prog pros
TRANSCRIPT
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m p u t a t i o n a l H e a t T
r a n s f e r
a n d F
l u i d F l o w
Oct 17-21, 2007
Xian, China
CFD: Progress and
Prospects
by
Brian Spalding,
of CHAM, Ltd
A lecture at the
Asian Symposium ASCHT-2007
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,
C o
m p u t a t i o n a l H e a t T
r a n s f e r
a n d F
l u i d F l o w
Oct 17-21, 2007
Xian, China
1. Introduction
1.1 Purpose
Computational fluid dynamics started half a century ago. In this
lecture, I review its progress and seek to indicate how it may
profitably develop further.
I direct my words to research
workers seeking problems which it
is possible and beneficial to solve.
I address also engineers,
especially those working in
process industries, whose
designs can be improved if the
indicated developments are carried
out.
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Oct 17-21, 2007
Xian, China1.2 Patterns of analysis
The problems facing applied science are multi-dimensional; and
they can be approached in various ways.
The main dimensions of variation are in:
• time,• space, and
• population (to be explained below).
Variations in time are easiest to handle,
because we all grow older at the same
rate: one day per day.
Variations in space are more complex,
but easy to understand; for some of us
can run faster than others.
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Populations which are relevant to CFD include those of:
• liquid droplets with differing diameters;
• solid particles with differing velocities;
• gas ‘fragments’ with differing compositions, or temperatures; and
• radiation fluxes with differing directions.
1.2 Patterns of analysis
Variations in population?
Here is a one-dimensional histogram
representing the distribution of the
age of persons for a particular
community at a particular time;
and here is a picture to show that
histograms can be two-dimensional.
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Oct 17-21, 2007
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and I shall argue that, in respect of calculation, the methods which
are used for spatial variations can be applied to population
variations also.
1.2 Patterns of analysis
I shall further distinguish the three main approaches to non-
uniformity, whether in time, space or population dimensions,
namely:
• neglect,
• presume,
which means in effect, guess, and
• calculate;
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I shall not argue that 'neglect' is always bad, or that 'calculate' is
always best.
Indeed, most successful approaches are hybrid; thus:
• even the most extreme of the calculators neglect something; and• nearly all presume rather than calculate some non-uniformities.
What is necessary is to make wise decisions about
• what to neglect,
• what to presume,
• what to calculate, and
• when to do each.
1.2 Patterns of analysis
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Oct 17-21, 2007
Xian, China1.3 The structure of
the lecture
In part 2, I shall explain my 3-dimension ~ 3-
approach classification; and I shall illustrate it by
way of examples from science and engineering.
In part 3, I shall recommend that CFD specialistsshould provide:
• heat-exchanger designers with software based
on less presumption and more calculation;
• chemical-reactor operators with prediction toolswhich calculate the distribution of fluid fragments
in composition space; and
• mechanical engineers with computer codes
which calculate the flow of fluids and the stressesin solids simultaneously.
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2. Examples of engineering analysis
2.1 Piston engines; space-direction
variations
The steam engine
For this example, the 'neglect' approach is quite
satisfactory, because the variations of steam temperature
and pressure with position in the space above the piston
are small at any instant of time.
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2. Examples of engineering analysis
2.1 Piston engines; space-direction
variations
Internal-combustion engines
The 'presume' approach is best,
especially when flame speed or spray
burning rates are based on experimental
observations.
The 'calculate' approach, i.e. conventional CFD, is often
employed; with limited success. Why? Because
it neglects 'population' aspects of:
(1) turbulent combustion and (2) droplet vaporisation.
Here the 'neglect' approach is not
satisfactory,because flames spread
slowly.
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The plane turbulent mixing layer; non-uniformity in space
2. Examples of engineering analysis
2.2 Simpler turbulent flows
I start with the simplest of
all turbulent flows; the
plane mixing layer.
The task is to predict the angle of the wedge-shaped layer of
turbulent fluid at the edge of a jet injected into fluid at rest.
.
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Xian, ChinaShape functions and weighting functions
The presumed-profile approach involves:
• Guess the shapes of the velocity and effective-viscosity
profies, e.g. as sloping or horizontal straight lines
• Multiply the differential equations by weighting functions.
• Integrate across the layer analytically.
• Deduce the angle by algebra.
Advantage: quick and easy.
Disadvantage: accuracy is uncertain.
The 'neglect' approach is not applicable here; for non-
uniformity is of the essence.
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Oct 17-21, 2007
Xian, ChinaThe plane turbulent mixing layer;
the Finite-Volume Method
The ‘calculate’ approach
(version of Patankar and myself, 1967):
This is now known as the 'finite-volume' method' (FVM),the
general form of its equations being:
value in the volume = sum for all faces of coefficient * value in
neighbou r volume + sum of additional sources
wherein the coefficients express diffusion and convection.
• presumes only that the velocity profile is ahistogram, with unknown column heights;
• uses weighting functions of 1, i.e. none at all;
• integrates across each histogram interval;
• deduces the unknowns numerically.
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Other steady-state turbulent jets,
wakes, plumes and boundary layers
The FVM was soon applied to these flows
which:
• had already been extensively studied
experimentally, and by presumed-profile
methods;
• are 'parabolic' (i.e. downstream events
do not influence upstream ones);
• therefore permitted solution by 'marching'methods' on memory-scarce computers;
• allowed turbulence models to be tested;
• gave us confidence to extend the FVM to
recirculating, three-dimensional,
unsteady, compressible and chemically-reactin flows
The early days of CFD; a condensed history
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Oct 17-21, 2007
Xian, China2.3 Steady flow around solid bodies
immersed in fluid streams
• aircraft design was based mainly
on a 'neglect' approach, in that thevariations of stagnation pressurewere neglected. The aerodynamic forces on the aircraft were
then computed by way of ideal-fluid theory.
• The effects of viscosity, and indeed turbulence were expressed by
the supposition that the 'displacement thickness' of thin boundarylayers enveloping wings and fuselage made these, in effect, rather
thicker than they truly were.
• The presumption approach was used, however, to calculate
the displacement-thickness distribution; so the whole method can be
characterised as being 'hybrid'.
Streamlined objects
Before CFD,
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Xian, ChinaCurrent practice
Now that CFD exists,
• the calculation' approach is adopted for the whole of the
space occupied by the fluid; which allows also the small
regions of 'separated flow’ to be simulated.
• However, an accurate calculation of the frictional
forces on the solid surface can be made only by the use
a very fine grid in the boundary layer;
• so, for economy, some element of profile-
presumption is retained, by way of wall functions.
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Oct 17-21, 2007
Xian, ChinaFlows around and inside buildings
• Before CFD, flow prediction was
based on experiments with small
geometrically similar physical
models;
• but this was unreliable , because
the similarity criteria of Reynolds
(viscosity) and Froude (buoyancy)
could not both be satisfied.
• Neither the neglect nor presume approaches had
anything to offer. Therefore, engineers concerned with
heating, ventilating, air-conditioning and fire-
protection of buildings were among the first to turn to
CFD.
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Oct 17-21, 2007
Xian, ChinaFlows around and inside buildings
• CFD has satisfied their requirements; and
• it is for widely used for simulating fires in car-parks and other
buildings;
• BUT, for phenomena such as the fire-ball, it needs to takeaccount of variations in hot-gas-population space.
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Heat exchangers; non-uniformities in space
2.4 Chemical-engineering equipment
No designer can 'neglect' the
temperature variations in heat
exchangers.
Instead, most guess them as
being similar to that calculated for
idealised counter-flow systems.
Since they know that the flow
patterns must differ, they multiplytheir calculated heat-transfer rates
by correction factors like those
on the right.
But these are still guesses, nonethe less.
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Heat exchangers; non-uniformities in
space (end)
These presumption practices derive from the pre-CFD age.
However, it was shown more than thirty years ago (by
Patankar and myself, as it happens), that the calculateapproach is practicable and indeed easy.
It is strange therefore that most heat exchangers
today are still based on presumption rather than
calculation.
Therefore, in section 3.1, below, I shall be
recommending a change of practice.
Sti d h i l t h i
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Stirred chemical reactors, showing
variations in both space and
population
The process:
Many chemicals products are
created by pumping feedstock
materials (A and B) into a reactor
vessel, where they are stirredtogether by a paddle, in order to
react chemically.
The task is to predict how the rate of production of C from reactants A and B
depends upon the power consumed by
stirring and the rate when mixed in a test-
tube, where: rate/(con cA *con cB ) = k_tube .
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Oct 17-21, 2007
Xian, ChinaStirred chemical reactors
Variations of time-averaged concentration
Before CFD,
the 'neglect' approach had to be used for variations
with position; and it was not bad; for, if the stirring is
vigorous enough, the time-average values of concA and
concB will indeed be almost uniform.
But what about moderate stirring?
The 'presume' approach is not usable in this case; for no
guidance exists as to what profiles should be presumed.
Nowadays, CFD is employed; but it is not enough;
for, if R_ave / (co ncA_ave * concB_ave)= k_reactor ,
it is found experimentally is that
k_reactor is much less than k_tube . Why is this?
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Xian, ChinaStirred chemical reactors
Variations in population space
The answer: non-uniformity in population
space, also called unmixedness, shown here ->
At any point in the reactor, fluid fragments of
many different concentrations can be found.
To calculate their time-average values, one must
know for what proportion of time each is
present.
That means that one needs a probability-
density function, like this --->
Can one calculate it? Yes, as I shall explain later;
and for each location and stirring rate too.
From it can be deduced the C- production rate.
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Xian, China2.5 Simpler non-uniformities in
population: droplet-size
Vaporization of fuel sprays (in Diesels
or gas turbines) consisting of droplets of
various diameters, D, which change size
at a rate governed by :
- dD/dT = const * (1/D) * ln(1+B)where B, the driving force for mass
transfer, depends upon (e.g.) local
temperatures and other gas properties.
This shows that droplets diminish in size
at different rates, the smaller onesdisappearing the more rapidly.
.
The task is to calculate the overall rate of vaporization.
This necessitates knowing the droplet-size distribution at each
location and each time.
V i ti f d l t i
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Vaporization of a spray; droplet-size
population
The usual three ways are:
1. Neglect variations, i.e. suppose that all the droplets at a
single location in the spray have the same diameter.
2. Presume that the profile isconstant (e. g .) of Rosin-
Rammler form, which cannot
be very accurate.
3. Calculate the ordinates of the
histogram by way of astandard finite-volume
equation, with the source term
dD/dT above.
Use calculate if droplet size is
critical, as in fire extinction.
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Oct 17-21, 2007
Xian, ChinaThe turbulent diffusion flame;
fuel-air-ratio population
Experimentally-observed unmixedness
Hottel, Weddell and Hawthorne drew attention in 1949
to the 'unmixedness' of the gases in a flame
produced by a jet of fuel gas injected into air.
They measured finite time-average concentrations of
both fuel and oxygen at the same location.
That could never be found in a laminar flame.
The first CFD analyses
It was not until 1971 that the first attempt to simulate
this unmixedness numerically was made, on the basis
of a very simple profile presumption.
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Xian, ChinaThe turbulent diffusion flame;
presumed fuel-air-ratio population
The guess was that, at a
point where the time-
average fuel-air ratio was
F, say, the gases
actually present therehad the ratio
F+ g for half the time,
and
F- g for the other half .
Standard CFD calculated F easily.
For g, a new differential equations was invented, having sources
guessed as being proportional to gradients of F- and velocity.
This approach, when appropriate empirical constants were
introduced, allowed turbulent diffusion flames to be simulated.
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
reactedness population
In the turbulent diffusion flame,
fuel and air enter separately, and
must be mixed before chemical
reaction can occur, at a rate
limited by the rate of that mixing.
I now consider a flow in which the fuel and air are mixed before they
enter, at uniform and constant velocity, a plane-walled duct in which
is placed a bluff-body 'flame- holder'.
A turbulent wedge-shaped flame spreads across the duct, as the
sketch indicates; and the profile of longitudinal velocity is roughly as
shown.
What then limits its rate? A different kind of mixing: that betweenburned and unburned gases.
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
the near-constancy of its angle
When first investigated, this flame showed some
puzzling features, namely that the wedge angle
was almost independent of:
• inlet velocity
• fuel-air ratio;• inlet temperature;
• pressure; and
• inlet turbulence intensity.
But why?
H.S. Tsien, while at CalTech, explained theshape of the profile; but what governed
its angle remained a mystery.
We learned only later
• non-uniformity in space depends on
• non-uniformity in population.
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
the first population presumption
The guessed profile
The first idea, embodied in the so-called eddy-break-up model ,
was that the gas population consisted of two components, namely:
The histogram representing the
presumed population thereforeconsisted of two spikes; and
their relative heights dictated
what would be measured as the
time-average temperature.
(1) fragments of wholly un-burned gas which were
too cold to burn; and(2) fragments of hot wholly-burned gas which also
could not burn because either all the fuel or all the
oxygen had been consumed.
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
collision between burned and unburned gas
fragments
These latter, being sufficiently hot and also containing
reactants, could burn; and did so very rapidly, thereby increasing
the height of the right-hand spike. Their actual concentration
was considered, implicitly, to be negligibly small.
The rate of collision per unit volume was guessed as proportional
to the rate of dissipation of turbulence energy.
This explained why the flame angle remained almost unchanged
when the inflow velocity was increased.
These two elements of the population were
thought of as colliding with one another and
thereby producing sub-fragments of
intermediate temperature and composition.
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
the next presumed reactedness profile
The four-fluid model
The EBU, published in 1970, became very popular; so much so that
25 years passed before the obvious next step was taken;:
to increase the number of presumed components from 2 to 4 !
Collisions between fluids
1 and 3 created fluid 2,
2 and 4 created fluid 3,
1 and 4 created fluid 2
and also fluid 3.
Reaction of fluid 3
created fluid 4
at a chemistry-
controlled rate.Fluids: 1 2 3 4
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Oct 17-21, 2007
Xian, ChinaConfined pre-mixed flame;
applications of the four-fluid model
The chemistry-controlled step (fluid 3 creates fluid 4) explained:
why:
1. the flame angle remained nearly constant, and
2. the flame could be suddenly extinguished by a velocity increase.
The four-fluid model wasused successfully for
simulating flame spread in a
baffled duct and for oil-
platform explosion
simulation.It has been little used; but it
was the first step towards
calculating the reactedness
population,
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In conventional CFD, we
divide space and time into as
many intervals as we need.
Why not do the same for the
reactedness at each point?
The height of each column can
then be deduced from a
From four fluids to many:
the multi-fluid model
Finite-Interval equation’ like this:
height of interval= sum for all faces of coefficient *
height of neighbour interval +
sum of additional sources +
sum for al l other intervals of coeff ic ient *
height o f other interval )
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Oct 17-21, 2007
Xian, ChinaWhat the terms in the finite-interval
equation represent
In: height of interval= sum for all faces of coeff ic ient *
height of neighbou r interval +
the coefficients express rates of convection and diffusion, as in
the the finite-volume equations of conventional CFD.
But in: sum for all other intervals of coeff ic ient *
height of other interval
the coefficients express the physical and chemical processes:
• collision between members of the fluid population, and
• chemical conversion of one member into another.
The finite-interval method is thus merely a natural extension of
the finite-volume method; and its equations can be solved in the
familiar successive-substitution manner.
The calculation of population distributions is easy.
O t 17 21 2007
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Oct 17-21, 2007
Xian, ChinaHow material is distributed after
collision
Here is a diagram from one
of the earliest publications.
It depicts one of the possible
hypotheses, called
'Promiscuous Mendelian'.
The 'colliders' are treated as 'mother' and 'father’; and the word
'promiscous' implies that any two members of the population may
collide.
The word Mendelian, a reference to Gregor
Mendel, the Austrian "father of modern
genetics", implies that the offspring may
appear with equal probability in any
interval between those of the parents.
O t 17 21 2007
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Oct 17-21, 2007
Xian, ChinaA calculated probability-density
function
This hypothesis has been embodied in
the PHOENICS computer code.
Here is one reactedness histogram,
computed with its aid.
As in the the eddy-break-up guess, thereare indeed spikes at zero and unity
reactedness;
but calculation has shown that the
intervals in-between are alsopopulated.
Such probability distributions can to be computed for
each location in the flame. Then the desired reaction
rate for the whole flame can be deduced.
O t 17 21 2007
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Oct 17-21, 2007
Xian, ChinaApplication to gas-turbine
combustion
A three-dimensional gaseous-fuel combustor
I show here one sector of a simple combustor
proposed by Professor Wu Chung-Hua in the
early days of PHOENICS.
O t 17 21 2007
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Oct 17-21, 2007
Xian, ChinaSmoke formation rate is influenced
by turbulent fluctutions
Much later, I used this combustor to
show how one must not neglect
fluctuations of fuel-air ratio when
predicting smoke formation.
The differences, although
small. are significant when
CFD is being used to optimise
the design.
I used a 10-fluid model,
with fuel-air-ratio as the
population-defining
attribute. Each cell had
its own computed
histogram
O t 17 21 2007
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Oct 17-21, 2007
Xian, ChinaConcluding remarks for Part 2
It has been shown that:
1. variations in population space should not be neglected
especially when chemical reaction is involved;
2. they can be presumed;3. but it is better to calculate them.
Why are not crowds of
researchers pouring intothis scarce-explored
territory?
Perhaps because they are
waiting for less-timid
crowds to do so first.
Oct 17 21 20073 Recommendations
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Oct 17-21, 2007
Xian, China3. Recommendations
3.1 To heat-exchanger designers
Current practice
I have already mentioned that heat exchangers are stilldesigned in the basis of presumption.
A shell-and-tube heat
exchanger looking like
this (tubes not shown)can be expected to have
a rather complex flow in
the shell.
So far, I have been discussing general ideas. Now I wish to make
three specific recommendations.
Oct 17 21 2007
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But why presume when one
can calculate, as was shownto be possible by the 35-year-
old publication in which this
image appeared?
or
Yet the software used by designers presumes that the flow in the
shell can be conceptualized thus, and described by very few
parameters.
Oct 17 21 20073 1 T h t h d i
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Oct 17-21, 2007
Xian, China3.1 To heat exchanger designers
The solution
The solution is:
1. do not attempt to calculate the flow pattern
between the tubes in detail, because current
computers are not large or fast enough to
handle the necessary fine grids except for afew tubes at a time.
2. Instead, use the space-averaged approach, with empirically-
based formulae for:
heat-transfer coefficients per unit volume, and
friction factors per unit volume,
as functions of local Reynolds and Prandtl numbers.
3. Then solve the finite-volume equations for (space-averaged)
velocity, pressure, temperature for the shell- and tube-side fluids,
treating both as interpenetrating continua, as is easily possible.
Oct 17 21 20073 1 To heat exchanger designers
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3.1 To heat exchanger designers
The solution (contd)
I now show some (not new) results for (the central plane of
symmetry of) a particular shell-and-tube heat exchanger.
(a) The shell-side velocity
vectors, when calculated,
appear thus
(b) The consequential shell-side temperatures, are not, as
presumed, a succession of vertical stripes; although the calculated
tube-side temperatures are (very nearly).
Oct 17 21 20073 1 To heat exchanger designers
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3.1 To heat exchanger designers
The solution (end)
(c) The conventional heat-exchanger-design packages presume
that the shell-side, tube-side and overall heat-transfer coefficients
are uniform throughout; but calculation reveals that they are not,
as the next pictures clearly demonstrate.
Corresponding non-uniformities are exhibited by the calculated
Reynolds- and Prandtl-number values, and the temperature-
dependent fluid properties, from which the heat-transfer coefficients have been computed.
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Oct 17-21 20073 2 To stirred reactor designers and
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But what about the mixture-ratio population grid?
Two distinct cases were considered, namely that:
1. the materials from the entering streams of reactants A and B
were fully mixed at each point in the reactor, which would
correspond to presuming • that its pdf was the single spike shown on the following
diagram, and that
• the amount of product C was as indicated by its horizontal
location;
2. alternatively, at each point there
could be found varying amounts
of 'fluids' (in the multi-fluid sense)
having one of eleven distinct
mixture ratios, so that its pdf
could be that of the histogram
3.2 To stirred-reactor designers and
operators (contd)
Oct 17-21 20073 2 To stirred reactor designers and
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Oct 17 21, 2007
Xian, China3.2 To stirred-reactor designers and
operators (contd)
Case 1 is the conventional-CFD approach which presumes the
state of the mixture-ratio population; and Case 2 represents what is
done by those who recognise that non-uniformities in population
space can be calculated.
The results of the twoapproaches are different. This
is demonstrated by the
following two contour
diagrams showing the product
(i.e. C) concentrations after 10revolutions.
The general patterns are not very dissimilar; but their scales are:
3.2 for the presumption approach and only
2.4 for the calculation approach, at this moment of time.
Oct 17-21 20073 2 To stirred-reactor designers and
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Oct 17 21, 2007
Xian, China3.2 To stirred-reactor designers and
operators (contd)
The explanation for the difference is to be found in the calculated
mixture-ratio histograms, of which a few will be shown,
corresponding to a single instant of time, a single vertical height and
circumferential angle, and at six different radii, starting near the axis
and moving outward.
These pdf histograms show that:
• detailed information about the micro-mixing can indeed be
obtained by calculation;
• the pdfs vary is shape in a manner that it would be impossible to
guess;
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Oct 17-21, 2007Why one method can suffice for
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,
Xian, ChinaWhy one method can suffice for
both classes of problem
The reasons are:
1. The differential equations for velocities in fluids are very
similar to those for displacements in solids, from which the
stresses can be deduced. Thus
[del**2]* u - [d/dx]* [ p*c1 ] + fx*c2 + convection terms= 0
for velocity, and
[del**2]* U + [d/dx]* [ D*C1 - Te*C3 ] + Fx*C2 = 0
for displacement.
2. The solid-stress equations are indeed the simpler , being linear
where the former are non-linear .
3. Since the solid-stress problem is simpler than the fluid-flow one,
computer codes written for the latter can easily serve for the
former also, as many publications have proved.
Oct 17-21, 2007A thermal-stress example
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The block is heated at
various several points so
that its thermal expansion
is non-uniform.
A thermal-stress example
The three examples which I shall show are several years
old; for I wish to emphasise that my message is not a new
one. But it has suffered from neglect.
First, a cooling fluid flows through
a pressurised curved duct ina solid block.
Oct 17-21, 2007Thermal and mechanical fluid-
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The equations for velocity and
displacement and velocity are so similar
that PHOENICS solves both sets at the
same time. Here the solutions are
presented in terms of vectors.
Thermal and mechanical fluid
structure interactions
In my second example, the fluid-
structure interaction is mechanical rather than thermal. A thin partition
bends as a consequence of the
differences of fluid pressure on
its two sides.
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Oct 17-21, 2007Recommendation number 3
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Xian, ChinaRecommendation number 3
My third recommendation is therefore that:
• Researchers should develop and refine the finite-
volume method for simultaneous fluid-flow and solid-stress calculation;
and
• Engineers concerned with fluid-structure interactions
should demand computer codes which embody
those methods.