Minutes of
the Meeting on 1 May 2001
Present:
Keith Austin (Flowmaster), Arris Tijsseling (Eindhoven
University), Bruno Brunone (Perugia University), Mohamed Ghidaoui
(Hong Kong), Zhao Ming (Hong Kong), Della Leslie, Alan Vardy, Jim
Brown and (Dundee University).
Chairman:
Alan Vardy
Minutes:
Della Leslie
Meeting commenced at 09:30 hours.
Chairman’s
Introduction:
Welcome to all. Alan summarised the connection between the two theories
on unsteady friction. Today should give an overview of the methods
and show that progress has been made since the last meeting. Alan
distributed a revised agenda.
Item 1.
Improved unsteady friction formulae,
part I
Jim Brown presented some of his and Alan’s current work on improving
unsteady friction formulae. He began by giving a brief history: aim
to better understand problem and to convert to rough from smooth
pipe. Work on rough pipe not covered today, but are very close to a
completed solution.
General interpretation of unsteady friction:
Fast transients in flow occur, e.g. valve closure or in tunnels during
the passage of pressure waves. To predict friction requires the
numerical analysis of equation, but in real systems this is not
possible because of prohibitive computation cost (e.g. 60hr/case),
therefore assume axi-symmetric (1-D) to reduce cost.
1-D unsteady flow: Incompressibility is assumed and Jim presented a
general form of the equations of motion. This general form covers
both plane and axi-symmetric coordinates. It is assumed turbulence
properties don’t have time to change and viscosity is a function
of position. A Laplace transform is used on the equations and
initial velocity is assumed to be zero. The result provides the
transformed wall shear stress, from which the steady-state condition
is found by letting the parameter s (from Laplace) tend to zero.
Subtracting this from the original expression provides the unsteady
component of the (transformed) shear stress. To find the actual
shear stress we need to perform an inverse Laplace transform, and
Jim said that this is not always possible to calculate. Next Jim
describes a new development of a pressure gradient based weighting
function, whereas usually acceleration has been used. He explains
how this weighting function can be derived from the preceding
analysis – providing a transformed weighting function. Jim shows
how this new weighting function can be related to the conventional
weighting function, illustrating both have a very similar form.
Then, instead of trying to directly invert the functions, an
approximation for each weighting function is defined with known
inverses. He illustrates that the approximation is very accurate
when compare to the actual function, and provides a relatively
simple final formulation. He noted that the weighting functions
rapidly decrease with time. By defining the time for it to reach 95%
of its final value, if the time step is larger than this then the
weighting function has very little effect on the solution. Jim
illustrates the method uses the Zielke case – it clearly
demonstrates the effectiveness of the method.
Item 2.
2-D Turbulence Models: Use steady-state based
Mohamed Ghidaoui first gave the group three current/new papers he had
written (Della will photocopy and distribute to the group with the
minutes). His presentation took the form of two parts, the second
part later in the day – item 4. The first part examined the use of
steady state based 2-D turbulence models. It is assumed the general
problem: non-slip condition at wall, fast transient, short time
scale. He then examined a number of different steady-state based
turbulence models for waterhammer, to test for sensitivity of
results to eddy viscosity distribution. He illustrated the various
viscosity profiles the models used and compare results. It showed
there was very little sensitivity to data near the centre of the
pipe; saying was probably because dominant behaviour is near pipe
wall. Mohamed concluded that there is a lack of sensitivity and thus
justifies the simplified distribution of Vardy and Brown 1995 and
explains why Vardy and Brown model as accurate as 2-D models (high
numerical resolution of centre not is needed).
Mohamed continued, saying that behaviour was dependent on time-scales:
time scale of transient and time scale of diffusion. If transient
scale is greater than diffusion, then turbulence frozen (everything
localised near the wall). Mohamed proposes a dimensionless
parameter, P, to decide when turbulence is frozen, i.e. time scales
different enough. He than demonstrates the use of the parameter by
giving a figure illustrating the error between experiments and
various models. This showed the best models are associated with the
highest P.
Bruno promised to send actual experimental data (Mohamed had been trying
to extract information from figures in published work).
Item 3.
Large Initial Reynolds number Transients
Bruno Brunone
gave an interesting presentation on some of his resent research
development. First he showed some figures, based on 2-D numerical
model, giving values of the parameter k vs. Reynolds number,
for each y0 (Alan and Jim pointed out that the
definition of y0 could be expressed as the
friction(2fL/D)*Mach number). Figures had a similar
form to the Moody diagram. He said that available experimental data
used only limited Re values, so was unable to compare.
Next he described
the current problem he had been working on – he had been
approached by a water supply Company who had problems with a rising
main. They had problems with pipe movement (pipe passes through
basement of a building).
Bruno had
obtained experimental field data associated with the problem.
Transient tests due to pump shutdown had Reynolds number of: 240568,
269476 and 390005 (three tests), much higher than in many past paper
(e.g. Budny has about 11000). The experimental results gave data
similar to lab test, showing decay and rounding of peaks. In the
third experimental test, there was water-column separation, which
Bruno said was due to a new pump with low inertia.
The next stage
was the numerical modelling of the field tests. Bruno presented the
approach he used to model the system – based on the unsteady
friction model using Ju = k3/g(dv/dt-a*dV/ds).
He gave the resulting MOC equations, including the parameter k3
(appears in only one equation). The equations are different along
the each characteristic, C+, C-. Alan said that direction of flow is
important with respect to axes. Alan suggested, you need to refer to
positive and negative velocity, i.e. choose axis in direction of
positive velocity and therefore can stay with non-symmetric
equations. Bruno then presented a symmetric version of the equation,
which includes sgn(V) term - this forces k term to
appear alternatively in the each characteristic. The parameter k3
is unknown for large Reynolds numbers, and the values from Vardy and
Brown smooth pipe data are assumed. Despite the problem having rough
pipes and larger Re, the results found appeared reasonable –
showed decay and rounding. A discussion on the differences
developed. Alan pointed out which regions of the plots were
important with respect to unsteady friction, showing there were in
fact significant differences.
Item 4
2-D Turbulence
Models: Assume Symmetric flow
Mohamed Ghidaoui presented the second part of his presentation on 2-D
turbulence models. This was examining the assumption of symmetric
flow. First he showed experimental results from a paper: this
described a ramp type experiment (acceleration, maintain and
decelerate the fluid). Results showed the unsteady velocity
profiles. The first picture showed oscillation near walls (laminar
flow). The second included vortices in the flow– these were not
symmetric and showed a phase lag (helical type). It showed these
vortices growing and interacting, illustrating a change of flow from
laminar to turbulent; the instability started near inflexion points.
The last example again illustrated the vortices, still with a phase
lag, but this time there was no interaction. Mohamed refer to
experimental results by Bruno, giving non-symmetric velocity
profiles, and said that this was consistent with helical form. The
axi-symmetric modes are very unstable.
Next Mohamed described stability mechanisms in the system: If there is
more input than output then there is a need for the flow to change,
i.e. stability governed by production and dissipation of energy. He
showed that production of energy is greatest at the inflexion point
and depends on the strength of the transient. He presented some
stability diagrams and showed that experimental results agreed with
the diagram (only limited data available) and most work did in fact
fall in the stable region (hence symmetric). Mohamed concluded the
presentation, saying that experimental evidence showed flow
instability; and the existence of flow instability & impact on
energy dissipation has not been recognised in the past.
Item 5
Improved
unsteady friction formulae, part
II
Jim Brown gave the second part of his
presentation on an improved unsteady friction formula. He outlined
some of the most recent work, which uses an annulus formulation for
viscosity. In the outer region (annulus), Cartesian (plane flow)
coordinate system in used, whilst the inner core uses polar
coordinates (axi-symmetric). The equations presented in the first
part of the presentation (Item 1) allows for both systems. In the
annulus, viscosity is assumed to be linear (with position) and in
the inner core is assumed constant - this can be any value be will
examine the case where it matches the outer value of annulus. The
boundary conditions assume non-slip conditions at the wall, and
velocity is continuous between annulus and the core. The velocity is
prescribed at the interface and there in equality between velocity
gradients of the core and annulus at the interface. In the 1995
paper, a uniform velocity was assumed in the core region and this is
the main change in the current work.
Using the method described in item 1, Jim
shows that the solution for the problem may be found – giving a
pressure gradient based weighting function. He compared the new
solution with that from the 1995 paper. Using a log scale there
appeared to be little difference, but with a linear scale there was
a clear change. The current work increased the time-life of unsteady
friction. It introduces changes in the later stages of models, which
was where there previously had been problems, and introduced more
wall shear stress.
Item 6
Turbulence model in quasi-2D simulations of pipe flows
Zhao Ming gave an interesting presentation
that compared turbulence models in quasi-steady 2D simulations of
pipe flows. First he outlined the difference between quasi-steady
and frozen turbulence model. Quasi-steady: instantaneous turbulence
for unsteady flow assumed same as steady flow, steady turbulence and
slow transient with very short time. Frozen turbulence: turbulence
assumed frozen and initial steady eddy viscosity. There was a
discussion on the different approaches. Alan said that in his work,
computer simulation use local Reynolds number, so that it was
similar to quasi steady but freezing each time step.
Zhao proposed a new approach for the
quasi-steady model, which he called the decomposition model. In this
he divided the velocity into two parts: initial steady velocity +
‘unsteady’ part. Alan said that it would be better if the
‘unsteady’ was given an alternative name, because it is not used
in the same context as other work. By removing the initial steady
profile from the analysis the remaining component tends towards a
log profile (with time) and has no inflexion points – this fitted
better with assumptions made for the quasi-steady model. Zhao showed
comparisons between the models and with experimental. The
decomposition model matched the peaks (produced more damping than
other models) in experimental data very well.
Alan asked what are the benefits of the model,
and whether there could be problem in the limits (subtracting two
large numbers – both steady and final ‘unsteady’ components
are non-zero)? A general discussion developed on the model.
Other business:
Next meeting?
It was proposed that the next meeting should occur in about a
year’s time – should contact participants near the time.
Item 7.
Chairman’s Closure
Thanks to all participants
Closure
of meeting at 16:50 hours.
Quote
of the day:
Engineers observe what they can’t solve; Mathematicians solve what
they can’t observe.
|