ANALISYS OF STATICAL RESPONSE OF THE GLORIA TYPE JACK-UP STRUCTURE

Similar documents
STABILITY OF MULTIHULLS Author: Jean Sans

Applying Hooke s Law to Multiple Bungee Cords. Introduction

Analysis and Research of Mooring System. Jiahui Fan*

Aidin Kazemi Daliri, Sepanta Naimi*

Stability and Computational Flow Analysis on Boat Hull

Hours / 100 Marks Seat No.

Finite Element Analysis of an Aluminium Bike Frame

Item 404 Driving Piling

Stress evaluation of a bicycle crank arm connection using BEM

DESIGN AND OPTIMIZATION OF ROLLING MILL CHOCK

MINIMUM DECK HEIGHT OF A SEMI-SUBMERSIBLE PLATFORM ACCORDING TO BLACK SEA ENVIRONMENT

APPLICATION OF PUSHOVER ANALYSIS ON EARTHQUAKE RESPONSE PREDICATION OF COMPLEX LARGE-SPAN STEEL STRUCTURES

and its weight (in newtons) when located on a planet with an acceleration of gravity equal to 4.0 ft/s 2.

Modeling of Hydraulic Hose Paths

Pre AP Physics: Unit 7 Vibrations, Waves, and Sound. Clear Creek High School

A new methodology to evaluate the flying shape of a sail

Learn more at

RULES PUBLICATION NO. 20/P SHIP SIDE STRENGTHENING OF FISHING VESSELS MOORING AT SEA ALONGSIDE OTHER VESSELS

Abstract. 1 Introduction

RECONSTRUCTION OF AN UNUSUAL ROAD TRAFFIC ACCIDENT USING COMPUTER SIMULATION

Aalborg Universitet. Published in: Proceedings of Offshore Wind 2007 Conference & Exhibition. Publication date: 2007

ISOLATION OF NON-HYDROSTATIC REGIONS WITHIN A BASIN

The OTSS System for Drift and Response Prediction of Damaged Ships

The water supply for a hydroelectric plant is a reservoir with a large surface area. An outlet pipe takes the water to a turbine.

3 1 PRESSURE. This is illustrated in Fig. 3 3.

Sea-going vessel versus wind turbine

CHAPTER IV FINITE ELEMENT ANALYSIS OF THE KNEE JOINT WITHOUT A MEDICAL IMPLANT

Stress and deformation of offshore piles under structural and wave loading

Underwater Intervention Conference 2006 Tampa, FL, January 24-26, 2006 A Minimum Cost Design Approach of an ROV for Underwater Inspection

Tribology in Industry. Research Regarding Drilling Masts Reliability under the Combined Action of the Wind and the Hook Load

Coupling and Analysis of 981 Deep Water Semi-submersible. Drilling Platform and the Mooring System

computed using Equation 3-18 by setting the 2nd term equal to 0 and K A equal to K o and using the pressure distribution as shown in Figure 3-23.

Lecture Outline Chapter 15. Physics, 4 th Edition James S. Walker. Copyright 2010 Pearson Education, Inc.

The Relationship between the Depth Embedded Pipe Pile and the Force of Clamping Jaw

Structural Analysis of Mast of Special Rotary Drilling Rig for Transmission Line

COUPLED DYNAMIC ANALYSIS OF MOORING LINES FOR DEEP WATER FLOATING SYSTEMS

LAB 7. ROTATION. 7.1 Problem. 7.2 Equipment. 7.3 Activities

The Application of ANSYS Contact Analysis in Cable Crane Load Conversion Device

Tutorial 5 Relative equilibrium

IMO REVISION OF THE INTACT STABILITY CODE. Proposal of methodology of direct assessment for stability under dead ship condition. Submitted by Japan

Hours / 100 Marks Seat No.

DESIGN OPTIMIZATION OF WORK ROLL CHOCK AND BACKUP ROLL CHOCK IN COLD ROLLING MILL

Chapter 2 Hydrostatics and Control

HOW FAST/FAR DOES FLY LINE FALL? N. Perkins of the University of Michigan, March 2003

Preliminary study of moored power cables

Special Considerations for Structural design and Fabrication for. tankers or similar vessels with Large Size (150m or more in length) in.

The 11 th International Scientific Conference elearning and Software for Education Bucharest, April 23-24, 2015

Comparative Stability Analysis of a Frigate According to the Different Navy Rules in Waves

Study of Passing Ship Effects along a Bank by Delft3D-FLOW and XBeach1

Physics 1C. Lecture 12C. "Fluctuat nec mergitur. = She is swayed by the waves but does not sink." --Motto of the city of Paris

Experiment P18: Buoyant Force (Force Sensor)

Research of Load and Structural Direct Calculation on Flat-Type River-Sea-Going Ship

Analysis of dilatometer test in calibration chamber

Engineering Practice on Ice Propeller Strength Assessment Based on IACS Polar Ice Rule URI3

Ship Stability. Ch. 8 Curves of Stability and Stability Criteria. Spring Myung-Il Roh

Design and Analysis of Rotary Lawn Mower

EVALUATING CRITERIA FOR DP VESSELS

STRESS ANALYSIS OF RATCHET PAWL DESIGN IN HOIST USING FINITE ELEMENT ANALYSIS

Irrigation &Hydraulics Department lb / ft to kg/lit.

Using the CONVAL software for the petrochemical plant control valves checking. Case study

Structural Design and Analysis of the New Mobile Refuge Chamber

A NOVEL FLOATING OFFSHORE WIND TURBINE CONCEPT: NEW DEVELOPMENTS

CALCULATION OF THE MECHANISM FOR THE STRETCHING AND RETRACTING OF THE BOOM OF A TRUCK MOUNTED CRANE

Technical Briefing Note

Dynamic Characteristics of the End-effector of a Drilling Robot for Aviation

JAR-23 Normal, Utility, Aerobatic, and Commuter Category Aeroplanes \ Issued 11 March 1994 \ Section 1- Requirements \ Subpart C - Structure \ General

Exam Question 9: Hydrostatics. March 6, Applied Mathematics: Lecture 8. Brendan Williamson. Introduction. Density, Weight and Volume

A Review of the Bed Roughness Variable in MIKE 21 FLOW MODEL FM, Hydrodynamic (HD) and Sediment Transport (ST) modules

Wave Load Pattern Definition

SUBPART C - STRUCTURE

The below identified patent application is available for licensing. Requests for information should be addressed to:

PAPER 2 THEORY QUESTIONS

Modal Analysis of Propulsion Shafting of a 48,000 tons Bulk Carrier

1. Air is blown through a pipe AB at a rate of 15 litre per minute. The cross-sectional area of broad

INTERNATIONAL JOURNAL OF DESIGN AND MANUFACTURING TECHNOLOGY (IJDMT) FREE VIBRATION ANALYSIS OF PASSENGER BOAT

Chapter 11 Waves. Waves transport energy without transporting matter. The intensity is the average power per unit area. It is measured in W/m 2.

DETRMINATION OF A PLUNGER TYPE WAVE MAKER CHARACTERISTICE IN A TOWING TANK

ASSESSMENT AND ANALYSIS OF PIPELINE BUCKLES

Torque Review. 3. What is true about the Torques on an object in rotational equilibrium?

Equilibrium. Observations

Marine Kit 4 Marine Kit 4 Sail Smooth, Sail Safe

CERTIFICATES OF COMPETENCY IN THE MERCHANT NAVY MARINE ENGINEER OFFICER

MODELLING MOORING LINE BEHAVIOUR TO DETERMINE THE IMPACT FORCE ON SQUID EGG BEDS

Design Project 2 Sizing of a Bicycle Chain Ring Bolt Set ENGR 0135 Sangyeop Lee November 16, 2016 Jordan Gittleman Noah Sargent Seth Strayer Desmond

FLUID MECHANICS Time: 1 hour (ECE-301) Max. Marks :30

Analysis on the operation of gas regulators and optimization of their operation

Abstract. 1 Introduction

DEVIL PHYSICS THE BADDEST CLASS ON CAMPUS AP PHYSICS

INCLINOMETER DEVICE FOR SHIP STABILITY EVALUATION

FC-CIV HIDRCANA: Channel Hydraulics Flow Mechanics Review Fluid Statics

Conceptual Design and Passive Stability of Tethered Platforms

Application of pushover analysis in estimating seismic demands for large-span spatial structure

Chapter 14: Waves. What s disturbing you?

Fluid Mechanics. Chapter Three: Fluid Statics. Dr. Amer Khalil Ababneh

Appendix M Structural Analysis of the Macondo #252 Work String. Appendix M Structural Analysis of the Macondo #252 Work String

Elastic-Plastic Finite Element Analysis for Zhongwei--guiyang Natural Gas Pipeline Endangered by Collapse

Casing Collapse Pressure for Non-zero Internal Pressure Condition. (Effect of Internal Pressure on Collapse)

LAB 13: FLUIDS OBJECTIVES

Clarification of Behavior of Huge Tsunami Action on Bridges - Hydraulic Model Experiment and Simulation Technology -

EXPERIMENTAL RESEARCH ON THE MECHANICAL SOLICITATIONS OF THE GREENHOUSES OF VEGETABLES AND FLOWERS LOCATED ON ROOFTOPS

Transcription:

Scientific Bulletin of the Politehnica University of Timisoara Transactions on Mechanics Special issue The 6 th International Conference on Hydraulic Machinery and Hydrodynamics Timisoara, Romania, October 21-22, 2004 ANALISYS OF STATICAL RESPONSE OF THE GLORIA TYPE JACK-UP STRUCTURE Georgic Slmnoiu Senior lecturer Ph. D. Valentin Oncica Lecturer Ph. D. Naval Academy Mircea cel Btrân Constana Naval Academy Mircea cel Btrân Constana Florin Nicolae Senior lecturer Ph. D. Naval Academy Mircea cel Btrân Constana ABSTRACT The statical response of a Gloria type jack-up was determinated by the authors with COSMOS programme, based on FEM, with designer hypothesis considering and extreme conditions in Black Sea. The structural model of Gloria type jack-up was loaded with hydrodynamic loads and wind loads obtained in paper Analysis of loadings acting on a Gloria type jack-up structure (by the same authors, HMH 2004) in this way: - the main vertical pipes (chords) where loaded with 100% hydrodynamic forces from diagram; - the secondary pipes (horizontal and diagonal) where loaded with percentage of hydrodynamic forces from diagram, depending on diameter of chord and diameter of secondary pipes ratio, for each level. The results of the analyses were: the values and the diagram of von Mises stresses, on levels and beam types and the displacement of structures. KEYWORDS Gloria type jack-up, FEM, hydrodynamic forces, von Mises stresses 1. GENERAL CONSIDERATIONS The tension and deformation state from the structure components was determined by the authors through static calculation, based on the finite element method (F.E.M.), using the COSMOS program, taking into consideration the hypothesis (data bases) of the designer, as follows: the constructional structure is that of the platform already in exploitation; length of the legs is 121,619 m; body mass at location 6640 t; longitudinal distance between legs 38,43 m; transversal distance between legs 33,26 m; water depth, h = 90 m; air space (the distance between the water surface and the bottom of the platform)= 11,2 m; maximum wave height, Hmax = 12 m wave period, T = 10 s; maximum wind speed, vmax = 44,72 m/s; the less favorable loading situation is when both wind and wave act simultaneously from N. 2. STRUCTURE LOADS PRODUCED BY WINDS AND WAVES The loading of the spatial model of the Gloria type jack-up maritime drilling platform was made according to the following principles. 1. The force of the wind, F v, calculated in [3], was applied in the center of gravity of the sail area of the platform model. 2. The loading of the structure with the loads generated by the waves was calculated as follows: legs 3 and 4 (fig. 1) were loaded considering the legs are hit by the crest of the wave accordingly to the loads given by the diagram in figure 5, thesis [3] legs 1 and 2 were loaded in conformance with: - loads given by the diagram in figure 5, thesis [3]; - wave length, @ = gt 2 / (2A) = 156,131 m; - period T = 10 s; - longitudinal distance between legs = 38,43 m. The vertical tubes were loaded with hydrodynamic loads in conformance with the diagram in figure 5, thesis [3] and the above

considerations, and the diagonal and horizontal tubes with loads proportional to their exterior diameters. The energetic loss of the wave due to the hitting of legs 3 and 4 was not taken into consideration. the numeric integration method used is the modified Newton-Raphson method. The rolling results are presented in figures 2 4 and table 1, as follows: figure 2 presents the tension state in the legs of the structure; figure 3 presents the tension state in the bars of leg 4, between levels 25 and 26; figure 4 presents the deformed structure of the platform, using an amplification coefficient of 100; in table 1 are given the values of the equivalent tensions, calculated with the 5 th theory (the theory for the deformation potential energy for modifying shape von Mises) from Material Resistance, on levels and types of bars, corresponsive to the most solicited zones of leg 4. Fig. 1 3.THE DETERMINATION OF THE TENSION AND DEFORMATION STATE The determination of the tension and deformation state was done through static calculus, using the COSMOS program. It presents the following possibilities: it has at it s base the generalized Hooke law and the equation of continuity; it permits the control of structure deformations both in movement and in tensions; the Lagrange interpolation functions transmit the tensions through the whole mass of the material; the procedure for solving the structural equilibrium is based on the gradient method; the static or dynamic analysis is done in linear or non-linear domain (material, shape or stress non-linearity); Fig. 2

Table 1 Equivalent tensions (von Mises) in the bars of the leg 4 of the platform Level ech, MPa Vertical tubes Horizontal pipes Diagonal pipes 1 III 200,3 c 83,4 c III 125,1 2 III 190,5 c 77,9 c III 119,4 3 III 181,7 c 73,6 c III 114,7 4 III 173,2 a 70,7 a III 110,5 5 III 165,9 a 67,2 a III 106,3 6 III 158,1 a 64,3 a III 102,2 7 III 151,4 c 62,1 c III 99,1 8 III 145,3 c 60,7 c III 96,5 9 III 139,6 a 58,2 a III 93,6 10 III 134,1 a 56,5 a III 90,7 11 III 129,7 a 55,4 a III 88,4 12 III 125,3 a 54,2 a III 87,2 13 I 127,1 a 52,9 a I 86,1 14 I 131,6 a 53,8 a I 86,9 15 I 136,5 c 54,8 c I 88,2 16 I 142,3 c 56,0 c I 89,6 17 I 146,7 c 57,4 c I 91,1 18 I 150,2 c 58,9 c I 92,8 19 II 154,4 c 60,6 c II - 94,3 20 II 158,7 a 62,4 a II 97,1 21 II 163,2 a 64,3 a II 100,4 22 II 167,9 a 66,3 a II - 103,6 23 II 172,5 a 68,5 a II - 106,5 24 II 177,4 a 70,7 a II 109,4 25 II 181,3 a 73,0 a II 112,0 26 II 186,2 a 75,5 a II 116,2 27 II 192,4 a 79,1 a II 121,7

Fig. 3

Fig. 4

Both in figures 2 and 3 as well as in table 1 are given the average values of the equivalent tensions in N/m2. The values of the movements in figure 4 are given in meters. 4. CONCLUSIONS Taking into consideration the present results, the following conclusion can be formulated regarding the tension state: 1. The bars in which tensions of maximum values appear are those from the vertical tubes model, as follows: the bars from the constraining zone oriented towards the Ox axis (S direction) of the legs 4 and 3, respectively 1 and 2 (see fig.2 and table 1) for which ech = 185...200 Mpa; the greater values are recorded in the case of legs 4 and 3 which bear stronger constraints, being hit by the waves; the bars from the binding area between the legs and the body, oriented in reversed direction of the Ox axis (N direction) of the legs 3 and 4, respectively 1 and 2 (see fig.2 and table 1) for which ech = 185...192 Mpa and in this case the greater values are recorded also in legs 4 and 3. It shows that the tensions in the binding area between the legs and the body are very close in values to the constrain area, due to the model chosen which is a tension concentrator. The real plausible values can be considered those from the area right next to the binding area between the legs and the body, namely ech = 170...180 Mpa. 2. In the horizontal pipes the maximum values of the equivalent tensions are about 40% of the determined maximum values from the vertical tubes. These are recorded in: the bars corespondent to the level 1 pipes, at legs 4 and 3, respectively 1 and 2, in the end and middle areas; the bars that make up the pipes from level 27, at legs 4 and 3, respectively 1 and 2, in the end areas (oriented in the direction of wind and waves) and in the middle areas of the pipes. 3.The maximum equivalent tensions in the diagonal pipes are about 65% of the maximum determined values for the vertical tubes. These are recorded in the same areas as in the vertical tubes. 4.Vertically, in the most solicitated bars of each type of tubular element, the equivalent tensions increase from the central area of the leg troughout the extremities. 5.The analysis of the tension state within levels 25 and 26 (fig.3) shows maximum tensions in the end areas of the diagonal and horizontal pipes, respectively in the vertical tubes extremities towards the body of the platform. The deformation state analysis (fig. 4) leads to the conclusion that the maximum recorded movement which coincides with the one of the platform s body, respectively the leg elements in the leg-body binding area is 0,116 m. This value is framed within the maximum admisable technological limit for maximum movement of the body which is 0,3 m. REFERENCES 1. xxx Project no. 823 for constructing Romanian jack-up maritime drilling. ICEPRONAV, GalaKi, 1980 2. SLLMNOIU, G. Contributions regarding exploitation attitude, improvement of construction and increasing performance of the Romanian maritime drilling platforms. Doctorate Thesis, Petrol-Gaze University PloieOti, 2001. 3. SLLMNOIU, G, CHIPAC, V, ONCICA, V. Structure modelling and loads determination which act on a jack-up maritime drilling platform. Aniversary Session 130 years of maritime teaching, Naval Academy Mircea cel BQtrân, ConstanKa, 2002