This document presents a comprehensive mechanistic model for predicting upward two-phase flow in wellbores. The model consists of a flow pattern prediction model and separate models for key flow characteristics like holdup and pressure drop for each predicted pattern of bubble, slug, and annular flow. The model is evaluated against a large well data set and shows good agreement. It performs better than other commonly used empirical correlations and an existing mechanistic model.
Numerical Calculation of Solid-Liquid two-Phase Flow Inside a Small Sewage Pumptheijes
Based on a mixture multiphase flow model,theRNG k–εturbulencemodelandfrozen rotor method were used to perform a numerical simulation of steady flow in the internal flow field of a sewage pump that transports solid and liquid phase flows. Resultsof the study indicate that the degree of wear on the front and the back of the blade suction surface from different densities of solid particles shows a completely opposite influencing trend. With the increase of delivered solid-phase density, the isobaric equilibrium position moves to the leading edge point of the blade, but the solid-phase isoconcentration point on the blade pressure surface and suction surface basically remains unchanged. The difference between hydraulic lift and water lift indelivering solid- and liquid-phase flows shows a rising trend with the increase of working flow
H-infinity controller with graphical LMI region profile for liquid slosh supp...TELKOMNIKA JOURNAL
This paper presents a H-infinity synthesis with pole clustering based on LMI region schemes for
liquid slosh control. Using LMI approach, the regional pole placement known as LMI region combined with
design objective in H-infinity controller guarantee a fast input tracking capability and very minimal liquid
slosh. A graphical profile of the transient response of liquid slosh suppression system with respect to pole
placement is very useful in giving more flexibility to the researcher in choosing a specific LMI region. With
the purpose to confirm the design of control scheme, a liquid slosh model is considered to represent
the lateral slosh movement. Supremacy of the proposed approach is shown by comparing the results with
hybrid model-free fuzzy-PID controller with derivative filter. The performance of the control schemes is
examined in terms of time response specifications of lateral tank tracking capability and level of liquid
slosh reduction.
Experimental conceptualisation of the Flow Net system construction inside the...Dr.Costas Sachpazis
ABSTRACT
By means of a drainage and seepage tank, an experimental flow net system inside the body of a homogeneous earth embankment dam model, formed from Leighton Buzzard Silica sand, was developed and studied in this experimental research paper.
Water flow through dams is one of the basic problems for geotechnical engineers. Seepage analysis in an important factor to be considered in the proper design of many civil engineering structures. Seepage can occur in both through the structure itself as the case of earth dams and under foundations of an engineering structure. Successful seepage analysis is achieved on the proper and accurate construction of a flow net.
Amongst the various existing methods of seepage analysis, the “Finite Element Method” and the method of “Experimental Flow Nets” are the most widely used ones.
Construction of a flow net is mainly used for solving water flow problems through porous media where the geometry makes sometimes analytical solutions impractical. This method is usually used in soil mechanics, geotechnical or civil engineering as an initial check for problems of water flow under hydraulic structures like embankments or dams. As such, a grid obtained by drawing a series of equipotential lines and stream or flow lines is called a flow net. In this procedure the Laplace equation principles must be satisfied.
Hence, the construction of a flow net is an important tool in analysing two-dimensional irrotational flow problems and provides an approximate solution to the flow problem by following simple rules, as initially set out by Forchheimer, 1900, and later refined by Casagrande,1937. It can also be very useful tool even for problems with complex geometries, as proven in this experimental research paper.
The objectives of this experimental research paper are:
• To determine the position and shape of the flow line representing the uppermost free water surface inside the body of a dam by using a drainage and seepage tank,
• To conceptualise the flow lines system and to demonstrate that each flow line starts perpendicular to the upstream slope of the dam and that that slope is a boundary equipotential line,
• To construct an experimental flow net and subsequently to verify and analyse it by the FEA method,
• To calculate the rate of seepage through the dam body, and
• To summarise the calculations and experimental findings in a concise and readable format.
In order to achieve these objectives, an experimental flow net system inside the body of a homogeneous earth embankment dam model was formulated by using a drainage and seepage tank.
From the constructed flow net in the present experimental research paper, an attempt has been made to analyze, determine and present the following parameters:
The pressure drop from one side of the embankment to the other,
The seepage flow rate in each flow “channel”,
The total seepage flow rate, and
The pore pressure ratio, ru, for the embankment.
IJERA (International journal of Engineering Research and Applications) is International online, ... peer reviewed journal. For more detail or submit your article, please visit www.ijera.com
Numerical Calculation of Solid-Liquid two-Phase Flow Inside a Small Sewage Pumptheijes
Based on a mixture multiphase flow model,theRNG k–εturbulencemodelandfrozen rotor method were used to perform a numerical simulation of steady flow in the internal flow field of a sewage pump that transports solid and liquid phase flows. Resultsof the study indicate that the degree of wear on the front and the back of the blade suction surface from different densities of solid particles shows a completely opposite influencing trend. With the increase of delivered solid-phase density, the isobaric equilibrium position moves to the leading edge point of the blade, but the solid-phase isoconcentration point on the blade pressure surface and suction surface basically remains unchanged. The difference between hydraulic lift and water lift indelivering solid- and liquid-phase flows shows a rising trend with the increase of working flow
H-infinity controller with graphical LMI region profile for liquid slosh supp...TELKOMNIKA JOURNAL
This paper presents a H-infinity synthesis with pole clustering based on LMI region schemes for
liquid slosh control. Using LMI approach, the regional pole placement known as LMI region combined with
design objective in H-infinity controller guarantee a fast input tracking capability and very minimal liquid
slosh. A graphical profile of the transient response of liquid slosh suppression system with respect to pole
placement is very useful in giving more flexibility to the researcher in choosing a specific LMI region. With
the purpose to confirm the design of control scheme, a liquid slosh model is considered to represent
the lateral slosh movement. Supremacy of the proposed approach is shown by comparing the results with
hybrid model-free fuzzy-PID controller with derivative filter. The performance of the control schemes is
examined in terms of time response specifications of lateral tank tracking capability and level of liquid
slosh reduction.
Experimental conceptualisation of the Flow Net system construction inside the...Dr.Costas Sachpazis
ABSTRACT
By means of a drainage and seepage tank, an experimental flow net system inside the body of a homogeneous earth embankment dam model, formed from Leighton Buzzard Silica sand, was developed and studied in this experimental research paper.
Water flow through dams is one of the basic problems for geotechnical engineers. Seepage analysis in an important factor to be considered in the proper design of many civil engineering structures. Seepage can occur in both through the structure itself as the case of earth dams and under foundations of an engineering structure. Successful seepage analysis is achieved on the proper and accurate construction of a flow net.
Amongst the various existing methods of seepage analysis, the “Finite Element Method” and the method of “Experimental Flow Nets” are the most widely used ones.
Construction of a flow net is mainly used for solving water flow problems through porous media where the geometry makes sometimes analytical solutions impractical. This method is usually used in soil mechanics, geotechnical or civil engineering as an initial check for problems of water flow under hydraulic structures like embankments or dams. As such, a grid obtained by drawing a series of equipotential lines and stream or flow lines is called a flow net. In this procedure the Laplace equation principles must be satisfied.
Hence, the construction of a flow net is an important tool in analysing two-dimensional irrotational flow problems and provides an approximate solution to the flow problem by following simple rules, as initially set out by Forchheimer, 1900, and later refined by Casagrande,1937. It can also be very useful tool even for problems with complex geometries, as proven in this experimental research paper.
The objectives of this experimental research paper are:
• To determine the position and shape of the flow line representing the uppermost free water surface inside the body of a dam by using a drainage and seepage tank,
• To conceptualise the flow lines system and to demonstrate that each flow line starts perpendicular to the upstream slope of the dam and that that slope is a boundary equipotential line,
• To construct an experimental flow net and subsequently to verify and analyse it by the FEA method,
• To calculate the rate of seepage through the dam body, and
• To summarise the calculations and experimental findings in a concise and readable format.
In order to achieve these objectives, an experimental flow net system inside the body of a homogeneous earth embankment dam model was formulated by using a drainage and seepage tank.
From the constructed flow net in the present experimental research paper, an attempt has been made to analyze, determine and present the following parameters:
The pressure drop from one side of the embankment to the other,
The seepage flow rate in each flow “channel”,
The total seepage flow rate, and
The pore pressure ratio, ru, for the embankment.
IJERA (International journal of Engineering Research and Applications) is International online, ... peer reviewed journal. For more detail or submit your article, please visit www.ijera.com
Geotechnical Engineering-I [Lec #27A: Flow Calculation From Flow Nets]Muhammad Irfan
Class notes of Geotechnical Engineering course I used to teach at UET Lahore. Feel free to download the slide show.
Anyone looking to modify these files and use them for their own teaching purposes can contact me directly to get hold of editable version.
Velocity distribution, coefficients, pattern of velocity distribution,examples, velocity measurement, derivation of velocity distribution coefficients, problems and solution, Bernoulli's theorem and energy equation, specific energy and equation.
Hardy cross method of pipe network analysissidrarashiddar
Hardy Cross Method of pipe network analysis has revolutionized the municipal water supply design. i.e., EPANET, a public domain software of water supply, uses the Hardy cross method for pipe network analysis. It is an iterative approach to estimate the flows within the pipe network where inflows (supply) and outflows (demand) with pipe characteristics are known.
International Journal of Computational Engineering Research (IJCER) is dedicated to protecting personal information and will make every reasonable effort to handle collected information appropriately. All information collected, as well as related requests, will be handled as carefully and efficiently as possible in accordance with IJCER standards for integrity and objectivity.
In this study the kinematic wave equation has been solved numerically using the modified Lax
explicit finite difference scheme (MLEFDS) and used for flood routing in a wide prismatic channel and a nonprismatic
channel. Two flood waves, one sinusoidal wave and one exponential wave, have been imposed at the
upstream boundary of the channel in which the flow is initially uniform. Six different schemes have been
introduced and used to compute the routing parameter, the wave celerity c. Two of these schemes are based on
constant depth and use constant celerity throughout the computation process. The rest of the schemes are based
on local depths and give celerity dependent on time and space. The effects of the routing parameter c on the
travel time of flood wave, the subsidence of the flood peak and the conservation flood flow volume have been
studied. The results seem to indicate that there is a minimal loss/gain of flow volume whatever the scheme is.
While it is confirmed that neither of the schemes is 100% volume conservative, it is found that the scheme
Kinematic Wave Model-2 (KWM-II) gives the most accurate result giving only 0.1% error in perspective of
volume conservation. The results obtained in this study are in good qualitative agreement with those obtained in
other similar studies.
The effect of rotational speed variation on the velocity vectors in the singl...IOSR Journals
The current investigation is aimed to simulate the three-dimensional complex internal flow in a
centrifugal pump impeller with five twisted blades by using a specialized computational fluid dynamics (CFD)
software ANSYS /FLUENT 14code with a standard k-ε two-equation turbulence model.
A single blade passage will be modeled to give more accurate results for velocity vectors on (blade, hub, and
shroud). The potential consequences of velocity vectors associated with operating a centrifugal compressor in
variable rotation speed.
A numerical three-dimensional, through flow calculations to predict velocity vectors through a
centrifugal pump were presented to examined the effect of rotational speed variation on the velocity vectors of
the centrifugal pump . The contours of the velocity vectors of the blade, hub, and shroud indicates low velocity
vectors in the suction side at high rotational speed (over operation limits )and the velocity vectors increases
gradually until reach maximum value at the leading edge (2.63×10 m/s) of the blade
Geotechnical Engineering-I [Lec #27A: Flow Calculation From Flow Nets]Muhammad Irfan
Class notes of Geotechnical Engineering course I used to teach at UET Lahore. Feel free to download the slide show.
Anyone looking to modify these files and use them for their own teaching purposes can contact me directly to get hold of editable version.
Velocity distribution, coefficients, pattern of velocity distribution,examples, velocity measurement, derivation of velocity distribution coefficients, problems and solution, Bernoulli's theorem and energy equation, specific energy and equation.
Hardy cross method of pipe network analysissidrarashiddar
Hardy Cross Method of pipe network analysis has revolutionized the municipal water supply design. i.e., EPANET, a public domain software of water supply, uses the Hardy cross method for pipe network analysis. It is an iterative approach to estimate the flows within the pipe network where inflows (supply) and outflows (demand) with pipe characteristics are known.
International Journal of Computational Engineering Research (IJCER) is dedicated to protecting personal information and will make every reasonable effort to handle collected information appropriately. All information collected, as well as related requests, will be handled as carefully and efficiently as possible in accordance with IJCER standards for integrity and objectivity.
In this study the kinematic wave equation has been solved numerically using the modified Lax
explicit finite difference scheme (MLEFDS) and used for flood routing in a wide prismatic channel and a nonprismatic
channel. Two flood waves, one sinusoidal wave and one exponential wave, have been imposed at the
upstream boundary of the channel in which the flow is initially uniform. Six different schemes have been
introduced and used to compute the routing parameter, the wave celerity c. Two of these schemes are based on
constant depth and use constant celerity throughout the computation process. The rest of the schemes are based
on local depths and give celerity dependent on time and space. The effects of the routing parameter c on the
travel time of flood wave, the subsidence of the flood peak and the conservation flood flow volume have been
studied. The results seem to indicate that there is a minimal loss/gain of flow volume whatever the scheme is.
While it is confirmed that neither of the schemes is 100% volume conservative, it is found that the scheme
Kinematic Wave Model-2 (KWM-II) gives the most accurate result giving only 0.1% error in perspective of
volume conservation. The results obtained in this study are in good qualitative agreement with those obtained in
other similar studies.
The effect of rotational speed variation on the velocity vectors in the singl...IOSR Journals
The current investigation is aimed to simulate the three-dimensional complex internal flow in a
centrifugal pump impeller with five twisted blades by using a specialized computational fluid dynamics (CFD)
software ANSYS /FLUENT 14code with a standard k-ε two-equation turbulence model.
A single blade passage will be modeled to give more accurate results for velocity vectors on (blade, hub, and
shroud). The potential consequences of velocity vectors associated with operating a centrifugal compressor in
variable rotation speed.
A numerical three-dimensional, through flow calculations to predict velocity vectors through a
centrifugal pump were presented to examined the effect of rotational speed variation on the velocity vectors of
the centrifugal pump . The contours of the velocity vectors of the blade, hub, and shroud indicates low velocity
vectors in the suction side at high rotational speed (over operation limits )and the velocity vectors increases
gradually until reach maximum value at the leading edge (2.63×10 m/s) of the blade
lab 4 requermenrt.pdf
MECH202 – Fluid Mechanics – 2015 Lab 4
Fluid Friction Loss
Introduction
In this experiment you will investigate the relationship between head loss due to fluid friction and
velocity for flow of water through both smooth and rough pipes. To do this you will:
1) Express the mathematical relationship between head loss and flow velocity
2) Compare measured and calculated head losses
3) Estimate unknown pipe roughness
Background
When a fluid is flowing through a pipe, it experiences some resistance due to shear stresses, which
converts some of its energy into unwanted heat. Energy loss through friction is referred to as “head
loss due to friction” and is a function of the; pipe length, pipe diameter, mean flow velocity,
properties of the fluid and roughness of the pipe (the later only being a factor for turbulent flows),
but is independent of pressure under with which the water flows. Mathematically, for a turbulent
flow, this can be expressed as:
hL=f
L
D
V
2
2 g
(Eq.1)
where
hL = Head loss due to friction (m)
f = Friction factor
L = Length of pipe (m)
V = Average flow velocity (m/s)
g = Gravitational acceleration (m/s^2)
Friction head losses in straight pipes of different sizes can be investigated over a wide range of
Reynolds' numbers to cover the laminar, transitional, and turbulent flow regimes in smooth pipes. A
further test pipe is artificially roughened and, at the higher Reynolds' numbers, shows a clear
departure from typical smooth bore pipe characteristics.
Experiment 4: Fluid Friction Loss
The head loss and flow velocity can also be expressed as:
1) hL∝V −whe n flow islaminar
2) hL∝V
n
−whe n flow isturbulent
where hL is the head loss due to friction and V is the fluid velocity. These two types of flow are
seperated by a trasition phase where no definite relationship between hL and V exist. Graphs
of hL −V and log (hL) − log (V ) are shown in Figure 1,
Figure 1. Relationship between hL ( expressed by h) and V ( expressed by u ) ;
as well as log (hL) and log ( V )
Experiment 4: Fluid Friction Loss
Experimental Apparatus
In Figure 2, the fluid friction apparatus is shown on the right while the Hydraulic bench that
supplies the water to the fluid friction apparatus is shown on the left. The flow rate that the
hydraulic bench provides can be measured by measuring the time required to collect a known
volume.
Figure 2. Experimental Apparatus
Experimental Procedure
1) Prime the pipe network with water by running the system until no air appears to be discharging
from the fluid friction apparatus.
2) Open and close the appropriate valves to obtain water flow through the required test pipe, the four
lowest pipes of the fluid friction apparatus will be used for this experiment. From the bottom to the
top, these are; the rough pipe with large diameter and then smooth pipes with three successively
smaller diameters.
3) Measure head loss ...
The effect of rotational speed variation on the static pressure in the centri...IOSR Journals
The current investigation is aimed to simulate the three-dimensional complex internal flow in a
centrifugal pump impeller with five twisted blades by using specialized computational fluid dynamics (CFD)
software ANSYS /FLUENT 14code with a standard k-ε two-equation turbulence model.
A single blade passage will be modeled to give more accurate results for static pressure contours on (blade,
hub, and shroud). The potential consequences of static pressure associated with operating a centrifugal
compressor in variable rotation speed.
A numerical three-dimensional, through flow calculations to predict static pressure through a
centrifugal pump were presented to examined the effect of rotational speed variation on the static pressure of
the centrifugal pump . The contours of the static pressure of the blade, hub, and shroud indicates negative low
static pressure in the suction side at high rotational speed (over operation limits )and the static pressure
increases gradually until reach maximum value at the leading edge (6×105 Pa) of the blade.
SPLIT SECOND ANALYSIS COVERING HIGH PRESSURE GAS FLOW DYNAMICS AT PIPE OUTLET...AEIJjournal2
A detailed investigation covering piped gas flow characteristics in high pressure flow conditions. Such flow analysis can be resolved using established mathematical equations known as the Fanno condition, which usually cover steady state, or final flow conditions. However, in real life, such flow conditions are
transient, varying with time. This paper uses CFD analysis providing a split second “snapshot” at what happens at the pipe outlet, and therefore, a closer understanding at what happens at the pipe’s outlet in high pressure gas flow condition
The use of Cellular Automata is extended in various disciplines for the modeling of complex system procedures. Their inherent simplicity and their natural parallelism make them a very efficient tool for the simulation of large scale physical phenomena. We explore the framework of Cellular Automata to develop a physically based model for the spatial and temporal prediction of shallow landslides. Particular weight is given to the modeling of hydrological processes in order to investigate the hydrological triggering mechanisms and the importance of continuous modeling of water balance to detect timing and location of soil slips occurrences. Specifically, the 3D flow of water and the resulting water balance in the unsaturated and saturated zone is modeled taking into account important phenomena such as hydraulic hysteresis and evapotranspiration. In this poster the hydrological component of the model will be presented and tested against well established benchmark experiments [Vauclin et al, 1975; Vauclin et al, 1979]. Furthermore, we investigate the applicability of incorporating it in a hydrological catchment model for the prediction (temporal and spatial) of rainfall-triggered shallow landslides.
IJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and TechnologyIJRET : International Journal of Research in Engineering and Technology is an international peer reviewed, online journal published by eSAT Publishing House for the enhancement of research in various disciplines of Engineering and Technology. The aim and scope of the journal is to provide an academic medium and an important reference for the advancement and dissemination of research results that support high-level learning, teaching and research in the fields of Engineering and Technology. We bring together Scientists, Academician, Field Engineers, Scholars and Students of related fields of Engineering and Technology
Comparison of flow analysis of a sudden and gradual change of pipe diameter u...eSAT Journals
Abstract This paper describes an analytical approach to describe the areas where Pipes (used for flow of fluids) are mostly susceptible to damage and tries to visualize the flow behaviour in various geometric conditions of a pipe. Fluent software was used to plot the characteristics of the flow and gambit software was used to design the 2D model. Two phase Computational fluid dynamics calculations, using K-epsilon model were employed. This simulation gives the values of pressure and velocity contours at various sections of the pipe in which water as a media. A comparison was made with the sudden and gradual change of pipe diameter (i.e., expansion and contraction of the pipe). The numerical results were validated against experimental data from the literature and were found to be in good agreement. Index Terms: gambit, fluent software.
Split Second Analysis Covering High Pressure Gas Flow Dynamics At Pipe Outlet...AEIJjournal2
A detailed investigation covering piped gas flow characteristics in high pressure flow conditions. Such flow
analysis can be resolved using established mathematical equations known as the Fanno condition, which
usually cover steady state, or final flow conditions. However, in real life, such flow conditions are
transient, varying with time. This paper uses CFD analysis providing a split second “snapshot” at what
happens at the pipe outlet, and therefore, a closer understanding at what happens at the pipe’s outlet in
high pressure gas flow condition.
In this example air was selected for simulation purposes. In HVAC applications, such gas flow conditions
can occur in typical applications such as; air compressors releasing high pressure air through a pipe, or
compressor over pressure refrigerant gas being released into the atmosphere via a discharge pipe.
Investigation has shown that rather than a steady mass flow rate condition occurring at the pipe outlet,
calculated by the Fanno flow condition, a spiked increase in flow rate occurs at the beginning,and then
stabilizing after a few seconds, with relatively minor ripples in flow rate. Other observations were also
made and commented.
CFD results in mass flow rate were compared with the mathematically derived results, differences were
recorded. The CFD analysis showed how the k-omega turbulence model performed well, with the processor
stabilizing at an early stage.
International Journal of Engineering Research and DevelopmentIJERD Editor
Electrical, Electronics and Computer Engineering,
Information Engineering and Technology,
Mechanical, Industrial and Manufacturing Engineering,
Automation and Mechatronics Engineering,
Material and Chemical Engineering,
Civil and Architecture Engineering,
Biotechnology and Bio Engineering,
Environmental Engineering,
Petroleum and Mining Engineering,
Marine and Agriculture engineering,
Aerospace Engineering.
Explore the innovative world of trenchless pipe repair with our comprehensive guide, "The Benefits and Techniques of Trenchless Pipe Repair." This document delves into the modern methods of repairing underground pipes without the need for extensive excavation, highlighting the numerous advantages and the latest techniques used in the industry.
Learn about the cost savings, reduced environmental impact, and minimal disruption associated with trenchless technology. Discover detailed explanations of popular techniques such as pipe bursting, cured-in-place pipe (CIPP) lining, and directional drilling. Understand how these methods can be applied to various types of infrastructure, from residential plumbing to large-scale municipal systems.
Ideal for homeowners, contractors, engineers, and anyone interested in modern plumbing solutions, this guide provides valuable insights into why trenchless pipe repair is becoming the preferred choice for pipe rehabilitation. Stay informed about the latest advancements and best practices in the field.
Student information management system project report ii.pdfKamal Acharya
Our project explains about the student management. This project mainly explains the various actions related to student details. This project shows some ease in adding, editing and deleting the student details. It also provides a less time consuming process for viewing, adding, editing and deleting the marks of the students.
Cosmetic shop management system project report.pdfKamal Acharya
Buying new cosmetic products is difficult. It can even be scary for those who have sensitive skin and are prone to skin trouble. The information needed to alleviate this problem is on the back of each product, but it's thought to interpret those ingredient lists unless you have a background in chemistry.
Instead of buying and hoping for the best, we can use data science to help us predict which products may be good fits for us. It includes various function programs to do the above mentioned tasks.
Data file handling has been effectively used in the program.
The automated cosmetic shop management system should deal with the automation of general workflow and administration process of the shop. The main processes of the system focus on customer's request where the system is able to search the most appropriate products and deliver it to the customers. It should help the employees to quickly identify the list of cosmetic product that have reached the minimum quantity and also keep a track of expired date for each cosmetic product. It should help the employees to find the rack number in which the product is placed.It is also Faster and more efficient way.
Hierarchical Digital Twin of a Naval Power SystemKerry Sado
A hierarchical digital twin of a Naval DC power system has been developed and experimentally verified. Similar to other state-of-the-art digital twins, this technology creates a digital replica of the physical system executed in real-time or faster, which can modify hardware controls. However, its advantage stems from distributing computational efforts by utilizing a hierarchical structure composed of lower-level digital twin blocks and a higher-level system digital twin. Each digital twin block is associated with a physical subsystem of the hardware and communicates with a singular system digital twin, which creates a system-level response. By extracting information from each level of the hierarchy, power system controls of the hardware were reconfigured autonomously. This hierarchical digital twin development offers several advantages over other digital twins, particularly in the field of naval power systems. The hierarchical structure allows for greater computational efficiency and scalability while the ability to autonomously reconfigure hardware controls offers increased flexibility and responsiveness. The hierarchical decomposition and models utilized were well aligned with the physical twin, as indicated by the maximum deviations between the developed digital twin hierarchy and the hardware.
Industrial Training at Shahjalal Fertilizer Company Limited (SFCL)MdTanvirMahtab2
This presentation is about the working procedure of Shahjalal Fertilizer Company Limited (SFCL). A Govt. owned Company of Bangladesh Chemical Industries Corporation under Ministry of Industries.
Immunizing Image Classifiers Against Localized Adversary Attacksgerogepatton
This paper addresses the vulnerability of deep learning models, particularly convolutional neural networks
(CNN)s, to adversarial attacks and presents a proactive training technique designed to counter them. We
introduce a novel volumization algorithm, which transforms 2D images into 3D volumetric representations.
When combined with 3D convolution and deep curriculum learning optimization (CLO), itsignificantly improves
the immunity of models against localized universal attacks by up to 40%. We evaluate our proposed approach
using contemporary CNN architectures and the modified Canadian Institute for Advanced Research (CIFAR-10
and CIFAR-100) and ImageNet Large Scale Visual Recognition Challenge (ILSVRC12) datasets, showcasing
accuracy improvements over previous techniques. The results indicate that the combination of the volumetric
input and curriculum learning holds significant promise for mitigating adversarial attacks without necessitating
adversary training.
Overview of the fundamental roles in Hydropower generation and the components involved in wider Electrical Engineering.
This paper presents the design and construction of hydroelectric dams from the hydrologist’s survey of the valley before construction, all aspects and involved disciplines, fluid dynamics, structural engineering, generation and mains frequency regulation to the very transmission of power through the network in the United Kingdom.
Author: Robbie Edward Sayers
Collaborators and co editors: Charlie Sims and Connor Healey.
(C) 2024 Robbie E. Sayers
Hybrid optimization of pumped hydro system and solar- Engr. Abdul-Azeez.pdffxintegritypublishin
Advancements in technology unveil a myriad of electrical and electronic breakthroughs geared towards efficiently harnessing limited resources to meet human energy demands. The optimization of hybrid solar PV panels and pumped hydro energy supply systems plays a pivotal role in utilizing natural resources effectively. This initiative not only benefits humanity but also fosters environmental sustainability. The study investigated the design optimization of these hybrid systems, focusing on understanding solar radiation patterns, identifying geographical influences on solar radiation, formulating a mathematical model for system optimization, and determining the optimal configuration of PV panels and pumped hydro storage. Through a comparative analysis approach and eight weeks of data collection, the study addressed key research questions related to solar radiation patterns and optimal system design. The findings highlighted regions with heightened solar radiation levels, showcasing substantial potential for power generation and emphasizing the system's efficiency. Optimizing system design significantly boosted power generation, promoted renewable energy utilization, and enhanced energy storage capacity. The study underscored the benefits of optimizing hybrid solar PV panels and pumped hydro energy supply systems for sustainable energy usage. Optimizing the design of solar PV panels and pumped hydro energy supply systems as examined across diverse climatic conditions in a developing country, not only enhances power generation but also improves the integration of renewable energy sources and boosts energy storage capacities, particularly beneficial for less economically prosperous regions. Additionally, the study provides valuable insights for advancing energy research in economically viable areas. Recommendations included conducting site-specific assessments, utilizing advanced modeling tools, implementing regular maintenance protocols, and enhancing communication among system components.
Hybrid optimization of pumped hydro system and solar- Engr. Abdul-Azeez.pdf
Ansari
1. A Comprehensive Mechanistic Model for
Upward Two-Phase Flow in Wellbores
A.M. Anssri, Pakistan Petroleum Ltd.; N .D. Sylvester, U. of Akrow and C. Sarioa, O. Shoham, and
J.P. Brill, U. of Tulsa
s % 40630
Summary. A comprehemive model is formulated to predict the flow behavior for upward two-phase flow. This model is composed of
a model for flow-pattern prediction and a set of independent mechanistic models for predicting such flow characteristics as holdup and
pressure dmp in bubble, slug, and annul= flow. ‘fbe comprehensive model is evaluated by using a well data bank made up of 1,712 well
cases covering a wide variety of field data. Model pei’fortnance is also compared with six commonly used empirical correlations and the
Hasan-Kabr mechanistic model. Overall model performance is in good agreement with the data. In comparison with other methods, the
comprehensive model performed the best.
Introduction
Two-ph.a.se flow is commonly encountered in the PeVO1eum, chefi-
cal, and nuclear indushies. This frequent occurrence presents the
challenge of, understanding, analyzing, and designing two-phase
systems.
Because of the complex nature of two-phase flow, the problem
was first approached through empirical methods. The trend has
shifted recently to the modeling approach, Tbe fundamental postu-
late of the modeling approach is the existence of flow patterns or
flow configurations. Vwious theories have been developed to pre-
dict flow patterns. Separate mcdels were developed for each flow
pattern topredictflow characteristics like holdup and pressure drop.
By considering basic fluid mechanics, the resulting models can be
applied with more confidence to flow condkions other than those.
used for their development.
Only Ozon et al.] and Hasan and Kab@ published studies on
comprehensive mechanistic modeling of two-phase flow in vertical
pipes. More work is needed to develop models that describe the
physical phenomena more rigorously.
The purpose of this study is to formulate a detailed comprehen-
sive mechanistic model for upw%d two-phase flow. The compre-
hensive model fmt predicts the existing flow patm’n and then calcu-
lates the flow vtiables by taking into account the actu.at
mechanisms of the predicted flow pattern. The model is evaluated
against a wide range of experhhental attd field data available in the
updated Tulsa U, Fluid Ftow Projects (TUFFP) weU data bank. The
performance of the mcdel is also compared with six empirical cor-
relations and one mechanistic model used in the field.
FlowPattern Prediction
Taitd et al? presented the basic work on mechanistic modeling of
flow-pattern Wmsitiom forupwardtwo-phme flow. Theyidentiled
four distinct flow patterns (bubble, slug, chum, and annular flow)
and formulated and evaluated tie transition boundaries among them
Wig: 1).,Bamea et al.4 later modified the transitions to extend the
apphcabdity of the model to inclined flows. Bamea5 then combined
flow-pattern prediction models applicable to different inclination
angle ranges into one unified model. Based on these different works,
flow pattern can be predicted by detining transition boundaxks
among bubble, slug, and annular flows.
Bubble/Slug ‘Emsition.Taitel et a[.3 gave the minimum diameter
at which bubble flow occurs as.
[1dtin= 19.01 - ‘. . . . . . . . . . . . . . . . . . . . . . . . (1)
For pipes larger than this, tie basic transition mechanism for bubble
to slug flow is coalescence of small gas bubbles into large Taylor
bubbles. This was found experimentally to occur at a void fraction
C-2pyriaht 1994 SC&W of Petr&a.m Engineers
SPE Production& Facilities, May 1994
of about 0.25. Using this vatuc of void fraction, we can express tbe
transition in terms of superficial and slip velocities
VSg=0.25V, +0.333USL, . . . . . (2)
where v. is the slip or bubble-rise velocity given by
[1
%
v, = 1.53
gc7L(pL-pG)
. . .
-’--r
. (3)
This is shown as Transition A in Fig. 2.
Dispersed Bubble ltansition. Athigh liquid rates, turbulent forces
breakkwge gas bubbles down into small ones, even at void fractions
exceeding 0.25. This yields the transition to dispersed bubble flows:
()
0,5
vs.
= 0.725 + 4.15 —
‘.% + ‘SL
. . . . . . . . . . . . . . . . . . ...(4)
Thii is shown as Transition B in Fig. 2.
At high gas velocities, this transition is governed by the maxi-
mum packing of bubbles to give mdcscence. Scott and Kouba7
concluded that this occurs at a void fraction of 0.76, giving the tram
sition for no-slip d%persed bubble flow as
%E=3J7%L. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (5)
This is shown as Tramitio” C in Fig. 2.
Transition to Anmdar FIow. The transition criterion for a.nnukm
flow is based on the gas-phase velocity required to prevent the en-
trained tiquid droplets from. falling back into tbe gas stream. This
gives the transition as
[1
%guL(pL–pG)
!J~g = 3.1 —
P: ‘ ‘“””””’’’””””””’””’”””””’
(6)
shown as Transition D in Fig. 2.
Bamea5 modified the same transition by considering the effects
of film thickness on the transition. One effect is that a thick liquid
fdm bridged the gas core at high liquid rates. The other effect is in-
stability of the liquid film, which causes downw%d flow of the film
at low liquid rates. The bridging mechanism is governed by the
minimum liquid holdup required to forma liquid slug
HW> 0 .12, . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ...(7)
where HLF is the fraction of pipe cress section occupied by the liq-
uid film, assuming no entrainment in the core. The mechanism of
film instability can be expressed in terms of the modified Lockhart
and Martinelii parameters, Q and YM,
143
2. tt
B:::&E _sLUG
FLOW
t
t
CHURN
FLOW
I
D
......................................................,....“.
. . .
,.
. . . . . .
. . .
.
1
ANNULAR
FLow
To account for the effect of the liquid enmainment in the gas core,
Eq. 7 is modified here as
()
,zfw+aLc* >0.12 . . . . . . . . . . . . . . . . . . . . . . . . .. (12)
Annular flow exists if vsg is greater than that at tbe tmnsitio” giv-
en by Eq. 6 and if the two Bamea criteria am satisfied. To satisfy the
Bamea criteria, Eq. 8 must first be solved implicitly for ~ti”. Hm
is then calculated from Eq. 11; ifEq. 12 is not satisfied, annular flow
exists. Eq. 8 cm usually be solved for afin by using a se.mnd-ordm
Newton-Rapbso” approach. Tbus, EqT8 can be expressed as
F&) = YM- 2-1”5H~ FM . . . . . . . . . . . . . . . . .. (13)
WJI–1.5HH)
and
1 .5HLWM
IV&”) =
wJ1-1.5ffu)
+ (2-1.5HM)VwH~(~5.5HW)
Wm(l-1.5HW)2
. .
The minimum dimensionless film thickness is then determined it-
eratively from
F(laimj )
!lfij+, ‘ dtij-m . . . . .
J
(15)
. . . . . .. (14)
Fig. l—Flow patterns in upward fwo-phase flow.
0.01 0.1 1 10 100
SUPERFICIAL GAS VELOC3TY (M/S)
Fig. 2—~pical flow-patiern map for wellbores.
YM = 2-1”5H~ x~, . . . . . . . . . . . . . . . . . . . . . . . . .
wJ1-1.5ffm)
(8)
.[
J3SLwhere XH = ~ . . . . . . . . . . . . . ...(9)
Sc
~w = g sin O(p=-pd
()
,. . . . . . . . . . . . . . . .
dp
(10)
z ~c
and B=(l–FE)2(fr&SL). Fem geometric considerations, ffLF can be
expressed in term of minimum dimensionless film thickness, ~ti,
as
Hm=@tin(l+tin). . . . . . . . . . . . . . . . . . . . . . . . . .. (11)
144
A good initial guess is C& =0.25.
FIow-Sehavior Prediction
After tbe flow patterns me predicted, the next step is to develop
physical models for the flow behavior in each flow pattern. This step
resulted in separate models for bubble, slug, and annular flow.
Chum flow bas not yet been modeled bemuse of its complexity and
is treated as part of slug flow. The models developed for other flow
patterns ze discussed below.
Bubble FlowModef.The bubble flow model is had on Caetano’s8
work for flow in an anmdus. The bubble flow and dispersed bubble
flow regimes are considered separately in developing the model for
the bubble flow pattern.
Because of the uniform distribution of gas bubbles in the liquid
and no slippage between the two phases, dispersed bubble flow can
be approximated as a pseudmingle phase. WLtb this simptificmim,
the two-phase pammetm can be expressed as
PI’P=PLh +P&aiL....... . . . . . . . . . . . . . . . . . ..(l6)
/%=#LaL+##-&). . . . . . . . . . . . . . . . . . . . . . . . .. (17)
andvrP=v~v~L+v~g, . . . . . . . . . . . . . . . . . . . . . . . . . . .. (18)
where ).L=vJvm. . . . . . . . . . . . . . . . . . .. (19)
For bubble flow, the slippage is considered by taking into account
the bubble-rise velocity relative to the mixture velocity. By assum-
ing a turbulent velocity profile fortbe mixture with the rising bubble
concentrated more at the center than along the pipe waif, we can ex-
press the slippage velocity as
%=vg-L2vm . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (20)
Hannathy6 gave an expression for bubble-rise velocity @q. 3).
To account for tie effect of bubble swarm, Zuber and Hench9 mod~.
tied &is expression
[1
%
— H;, . . . . . . . . . . . . . . . . . . . . .
~~ = 153 WAPL-%) f
P;
(21)
3. (a) DEVELOPED SLUG UNIT (b) DEVELOPING SLUG UNIT
Fig. S-Schematic of slug flow.
where the value of n’ varies from one study to another. b the present
study, ?/=0.5 was used to give the best results. Thus, Eq. 20 yields
[1
%g%(!%k) @5 = k_l,2yM, . . . . . . . . . . . . (22
1.53 —
P; L I-HL
This gives an implicit equation for the actual holdup for bubble
flow. The two-phase flow Patzmeters can now be cafctdated tlom
P=P=P.H. +P,(l-HJ . . . . . . . . . . . . . . . . . . . . . . . . .. (23)
md#=p=pLH’+j@-ffJ. . . . . . . . . . . . . . . . . . . . . . .. (24)
The two-phase pressure gm.dient is made up of three components.
TbUs,
(a ‘($). (J (d.+ ~ + ~ . . . . . . . . . . . . . . . . .. (25)
()
dp
z,
=ppgsiutl. . . . . . . . . . . . . . . . . . . . . . . . . . .. (26)
()
p =fTPPrP%
—, . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (27)
&f 2d
where~p is obtained from a Moody diagram for a Reynolds number
defined by
N&r*. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (28)
Because bubble flow is dominated by a relatively incompressible
liquid phase, there is no significant change in tbe density of the flow-
ing fluids. This keeps the fluid velocity neady constant, resulting in
es2entiaJly no pressure drop owing to acceleration. Therefore, the
acceleration pressure drop is safely neglected, compared with the
other pressure drop components.
Slug Flow ModeI. Fermndes et al.lo developed the fmt tbomugh
physical model for slug flow. Sylvesterl 1 presented a simplified ver-
SPE Prodnctio” & Facilides, May 1994
sion of this model. Tbe basic simplification was the use of a correla-
tion for slug void fraction. These models used an impo~t 8ssump-
tion of fully developed slug flow. McQui13an and Whalley12
introduced the concept of developing flow during their study of
flow-pattern transitions. Because of the basic difference in flow ge-
ometty, the model keats fully developed and developing flow sepa-
rately.
For a fuly developed slug unit (Fig. 3a), the overall gas andfiqtdd
mass balances give
‘S$ ‘&%rB(l-HLr’?) + k%s(%ts) . . . . (29)
and v~L = (l-/Y)vmHW -~VL#LrB, . . . . . . . (30)
respectively, where
B=.%JLsw . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ..(?1)
Mass balances forliquid and gas from liquid slug to Taylor bubble
give
(v,8cc-v~)Hm =[vw(-VL,J]HL,J . . . . . . . . . . . .. (32)
and (vwv8J(l-ffm) = (VTB-V8T.J(l-HLT,J. . . (33)
The Taylor bubble-rise velocity is equal to the centerline velocity
plus the Taylor bubble-rise velocily in a stagnaut liquid colutmu i.e.,
[1
,A
Um=1.2vm + 0.35 = . . . . . . . . . . . . . . . . . (34)
pL
Similarly, the veloci~ of the gas hubbies in the liquid slug is
1/.
[1
“gu= 1.2,”,+ 1.53 -. PA, . . . . . . . . . .. (35)
P?
where the s=ond term on tfte right side represents the bubble-rise
velocity defined in Eq.21.
‘fhevelocityofthe falliigfimcanb+ correlatedwitbthe film
thickness with the Brotz13 expression,
VLm==, . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (36)
where fiL, the constant film thickness for developed flow, can be ex-
pressed in terms of Taylor bubble void fraction to give
vm=9.916[gd(l-&) ]W. . . . . . . . . . . . . . . . . . . . .. (37)
145
4. Tbeliquid slug void fraction can be obtained by Sylvester’sll cor-
relation and fmm Femandes et al. ‘slo and Schmidt’s 14 data,
Vss
‘Sm = 0.425 + 2.65vm”
. . . . . . . . . . . . . . . . . . . . . . . .. (38)
Eqs. 29 or 30,31 through 35,37, &d 38 can be solved iteratively
to obtain the following eight “&mnvns that Min. the slug flow
modck & HLm, H81.s, V8TB, VLTB, VgU, VI,LS, and vrB. Vo and Sho-
ham15 showed that these eight equations can be combined algebra-
ically to give
(9.916 @)(l-_~H,,HVTB(l-H,TB) +x= 0,
. . . . . . . . . . . . . . . . . . . . .. (39)
.[vm.HgH[l.53[-~(1-H,u)O}].
..’ . . . . . . . . . . . . ..”..- . . .. (40)
With VB and Hgf-s given by Eqs. 34 and 38, respectively, ~ can
be readily determined from Eq. 40. Eq. 39 is then used to fmd HLm
with an iterative solution method. De fting the left side of Eq. 39 as
F(ffLT,s), then
F(HU,) = (9.916 @( I--)05HLrurB(I-HLm) +.l.
. . . . . . . . . (41)
Taking the derivative of Eq. 41 with respect to HLTB yields
F’(ffm) = VTB + (9.916@
[
x (1--0’+
HLTB
14J~”
.. . . . . . . . . . . . . . . . . . . . .. (42)
HLTB, the root of Eq. 39, is then determined iteratively flom
F(HL@
H
ErBj+L = ‘LT8j-q . . . . . . . . . . . . . . (43)
The step-by-step pmcedme for determining all slug flow vari-
ablesis as follows.
1. Catculate WB and HgLS from Eqs. 34 and 38.
Z. Using Eqs.40tbrough 43, determine H~TB. A good initial
guess is HLTB=O.15.
3. Solve Q. 37 for VLTB. Note that HgTB=I-HLTB.
4, Solve !3q. 32 for v~. Note that HI,U=l-H8M.
S. Solve Eq. 35 for Vg=.
6. Solve Eq. 33 for vgTB.
7. Solve ~. 29 or 30 forff.
,8. Assuming that& =30d, calculate ,&u and LTB from the defini-
tion of~.
To model developing slug flow, as in Fig. 3b, we must determine
the existence of such flow, This requires calculating and comparing
the cap length with the total length of a developed Taylor bubble.
The expression for the cap length is12
[
2
LC=&II~a+_ I-H
1~NLm(~L,B)-&, ..........(44)
where WgTB and HNUB me cahlated at the terminal film thickness
(called NusseIt fhn thickness) given by
[ 1
113
~N= ;dVNL.B#L(l-ffNLIB)
8(PL-P,)
. . . . . . . . . . . . . . . . . .. (45)
146
TIE geommy of the film flow gives HNUB in terms of 8N as
()
2
HNH. =l- 1-$ . . . . . . . . . . . . . . . . . . . . . . . . . . .. (46)
To determine vNgTB, the net flowrate of & can be used to obtain
“Ngm=vrB_ (”T8_”gM)-. . . . . . . . . . . . . . . . . . (47)
Tbe length of the liquid slug can be calculated empirically from
LU=C’d, . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . (48)
where C’ was found16to vary from 16t045. Weuse C’=30 in this
study. This gives the Taylor bubble length as
Lm=[LH/(l#)I& . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (49)
From the comparison of& and LTB, if & ? LTB, the flow is devel-
oping slug flow. This requires new values for L~, f&, and
V&B calcula~d emherfor developed flow.
For L&., Taylor bubble volume can be used
‘iB
% =
~
A~(L)dL, . . . . . . . . . . . . . . . . . . . . . . . . . . .. (50)
.
where A& can be expressed in tennsof local holdup hLTB(L),
which i“ turn can be expressed in terms of velocities by using Eq.
32. This gives
‘~JL)=[l-(vr=i(51)
The volume w be expressed in terms of flow gmmetry as
()
L% + Lu
Grz= YsgAp ~ -vgDAP(l–HuJ:. (52)
Substitution of Eqs.51 md52into Eq.50 gives
()
L~ + LU LB
VS* — -V@(l–HIM) ~
‘TB
%
‘1[
~_(v,,- vu)Hm
Jzz
1
do.....................
.
(53)
F.q. 53 can be integrated and then simplified to give
~~+(yP~+5=054)
where u=-v~g~, . . . . . . .. . . . . . . . . . . . . . . . . . . . . . . .. (55)
~ = %-YSU(2-HJ
%
LLS, . . . . . . . . . . . . . . . . . . . . . . . .. (56)
~nd ~ = %-vu
—Ifw. . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (57)
&
After calculating L$8, the other local parameters can be calcu-
lated from
V:rB(O= ~-VIZ . . . . . . . . . . . . . . . . . . . . . . . . . . .. (58)
(vTrvU)HU
‘d ‘:” ‘L; ‘ Jz
. . . . (59)
In calculating pressure gradiems, we consider the effect of vary-
ing film thickness and neglect the effect of friction along the Taylor
bubble.
SPE production&Facilities, May 1994
5. For developed flow, the elevation component occurring across a
slug unit is given by
()y =[(l-i$pts +~pglgsinO, . . . . . . . . . . . . . . . . .. (60)
dLe
where pU=pLHm +pJ1-Ifu). . . . . . . . . . . . . . . . . . .. (61)
The elevation component for developing slug flow is given by
()A ‘[(l~*)pU +B*pm.lgsinO, . . . . . . . . . . .. (62)
dLe
where prm is based on average void fraction in the Taylor bubble
section witi varying film Wlckness. It is given by
P,B. =p,HLm+P,(l-Hma), . . . . . . . . . . . . . . . . . .. (63)
where HLTLM is obtained by integrating Eq. 59 and dividing by L*m,
giving
2(uTrYw)Hm
HL7BA =
&G%-
. . . . . . . . . . . . . . . . (64)
The frictio’n component is the same for boththedeveloped and de-
veloping slug flows because it occurs only across the liquid slug.
This is given as
(.)
dp
=f_(l~), , . . . . . . . . . . . . . . . . . . . . . . . .. (65)
m,
where ~should bereplaced by,O*for developing flow. f~canbe
calculated by using
‘R,U =pUvmd/pB. . . . . . . . . . . . . . . . . . . . . . . . . . . .. (66)
For the pressure gradient due to acceleration, he velocity in the
@lm must be considered. The liquid in the slug experiences decel-
eration as its upward velocity of VLLS changes to a downward veloc-
ity of VLTB. The sm. Iicpid atso experiences acceleration when it
exits from the film with a velocity VLTB into an upward moving liq-
uid slug of velocity VT-I-S. ff the two changes in the liquid velocity
occur within the same slug unit, then no net pressure drop due to ac-
celeration exists over that slug tmh.’f hishappens when tbe slug
flow is stable. The correlation used for slug length is based on its
stable length, so the possibility of a net pressure drop due to accel-
eration does not exist. Therefore, no acceleration component of
pressure gradient is considwed over a slug unit.
Annular Flow ModeL A discussion on the hydrodynamics of annu-
h flow was presented by Wallis. 17 Along with this, WafIis also
presentd tie classic correlations for entrainment and interracial
friction as a function of film thickness. Later, Hewitt and Hall-Tay-
lorlg gave a detailed analysis of the mechanisms involved in an an-
nular flow. AI1 the models that followed later are based on this ap-
proach.
A fully developed annular flow is shown in Fig 4. The conserva-
tion of momentum applied separately to the core .amd the fdm yields
()A.% -zj~t-p.A.gsin6’=0 . . . . . . . . . . . . . . . . . . .. (67)
c
()
*and AP ~ +riSi–rpSF-pLAFg sin6= O. . . . . . (6g)
F
The core density, PO is a no-slip density because the core is con-
sidered a homogeneous mixture of gas and en fmined fiquid droplets
flowing at the same velocity. Thus,
PC= PL&C+P&aLC), . . . . . . . . . . . . . . . . . . . . . . . .. (69)
FEv~L
where ,IK = —.
‘SX + ‘EVSL
. . . . . . . . . . . . . . . . . . . . . . . . .. (70)
SPE production& Facilities, May t994
GAS CORE—
LIQUID FILM—
ENTRAINED
LIQUID DROPLET-
VF
ST“1. .“.
I
-.. ..-. .. .. . ....
. . . .. . ,~ .“
.
‘F
rF
i
-e
8Dc -
i
Fig. 4-gchematic of annular flow.
FE is the fraction of the total liquid enmined in the core, given by
wallis as
FE = l-sxP[4.125(u.,+~ 1.5)1, . . . .; . (71)
where uCtir=lO, OOO~(~)fi. . . . . . . . . . . . . . . . . . . .. (72)
The shear stress in the film can be expressed as
$
rF=f#L~. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (73)
where f~ is obtained from a Moody diagram for a Reynolds number
defined by
pLvFdHF
—, . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (74)N~t, = ~L
where vF=_=w . . . . . . . . . . . . . . . . . ..(75)
~ddHF=@(14Jd .. . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (76)
This gives
[- 1
2
f_
ZF=. @-FJ’P~ &4J . . . . . . . . . . . . . . (77)
147
6. Eq. 77 reducks to
()
~F _ d (l-FE)z f~ d~
4 [4C!(ldJ]2f~L dL ~L
, . . . . . . . . . . . . . . . . . . . .. (78)
where the superfmid liquid friction pressure grad~ent is given by
()
dp _ .fsLPLv&
——, .,, ,,, ,,, ,,, ..,,,,, ,,, .,,,,, ,,,
z
SL
2d
(79)
fiL is the fdiO. f?iCtOr for Supefi.ial liquid velocity and can be
obtained from a Moody diagram for a Reynolds number defined by
N ~$L=pLv,Ld/pP . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (80)
For the shear stress at the interface,
Ti=~jPc!J~/8, . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (81)
where vC=v~c/(1-2c3) z . . . . . . . . . . . . . . . . . . . . . . . . . . .. (82)
and~=fScZ, . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (83)
where Z is a correlating factor for in ferfacial friction aid the fibn
thickness. Based on the performance of the model, tie Wallis ex-
p~ssion for Zworks well for thin films or high entminments, where-
as the WhMey and Hewitt19 expression is good for thick tilnts or
low entittments. ‘fbu.s,
Z=l+300~ for FE> 0.9 . . . . . . . . . . . . . . . . . . . . . . . . . (84)
mdZ=l+24($1’3~ for FE <0.9. . . . . . . . . . . . . .. (85)
Combining Eqs. 81 through 83 yields
()
~,_d Z dp
4(1-2@4 ~ SC’
. . . . . . . . . . . (86)
The supetilcial friction pressure gradient in the core is given by
(*)sc=f- (87)
wherefSc is obtained from a Moody diagram for a Reynolds number
defined by
N%
=pcv’#i//4,” ., . . . . . . . . . . . . . . . . . . . . . . . . . . .. (88)
vsc = FEW + VS8, . . . . . . . . . . . . . . . . . . . . . . . . . . . . .. (89)
and#c=pJU +p,(l-,lLc), . . . . . . . . . . . . . . . . . . . . . .. (90)
Tbe pressure gradient for annulw flow can be calculated by sub-
stituting the above equations into Eqs. 67 and 68. llns,
($JC=*(*),C +pwsin6’ . . . . . . . . . . . . . ..(9l)
()
~d @ _ (1-FJ2 f, &
dLF
()()*-3(1~~3 f,’ d ~
()
dp
+p&slne. . . . . . . . . . . . . . . .
-4&f&@3 m ,C
(92)
The basic unknown in the above equations is the dimensionless
film thickness, ~. An implicit equation for ~ can be obtained by
equating Eqs.91 and92. This gives
()
dp
4’XIJWW5 = ,C-(p’-pc)gsine
()
(l-FE)z fF dp
_—— —
64d3(ldJ3fSL W ~L
=0. . . . . . . . . . . . . . . .
—
. . . . . .. (93)
To simplify this equation, the dimensiodess approach developed
by Alves et aL20 is used. This approach defines the following d~.
mensionless groups in addition to previously &tined modified
Lockhart Mutinelli parameters, XM and l’M.
~;= (dp/dL)c-gpcsin8
(dp/dL)xc
(dp/dL)F -gPL sin 9
and& =
(dp/dL)~L “
. . . . . . . . . . . . . . . (94)
. . . . . . . . . . . . . . . . . . . . .. (95)
By using the moditied Lockftart MartineHi parameters, Eq. 93 re-
duces to
WM
y~-4d(l&.5(14J]25 —=0. . . . . . . .. (96)
+ [Q(14J]3
l%. above eqwtions can be solved iteratively to obtain &If Eq.
96 is F(&), then taking the derivative of Eq. 96 with respect to ~
yields
.zt4(l-21)]
“@ ‘[@(14J12[14_(14JI~5
-4a(14J[l%_(14J] 2.5
2.5Z[4( l-@]
3x;[4(~_@]
-@(l-@ [14@d)]35- [@(l+)]’
. . . . . . . . . . . (97)
& the root of Eq. ;6. 77ftus,
.: . . . . . . .. (98)dj+,=b.-~. ....................
-J F@j)
Once &is known, the dimensionless groups #F andcjc can be ob-
fained from the followhg form of Eqs. 91 and 92
@~=_Z.-
(1-tiJ5
. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ..(99)
{drz=l.
....................(100)
Alves20stated that Eq. 100canbe expresseda$
~; = %+-YM
~
. . . . . . . . . . . . . . . . . . . . . . . . . . . . . . . ..(101)
The total pressure gradient can then bc obtained from either F.q. 94
or 95 because the pressure gradient in the film and core must be the
same.’fhus,
Or(*)==($)F=@~(*)w+gpsin6(103)
Note that the above total pressure gradimt equations do not in-
clude accelerational pressure gfadient. ‘fhis is based on results
found by Lopes and Dukfer21 indicating that, except for a limited
range of high liquid flow rates, the accelerational component result-
SPE Production& Facilities, May 1994
7. TABLE l—RANGE OF WELL DATA
Nominal Diameter Oil Rate
Source
Gas Rate Oil Gravity
(in.) (STBID) (MSCFID) (“API)
Old TUFFP’ Data I108 01010,150
Bank
1,5 to 10,567 9.5 to 70,5
Govier and 2t04 8 to 1,600 114 tO 27,400 17t0 112
Fogaras%
Asheim23 2718 tO 6 720 to 27,000 740 to 55,700 35 to S6
Chierici et aI,Z4 27L3 to 5 0.3 to 69 6 to 27,914 8.3 to 46
Prudhoe Bay 5% to 7 600 to 23,000 200 to 110,000 24 to 66
.Includes data from Poenmmn and Catwnter,= Fmcher and Brown,% Ha9edom,27 Baxendall and 7homas,28 0rkiszews!4 ,29
ESPmOl,m MMSU18.M,3* canacho,~ and field dti from seveml 03 cnmPanias.
ing from the exchange of liquid droplets between the core and the E3 indicates the degree of scattering of the errors shout their average
film is negligible. value.
Average ermc
Evahtation
The evaluation of the comprehensive model is can’k?d out hy
compming tie pressure drop from the mcdel with the measured data
in the updated TUFFP well data bank that comprises 1,712 well
cases with a wide range of data, as given in Table 1. The perfor-
mance of the model is also compared with that of six correlations
and another mechanistic model tlmt am commonty used in the petro-
leum indus~.
Criteria for Comparison with Data
The evaluation of the model using the databank is hazed on the fol-
lowing statistical parameters
Average percent error:
(104)
()
.E,= +~eri x100, . . . . . . . . . . . . . . . . . . . . . . . .
r. ,
APM-APi.. . .
where ed = . . . . . . . . . . . . . . . . . . . . . . .. (105)
Apiw
EI indicates the overatt trend of the perfommce, relative to the
measured pressure drop.
Absolute average percentage error
()
“
E,= ~~le.1 x1OO. . . . . . . . . . . . . . . . .
i.1
. . . . . . . . (lo6)
Ez indicates how large the errors are on the average.
Percent standard deviation
()
“
E,= }~ej , . . . . . . . . . . . . . . . . . . . . . . . . . . . . .
i= 1
(108)
where e; = ApjCOIC-Api~,.r . . . . . . . . . . . . . . . . . . . . . . .. (109)
E4 indicates the overall trend independent of the measured pressure”
dzop.
Absolute average errcx
-()
.Es= ;~lefl . . . . . . . . . . . . . . .
i= 1
(1 10)
Es is ASO independent of the measured pressure drop and indicates
the magnitude of the average error.
Standard deviation
rE,= j (e,;_J2—.. . . . . . . . (111)
,= ,
E6 indicates the scattering of the results, independent of the mea-
sured pressure drop.
Criteria for Comparison With Other
Correlations and Models
The ccmelations and models used for the comparison area modified
Hagedorn and Bmwn,z7 Duns andROS,330rkiszewski29 with Trig-
gia correction,~ Beggs and B2i1135 with Palmer correction,36 Muk-
heriee and Brill.37 Aziz et al.. 38 a“d RISLUI and Kabir.239 The com-
pmison is accomplished bycomp.ming the statistical parameters.
The comparison involves the use of a relative performance factor
defined by
.
J__
(eri -El)z IE,I-IE,J E2-E2
E3. ~ — . . . . . . . . . . .
n-1
(107) F. =
1?21 I-IE1 .1 +-
j= I m nun
MOEL
HAGBR
Azlz
DUNRS
HASKA
BEGBR
ORKIS
MUKSR
EDB
1712
0.700
0.665
1.312
1.719
1.940
2,982
4,284
4.883
WV
—
1086
1,121
0.600
1.108
1,678
2.005
2.906
5.273
4.647
TASLE 2-RELATIVE PERFORMANCE FACTORS
DW VNH__@~ ANH AB
626
1.378
0.919
2.085
1,678
2,201
3.445
2.322
6.000
755
0.081
0.B76
0.803
1.711
1.836
3,321
5,836
3,909
1381
0.000
0,774
1,062
1.792
1,780
3,414
4.688
4.601
29
0.143
2.029
0.282
1.126
0.009
2.82s
1.226
4.463
1052
1.295
0.386
1.798
2.056
2,575
2,S83
3.12S
5,342
654
1.461
0.485
1.764
2.028
2.590
2.595
3.316
5.140
SNH
745
0.112
0.457
1.314
1.852
2,044
3.261
3.551
4.977
VSNH AAN
—
387 70
0.142 0.000
0.939 0,546
1.486 0,214
2.298 1.213
1,996 ‘ 1.043
3,262 1.972
4.403 8..::
4.683
!BD.e.tim databank VW..erma! well caseq Dw=detia!ed well cases VNH.VB,liC4 wll ea$e$ without H.g8dom and Brown dam ANH41 well cases Wi!hout Hagedorn and
3mw” data A&d wll cams with 75% bubble fluw AS41 well cams with 100% slug 110!+ VS=vetical well cams with 100% slug flow SNH=dl w.U cases wilh100% s[ug flow
Without Hagtiorn and Brow. dal% VSNH=vec7ica wII cases with 100% slug flow Wm.! Hagedorn and Bmn dalx ,&AN4] well oases w%h 100% annular flow HAGBR.
I.gedom and Brown corrwti.n; A217.=A2iz.! .1. cormlatlm DUNRS=Dun3 and R.. com!atiow HASKA=H.Sa. and Kabir mechmlstic modet BEG8R=Bww and .3rl! corml%x
)RKIS.OrWzews.ki cerrela!iox MUKBR=Mukherjee and 8till correlation.
8. E,-E, IE41-IE4 I
- + m“
+ E3mm-E3dn IE4JIE, I
nun
ETE5mh E=E6Mn
+ E5m-E5ti + E6mu–E6&’
. . . . . . . . . . . . . . . . . . ,. (112)
The minimum and maximum possible vafues for Fw are O and 6,
intilcating the best and worst performances, respectively.
The evacuation of the model in terms of Fw is given in TabIe 2,
with the best value for each column being boldfaced.
OveraU Evahmtion. The ov?rall evaluation involves the entire
comprehensive model so as to study the combined petionnance of
all the independent flow pattern behaviomnodels together The eval-
uation is first performed by using the entire &ta bank, resulting in
COL 1 of Table 2. Model performance is also checked for vertical
well cases only, resulting in Col. 2 of Table 2, and for deviated weU
cases only, resulting in CoL 3 of Table 2. To make the comparison
unbiased with respect to fbe correlations, a second datsba.w was
created that excluded 331 sets of data from the Hagedorn and Brown
study. For this reduced data bank, the results for all vertical well
cases are shown in Col. 4 of Table 2, and the results for combined
veticaf and deviated weil cases are shown in COL 5 of Table 2.
Evaluation of Individual Ftow Pattern ModeLs. ~e perfmmance
of individual flow pattern models is based on sets of data that m
dominant in one particular flow pattern, as predicted by the bansi-
tions described earlier. For the bubble flow model, well cases wifh
bubble flow existing for more than 75% of the welf length we con.
sidered in order to have an adequate rmmber of cases. These results
are shown in COL 6 of Table 2. Cols. 7 through 10 of ‘Rable 2 give
results for well cases predicted to have slug flow exist for 100% of
tbe well fength. The cases used for COL 7.and 8 were selected from
the entire data bmk, whereas the cases used foc Cols. 9 and 10 and
11 were selected from the reduced data bank fhat eliminated the
Hagedorn and Bmum data, which is one-third of all the vertical well
cases. Finally, Col. 11 of Table 2 gives results for those cases in the
10M data bank that were pmdkxed m be in a.mmlar flow for 100%
of the well length.
Complete performance results of each model or correlation
against idvidual statistical parameters (El, E6) are give” in the
supplement to this paper.m
Conclusions
From Cofs. 1 through 11 of Table 2, the performance of the mcdel
and other empiricaf correlations indicates the fcdSowing,
1. The overall perfomumce of the comprehensive mcdel is s“pe-
rior to afl other me fhods considered. However, the ovemfl perfofm-
a.nces of the Hage.dmn and Brown, Aziz et aL, Duns and Rm, and
Hasan and Kabir models are comparable to that of the model. For
the last three, this can be attributed to the use of flow mechanisms
in these methods. The excellent performance of the Hagedorn and
Brown correlation can be explained cmly by tie extmsive data used
in ifs development and modifications made to the correlation. In
fact, when the data without Hagedorn and Brown wetl cases are com
sidered, the model pmfonned the best (Cols. 4 and 5).
2. Although the Hagedorn and Brown correlation perfmmed bet-
ter than the other correlations and models for deviated wells, none
of the me fbods gave satisfacto~ results (Cccl. 3),
3. Only 29 well cases were found with over75% of the well length
predicted to be i“ bubble flow. The model performed second best to
the Efasan and Kabir mechanistic model for bubble flow (Col. 6).
4. The petiotma.nce of the slug flow model is exceeded by fhe
Hagedorn and Bmvm correlation when the Hagedorn and Brown
&ta are imluded i“ the data bank (Cols. 7 and 8). The model per-
formed best when Hagedorn and Brow” data are not included for all
well cases and all vertical well cases (Ccds. 9 and 10).
5. The performance of the annufar flow models is significantly
better than all other methods (Col. 11).
6. Several variables in the mechanistic modeI, such as bubble rise
velocities and film thickness, we dependent cm pipe inclination
angle. Modifications to include inclination angle effects on these
variables should fmther improve model performance.
Acknowledgments
We thank the TUFFP member companies whose membership fees
were used to fund part of fbis reseacb projecf, and Pakistan Petro-
Ieum Ltd. for the fnancial support provided A.M. Ansari.
References
L Ozon, P.M., Ferschmider, G., and Chwekoff, A.: “A New M.kiphme
Flow Model Pdicm Resmre and Temperature Profiles? paper SPE
16535 presented al the 1987 SPE Offshore Emope Ccmference, Aber-
deen, Sept. S–1 1, 19S7.
2. Hamn, A.R. and Kabir, C, S,:“A Smdy of Mulfiphase flow Behavior in
Verticaf VMts,” SPEPE (M&y 1988) 263.
3. Taitel. Y.. Bamea. D.. and Dnkter. A.E.: “Moddline Flow Paftem Tmn-
Sitio”s for Steady Upward Gas-Liquid Flow in VeI%l Tubes,” AIChE
J. [1 9$4)> 26.345.. . ... . .. —.,-.. .
4. Barnea, D., Shoham,O..amlTahel, Y: “F1.aw PattemTnusitionfor VeI-
dcat Dow”ward Two-Phase t%w,” Chem E.g. Sci. (1982) 37, 74I.
5. Bamea, D.: “A Unified Model for Predicting Flow-Pattern Tmnsiti.m
for tie Whole Raoge of Pipe inclinations; Intl. J. Mulliphase Flow
(1987) 13,1.
6. Hammthy, T.2 “Velocity of Lacge Drops and Bubbles i“ Media of Inti-
nite m Remitted Extent,” AJChEJ. (1960) 6,281.
7. SCOR, S.L. and Kouba, G.E.: “Advances i“ Slug Flow Characterization
for Hmimrdat and Slightly Imfimd P@efines? P2P,, SPE 20628 pr-
esented at the 1990 SPE Annw.t Technical Cmference and Exbibitim,
New Odans, Sept. 23-26.
8. Caetano, E.F.: ‘Upward Vertical llvcHimse ROW T&o.gh an .&mu-
lus~ PhO dissmta[ ion, U. of Tulsa, T“!m, OK (1985).
9. Zuber, N. and Hench, L: “Sfeady Stale and Transient Void Fraction of
Bubbti”E Systems and 2fmir operating Limits. par! 1: Steady Mate Op.
erafion,” Genemt Electric Report 62GL1OO (1962).
10. Femandes, R.C., Setnaih T., and Dukfer, A.S.: “Hydmdynandc Mcdel
for Gas-Liquid Slug Flow in Vemicaf Tubes,” A{ChEJ. (1986) 29,981.
IL Sylvester, N,D.: “A Mechanistic Model for ‘fWo-Phase Verdcaf Slug
Flow in Pipes; ASMEJ, Energy Rcwumes Tech. (1987) 109,206.
12. McQnilIan, K.W. and Whalley, P.B.: “Flow Patterns in Vecricd Tvm-
Phase Flow” 1“/1, J. Mdtiphas, Flow (1985) 32, 161.
13. Brotz, W.: VJber die Vmausberechmmg da Abm’ptiomgesch-windiS-
keit von Gasen in Stmrnemkm Ftumiekeitsscbicbkn.” Chem. Ire-. Tech,
(1954) 26,470.
14. Schnd&, Z.; Expenmnml Study of Gas-L@td Flow inaPipeline-Riser
.fY.fm MS fJmis. U. of TM.% Tds. (1976).
15. Vo, D.T. and Shoham, 0.: ‘*A Note on the Existence of a Solution for
‘Rvo-Fbase S1ug Ftow i“ VertimJ Fipes? ASME J. Energy Rexxoces
Tech (19S9) 111,64.
16. Dukler,A,K, MaroD, D. M., and Branmr, N.; C<APhysical Model forpr~
dictf.g the Minimum Stable Slug La@? Chem, E.g. Set. (1985)
,.70....,
17. Wallis, G.B.: One-Dinemimxd Two-Phase Flow, McGmw-Hill Book
Co. Inc., New York Citv (1969).
18, lfewi~ G.F. and ffall-~aylor, N.S.: Annular Two-Plw.w F@ Perga-
mo” F?es$, H.mtm (1970).
19. Whalley, P.B. and Hewitt, G.F.: ‘T’& Cormladmof Liquid Entrainment
Fracfim and Erdminmmt Rate i“ Annular Two-Phase Flow” URAEA
Repwi AERE-R9 187, Harwell (1978).
20. Alms, 1.N. @taI,: “ModdinS AmmlarFlow BduwiorforGas WeJls,;,pa.
per pmsemc?d m fbe 19S8 Wimer Amual Mee6m3 of ASMF& Chicago,
NOV. 27-Dee. 2.
21. Lopes, J.C.B, and Dukfer, A.E.: “Droplet Entmimnmt in Verdcaf Aruu-
IarFlow and Its Ccmtibution to Mommtwn Tram fer~A!ChEJ. (1986)
15rNl
22. Goviq G.W. and Fogarasi, M.: “pressure Dmp i“ Wells producing Gas
and Co”demate.” J, Cdn, Pet. Tech (OCt.-Dec. 1975) 28.
23. Ash.im, H.: “MONA, An Accurate Tlvo-Pbaw Well FlowModel Bawd
on Phase Slippage,” SPSPE fhls.y 1986) 221.
24. Chierici, G,L., Ciucci, G.M., and Sclccchi, G.: ‘Two-Phase Vertical
Flow in Oil Wells-prediction of @ssure Dmp,’’JPT(Aug. 1974) 927.
25. Poemmmn, F.H. and Carpenter, P.G.: ‘The Muldphax HOW of Gas, Oil
and W.mfTbrougb Vmdmf Flow Strings with Application to the. Design
and Gas-Lift fnstallations~ Drill. & Prod Pmt., API, Dallas (1952)
257.
150
9. 26. F?acher, G.H,, and Brown, K.!2 TrvXctio. of pressure Gradiem$ for
Multiphase F30W in T.bing,” Tram.. AfME (1963) 2.%, 59.
27. Hagedorn, A.R.: ‘E.qmimental SmdyofRessure Gradients &curring
during Continuous ‘fW*Phase Flow in Small Diameter Verticaf Con.
dubs,” PhD dissertation, U. of Texas, Austin (1964).
28. Baxendell, P.B.: ‘The Calculation of Pressure Gradients in High Rate
Flov?i”g Wells; JPT (Oct. 1961) 1023.
29. Grkiszewski, J.: %edicdng Two-Phase ~SSm DrOPS in VtiCal
Pip.%” JPF’(Jme 1967) 829.
30. f?.spanol, H.J.W ‘~cmnparisonof Three Methods fore?.lculating aFms-
sure’hveme i“Verticd Mulfi-Phase Flow,” MS thesis. U. of2Msa.Tul-
sa, OK (1968).
31. Messufam, S.A.G.: “Comparison of Correlations for Redicting Muki-
phase 3%wimgprewre f.nsms in Verdcal PiF@s.” MS thesis. U. oPDd-
S+ Ttdm, OK (1970)
32. Camach.a, C.A.: “comparison of Correlations for PTedcdng Ressure
Losws inHQh Gas-Liquid Ratio Vedicrd WelisYMS fhesii. U. ofTulsa,
‘fuka, OK (1970).
33. Duns, H. lr. and Ros, N.C.3.: “Vertical Ftow of Gas and Liquid Mixtures
in Wells.” Pmt.. 6fb World Pet. Con% (1963) 451.
34. Brill, J.P.: ‘Discontimilies in the Orfi=wsid Correlation for predict-
ingpressure-enfs in Wells,” J. E.eqyRes. Tech, (M.xch, 1989)41,
34.
3S. Beggs, H.D. and Bdll, J.P.: “A Sfudy of Two-Phase Flow in fnctiied
Pipes, - JPT(?vfay 1973) 6+77.
36. Palmer, C.M.: ‘.Evalua60n of fnclimd Pipe Twc-Phase Liquid HoldIIp
Correlations Using Expetimmcal Data,” MS thesis, U. oflldsa. Tu@
OK (1975).
37. Muklmjee, H. and Brill, J. P.: “Ressure Drop Correlations for fnctined
‘IVc-Phase Flow,” J. Energy Res. Tech. fDec. 1985).
38. tiIz, K, Govier, G.W., and Fogarasi. M.: “pressure Drop in Wells Re-
ducing Gil and Gas,” J. Gin. P.L Tech. (July-gept. 1972) 38.
39. Kabir, C.P., and Hasan, AR.: “performance of a TWo-Phase GadLiquid
Flow Mcdel i“ Vmical Wells,” JPSE (1990) 4,273.
40. .4mari, A.M. et d,: ,’Supplement to paper SPE 20630, A Comprehm-
sive Mechanistic Mcdd for UpwardTWc-Pba.$e Flow in WeUbores,”pa-
per SPE 28671 available at SPE headquarters, Richardson, TX.
Nomenclature
a = coefficient defined in Eq. 55
A = cross-sectional area of pipe, L, m2
b = coefficient defined in Eq. 56
c-= cceffkient defined in Eq. 57
C = constant factor relating friction factor to Reynolds
number for smoofh pipes
C’= coefficient defined in Eq. 48
d. pipe diameter, L, m
e = error function
El= average percentage error, %
E2 = absolute average percentage error, %
Es= standard deviation, %
E~ = average error, miLt2, psi
ES= absolute average error, mlL12, psi
Es= standard deviation, mlLt2, psi
f= friction factor
FE . fraction of liquid entrained in gas core
FT = relative performance f=tor, defined in Eq. 112
g = gravity acceleration, m.fs2
h = local holdup fraction
H. average holdup &action
L. Iengfb along the pips, m
n = number of well cases
z’= exponent to account for the swarm effect on bubble
rise velociw
NW= Reynokk number
~ = pressufe, m/Lt2, psi
q = flowrate, L3{t m3fs
s. wetted perimeter, L, m
v = velocity, Ut mls
V= volume, L3, m3
X= Lockhart and Marti”elli parameter
Y= Lockhart and h’fardnelli parameter
Z = empirical factor defining interracial friction
~ = Iengfb ratio, defined in F.q. 31
C5 = fdm thickness, L, m
C3 = ratio of fti thickness to diameter
X = difference
s = absolute pipe m@mss, L, m
@ = angle from horizontal, md or &g
A = no-slip holdup fraction
P = dynamic viscosity, kg/ins. kghr$
v = kinematic viscosity, L21t, m21sq
p = density, mJL3, kg/m3
~ = Solace Ensio”, mltz, dynelcm
r = shear stiess, @Lt2, Nlm3
@ = dimensionless groups defined in Eqs. 94 and 95
Subscripts
a = amelera,tion
A = average
c = Taylor bubble cap, core
crit = critical
e = elevation
f. friction
F= film
g.ga3
H = hydraulic
i = ith element
I= interracial
L = liquid
IS= liquid slug
m . mixture
M. modified
mu= maximum
mill . Inil-hum
N= Nimselt
p = pipe
r = relative
s = slip
S = superficial
SU = slug unit
t. total
3“B = Taylor bubble
TP. two-phase
Supermript
* = developing slug flow
S1 Metric Conversion Factor
in. X2,54* E+OO = cm
T.mvmhn factor is exact SPRPF
OIIOi.4 SPE ma.u!ctipt mceiv@d for review Sept. 2, 1930. Revb%d mm.szrht -bed
Sept. 2s, 1993. Paw? acmpted lor Lmbl!cation DWC 6, 1993. F’awr (SPE 2Ce30) fimt Pr6-
~#:2~ 1990 SPE Annual Tecim@d Cnnfemnm 4 Ei+M+io” held i“ New Orbs.,,
1
SPE production.9 Facitides. May 19P4 151
10. A CONL)REHENSIVE MECHANISTIC MODEL FOR UPWARD
10 TWO Pm SE FLOW I N WELL130RES. Jwuu!UQ.
High.Water.Cut Gas Wellst SPE Prod, Eng, J, (Aug.
1987), 165-177,
26Chlerlol, G. L,, Culeol, Q, M, ,and Soloccl, G,: ‘Two.Phase
Vertical Flow In 011 Wells .. Predlotlon of Pressure
Drop,” SPE J. Pet, Tech. (Aug. 1974), 927-938.
26 Poet? mann, F, H., and Car penter, P. G,: “The
Multlphase Flow of Gas, “011 and Water
Tht ough Vertical Fiow Str Ings with
Application to the Design of Gas. Lift
Installations, ” API Drllllng and Produotlon
Prlictlaes, 257- 317 (1962).
27 Fanoher, G. H., and Brown, K. E,: “Pr edlc4 Ion
of Pressure Gradients for Multi phase Flew In
Tubing, ” Trans. AM4E(1 963), u, 59-69.
28 Hagedorn, A, R,: ~~
~lRa.d
~, Ph, D.
Dissertation, The University of Texas at
Austin (1964),
28 Baxendell, P, B,: “The Caloulatlon of Pr es$ure
Gradients in High Rate Flowing Well),’ SPE
J. Pet, Tech, (@S, 1961), 1023.
300rklszew sKI, ..t,: “Predicting Two-Phase
Pressure Drops in Vertical Pipes,’ SPE J.
Pet, Tech. (June 1967), 829=838.
31 Espanoi, H, J. H.: Q21tlfJJf~ff
~~
lRMLWU4ulikp~ZSe FI ou , M, S. Thesis
The University of Tuisa (1968).
32 Mes*uiam, S, A, Q,: ~ o~
~=ELf@lQ~
~*
M*S. Thesi8, The University of Tuisa (1970),
33 Camaeho, C, A,: @mg6111~
~&L&fit&
~ M.S* Th@~is, The
University of Tulsa (1970),
34 Duns, H,, Jr, and Ros, N, C, J,: ‘ Vertiaal
FIGW of Gas and Liquid Mixtures in Welis, ”
~Worid pet, Congr es% 451,
(1063),
35 Briii, J. P,: “Dieoontinuitieo in the
Q’kiczewski Oorreiat ion for Predicting
180
Pressure Gradients in Wells-, ” ASME JERT,
111, 34 . 36, (March, 1989).
36 Beggs, H. D, and Briil, J. P.: ‘A Study of
Two- Phase Fiow ir~ lnolined Pipes, ” Jilts
~., 607.617, (May, 1973),
37paimer , C, M,: “ Evacuation of inc!!ned Pipe
Two- Ph#jse Liquid Hoidup Correlations Using
Experimental Data, ” M, S, Thesis, The’
University of Tuisa (1975).
38 Mukherjee, H. and Brill, J. P.: ‘Pressure
Drop Correlatior?s for inclined Two- Phase
Flow, ” Trans. ASM5 JERT (Dee., 1985).
3gAziz, Y., Govier, G. W, and Fogar asi, M.:
“Pressure Drop in Welis Produoing Oil and
@AS,” ~= 48, (JuiY .
September, 1972),
fWMENCiATURE
lWGr.@h L
a
A
b
c
c
c’
d
D
e
El
132
B3
E4
Es
E6
L
8
h
If
L
n
n’
N
P
Q
Re
RPF
s
coefficient defined in Bq. 46
cross-sectional area of pipe, mz
coefficient defined in Hq. 47
coefficient defined in Eq. 48
constan: factor reldtg friction factor to Reynolds
number for smooth pipm
coefficient defined in Eq. 3$
differential change in a variable
pipe diameter, m
error function
avarago percentage error, %
absolute average porcontage error, %
standard deviation, %
averago error, psi
absoluto average error, psi
standard deviation, psi
friction factor
fraction of liquid entrained in gas coro
grswity aoceleratlon, m/s2
local holdup fractton
averago holdup fraction
longti~ along the pipe, m
exponent relating friction factor to Reynolds
numbu for smooth pipm
expentmt to account for the swarm effect on bubble
riso volooity
number of well cases successfully traversed
pressure, psi [ N/m2 1
flow rate, m9/s
Reynolds number
Rolat{vo Porfortnmtao Factor, defined in Iiq. 92
wetted porimotor, m
11. v velocity, mls
v volume, m’
x Lockhart and Martinelli parameter
Y Lockhart and Martinelli parameter
z empirical factor dcfinitig interfaclal friction
Icmgth ratio, defined in I@ 27
film thickness, m
ratio of fihn thickness to diwnetcr
dlfferenoe
aiwolute pipe roughness, m
dimensionless groups, defined in Eqs, 79 and f?f)
no-slip holdup fraction
dynamic viscosity, kg/m+i
kinematic viscosity, m2/s
angle from hortizontnl, rad or deg
density, kg/m3
surface tcttsion, dyntdcrn
shear stress, N/m9
.“yw%m.ii
acceleration
A avorago
c Taylor bubble cap, com
crit critical
9 elevation
f friction
P film
o ga8
H hydrauIie
i ith element
I interfacing
L liquid
LS liquid slug
M mixture
mn min{mum
N Nussolt
r relative
s slip
S sttporfioial
w slug unit
t total
m Taylor bubble
Tp two.phase
* dtwelopin~ slug flow
14. !
0000
0000
0:.:0:
Q:?
33.%7~o
00
t
}
SLUG
FLOW
t
Do
o
0
t
t
~
..$.
. . . .
. . .
$.’.
. .,,
,..
0,
.$
.*
‘.
.*”
t
C1-llol;A;lW&AR
Fig. l-Flow patterns in upward two.phase flow.
201 I I I I [ I
i
(o) DEVELOPED SLUG UNIT
!2Q
3
z 0.1
A
a
6
ii
K
u.!
o. 0.0’
a
u)
0.00i
BUBBL’T / BARNEA
TRANSITION
I
I
/
I[ANNULAR
D
I
A SLUGOR CHURN
I
I
I
1
I
I
II
i
1“ I I I I
SUPERFICIAL GAS VELOCITY (m/S)
FIu. 2-Typlcel flow pattern map for wellborss.
q
t.k
,w
t: ‘
u ,
.n
{?=
I II I
02 0.1 1 10 100
~
,aso~
NT
4L
r ‘GTB
LyB
‘GTB 1
V~TB
DEVELOPING
J TAYLOR
BUBBLE -
-1.-0
‘v QL O?do
(b) DEVELOPINGSLUGUNIT
Fig, 3-Sohemetlo diagram of slug flow,
164
15. I ,’
“1
GAS CORE
,, . .
LIQUID FILM ~ _
. ,,
,,
ENTRAINED
.,
LIQUID DROPLET
~
1
,, . . IC . ‘
1:
I ~F
;::::,
F19.4-Sc,hemellc diagram o! annular flow, ~
,,
!.
,,
i, ,.
10‘ .
I‘?2(
+ CALCULATED PRESSURE
T
t
‘
9.0
ANNhLAFl
x MEASUREDPRJNWRE
J.
S1
:,:
,4
h
,,
,:
I
i
,
,,,
,., PRESSURE ( PSI ) :
1
Fig. 5.-Performanoe of tho co~praltan$lve model-typloal prenaure profile,
1,
,,, ,,.
I
I
:.
,
I
16s
,,,