure are both expounded. Based on its axial strength, a formula of the ultimate load-carrying capability of FSR layers is derived. The shielding function and self-protective capability of FSR layers to the UHPV cylinder are analyzed quantitatively in detail, and a design criterion is also defined. According to the formula and the design criterion defined in this paper, the predicted ultimate load-carrying capability of the FSR layers is 48.3% higher than that in previous references. Results from burst tests of 6 model vessels show that the brittle failure morphology of UHPV cylinders are changed with FSR layers and the potential hazard of failure of the UHPV is reduced. In addition, the cross fracture of the UHPV cylinder is shielded effectively and the derived formulation on the ultimate load-carrying capability of FSR layers is reasonable. UHPV cylinders designed according to the formula and the criterion can use much fewer FSR layers with the same shielding capability.

Comparison Between the ASME BPVC Section VIII Division 3 and the Chinese Regulation TSG 21-2016 With Regard to the Design of High Pressure Vessels

2018 ◽  
Author(s):  
David Fuenmayor ◽  
Rolf Wink ◽  
Matthias Bortz
Keyword(s):  
High Pressure ◽  
Pressure Vessel ◽  
Pressure Vessels ◽  
Chinese Economy ◽  
High Pressure Vessel ◽  
Safety Technology ◽  
Section Viii ◽  
Design Construction

There are numerous codes covering the design, manufacturing, inspection, testing, and operation of pressure vessels. These national or international codes aim at providing assurance regarding the safety and quality of pressure vessels. The development of the Chinese economy has led to a significant increase in the number of installed high-pressure vessels which in turn required a revision of the existing regulations. The Supervision Regulation on Safety Technology for Stationary Pressure Vessel TSG 21-2016 superseded the existing Super-High Pressure Vessel Safety and Technical Supervision Regulation TSG R0002-2005 in October of 2016. This new regulation covers, among others, the design, construction, and inspection of pressure vessels with design pressures above 100 MPa. This paper provides a technical comparison between the provisions given in TSG 21-2016 for super-high pressure vessels and the requirements in ASME Boiler and Pressure Vessel Code Section VIII Division 3.

Fracture Assessments of High Pressure Vessel Components Having Longitudinal Holes

2017 ◽  
Author(s):  
Yu Xu ◽  
Kuao-John Young
Keyword(s):  
High Pressure ◽  
Stress Concentration ◽  
Fracture Mechanics ◽  
Pressure Vessel ◽  
High Stress ◽  
Pressure Vessels ◽  
Crack Face ◽  
High Pressure Vessel ◽  
High Stress Concentration ◽  
Critical Locations

Small size longitudinal holes are common in components of high pressure vessels. In fracture mechanics evaluation, longitudinal holes have not drawn as much attention as cross-bores. However, longitudinal holes become critical at certain locations for such assessments because of high stress concentration and short distance to vessel component wall. The high stress concentration can be attributed to three parts: global hoop stress that is magnified by the existence of the hole, local stresses due to pressure in the hole, and crack face pressure. In high pressure vessel design, axisymmetric models are used extensively in stress analyses, and their results are subsequently employed to identify critical locations for fracture mechanics evaluation. However, axisymmetric models ignore longitudinal holes and therefore cannot be used to identify the critical location inside the holes. This paper is intended to highlight the importance of including longitudinal holes in fracture mechanics evaluation, and to present a quick and effective way of evaluating high stress concentration at a longitudinal hole using the combined analytical solutions and axisymmetric stress analysis results, identifying critical locations and conducting fracture mechanics evaluation.

Development of Japanese High Pressure Vessel Standard HPIS C106 With ASME Section VIII Division 3

2017 ◽  
Author(s):  
Susumu Terada
Keyword(s):  
High Pressure ◽  
Crystal Growth ◽  
Pressure Vessel ◽  
Pressure Vessels ◽  
Design Code ◽  
Isostatic Pressing ◽  
High Pressure Vessel ◽  
Cyclic Operation ◽  
Section Viii

Many high pressure vessels are used in isostatic pressing, polyethylene process and crystal growth application. The design condition of these high pressure vessels becomes more severe in pressure, temperature and cyclic operation. It was desired that design code for such high pressure vessels be issued enabling more reasonable design than ASME Section VIII Div.1 and Div.2. Against above request, ASME Sec. VIII Div.3 was issued in 1997. While in Japan the subcommittee for high pressure vessels in HPI was started in October 1997 in order to issue the Japanese code for high pressure vessels. At first the background of ASME Div.3 was investigated and then “Rules for Construction of High Pressure Vessels: HPIS C 106” was issued in 2005. That was some differences from ASME Div.3, because we considered that ASME Div.3 should be modified. The author has also been appointed as a member of ASME SG-HPV Committee since 2003. The author has proposed some modification and addition of rules for ASME Div.3 since 2000 and most of them already have been approved and incorporated in ASME Div.3. The background of these modification and addition of rules are shown in this paper.

Research and Development of a Rubber O-Ring Sealing Device for High Pressure Vessels

2013 ◽  
Author(s):  
Fan Zhou ◽  
Zhiping Chen ◽  
Haigui Fan
Keyword(s):  
High Pressure ◽  
Pressure Vessel ◽  
Axial Stress ◽  
Element Model ◽  
Pressure Vessels ◽  
Internal Diameter ◽  
High Pressure Vessel ◽  
Threaded Connections ◽  
Wide Range ◽  
Sealing Device

An O-ring made of rubber exhibits excellent sealing performance with a wide range of applications. The highest sealing pressure can be up to 400MPa. The temperature ranges from −60 °C to 200 °C and the medium is low-corrosiveness. This paper proposes an O-ring sealing device for high pressure vessels, which can be opened and operated outside a cylinder. There are no bolts bearing the axial stress under the internal pressure load, and the sealing efficiency of this device is guaranteed by the dimension chain. The whole sealing device has no threaded connections except for the oriented screw which does not bear load under the working conditions. Based on this newly developed sealing device, a high pressure vessel with the design pressure of 60 MPa and the internal diameter of 700 mm used to simulate 6000 m deep sea environment is developed and investigated. This paper firstly introduces the rationale behind the design of the sealing structure for this high pressure vessel, and then discusses a finite element model of the cylinder end for this high pressure vessel and the stress classification method which is used to evaluate the safety of the critical sections. Lastly, the paper presents a set of experimental devices and a series of experiments which were carried out. The results show that the proposed sealing structure can be used in high pressure vessels. The results also verify the assumption of triangle contact pressure distribution between the shear ring and the cylinder end. It is hoped that this study will be of interest and value to researchers when they design the similar structures in the future.

Numerical Analysis on Delta-Ring Seal Structure of Ultra High Pressure Vessel Employed in Food Processing

2013 ◽  
Vol 303-306 ◽  
pp. 2839-2842
Author(s):  
Rong Li Li ◽  
Xiao Yong Liu ◽  
Shou Qin Zhang ◽  
Tao Li ◽  
Guo Jing Ren
Keyword(s):  
High Pressure ◽  
Numerical Analysis ◽  
Pressure Vessel ◽  
Food Processing ◽  
Residual Deformation ◽  
Full Field ◽  
High Pressure Vessel ◽  
Ultra High Pressure ◽  
Inner Pressure ◽  
Ring Seal

Due to the characters of the ultra high pressure vessel employed in food processing, a seal structure was introduced in this study. Then numerical analysis was performed using the larger finite element stress analysis software ansys12.0 for the stresses of the seal structure under internal pressure. In order to solve the contact question of delta-ring seal structure by using face-face contact model, a 3-D axisymmetric solid element was employed to calculate the stresses of the connected location among delta-ring, blind cover and end cylinder, the mises stresses in this structure were analyzed. Thus, the distribution nephograms of the stress on the contact surface were obtained in different conditions. Full-field plastic deformation of seal structure was generated when the inner pressure was larger than 300Mpa. At last, the reason for residual deformation was analyzed.

The Features of the Integrated Multilayer-Wrapped High Pressure Vessel and its Fabrication Quality being Inspected by Hydrostatic Test

2011 ◽  
Vol 201-203 ◽  
pp. 1539-1543
Author(s):  
Peng Yun Song ◽  
Yang Yong ◽  
Wang Zhong ◽  
Weng Yu ◽  
Ming Fu Hu ◽  
...  
Keyword(s):  
High Pressure ◽  
Pressure Vessel ◽  
Circumferential Stress ◽  
Special Kind ◽  
Outer Shell ◽  
Solid Shell ◽  
High Pressure Vessel ◽  
Test Pressure ◽  
Synthetic Reaction ◽  
Design Pressure

The integrated multilayer-wrapped high pressure vessel is a special kind of multilayered pressure vessel whose circumferential weld seams are able to be in an offset pattern. The fabrication quality is assured by controlling the gaps of the layers. The tightness of the wrapped layers can be inspected by the hydrostatic test. The stress at the outer shell of a DN1400 urea synthetic reaction tower of the integrated multilayer-wrapped has been measured at the time of the hydrostatic test. The results show that the longitudinal stress is identical to that of the theoretical value, and the ratio of the measured circumferential stress to the theoretical calculated one of the corresponding solid shell vessel is more than 0.5 when the hydrostatic test pressure reaches the design pressure. The averaged ratio of the measured circumferential stress to the theoretical calculated one is 0.61 of the two measured sections at the hydrostatic test pressure of 20 MPa. The conclusions are: (1) the fabrication quality of the integrated multilayer-wrapped high pressure vessel are able to be assured, and (2) the tightness of the wrapped layers can be inspected by measuring the circumferential stress at outer shell, and compared to that of the theoretical value of the corresponding solid shell vessel, and (3) it is realizable that the circumferential stress at outer shell of the multilayer-wrapped vessel being not less than 50% of that of the theoretical calculated one of the corresponding solid shell vessel at the design pressure.

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