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Kevin,
I just did a hand calculation and confirmed it is because formula 4.115 that
cause
twice of the heat loss into the wall.
My duct have a dimension of 1800m long x 4m wide x 3m high, which give a
hydraulic
diameter of 3.4m. If I take into account of the difference of the coefficient
in
front of the Re, which should be 0.023, not 0.037, then I can easily reduce
heat
transfer coefficient to the wall by 50% approximately.
0.023/0.037 x (3.4**0.8/3.4)=1/2.05
This is why I recorded twice of the temperature drop using FDS when compared to
the
empirical model (http://en.wikipedia.org/wiki/Heat_transfer_coefficient, as
well as
Incropera & Dewitt, Introduction to Heat Transfer, 3rd Edition, Eq 8-60).
I am sure the heat transfer into the solid wall will be very close to the
results
from the empirical model. Of course this is for the longitudinal flow along a
duct.
If you are reluctant to change this for FDS which is designed not only for the
longitudinal tunnel/long duct, then I proposed release another version of FDS
specially for this? this is my opinion.
Jason
Original comment by yunlo...@gmail.com
on 20 Feb 2009 at 3:11
(1) How is FDS going to know what the characteristic length of a flow geometry
is?
It can't possibly know that. The correlation is of the form Re_L^0.8 / L, so
it is
not strongly dependent on L.
(2) correlation in FDS is for heat transfer to a flat plate (and for the
typical user
that is the appropriate correlation) not heat transfer to a duct.
Original comment by drjfloyd
on 20 Feb 2009 at 3:12
drjfloyd,
(1) the characteristic length of a flow geometry is based on the hydraulic
diameter,
which is: 4x cross-Section-Area/Perimeter. This is no technical difficulties to
do
this.
(2) Most fo the heat transfer text book recommended this:
Nu=0.023xRe^0.8xPr^0.3
Why FDS use: Nu=0.037xRe^0.8xPr^0.3?
I can not understand, and no reference is given in the users guide.
At least another special version of FDS should be released specially for the
longitudinal flow and heat transfer cases.
Jason
Original comment by yunlo...@gmail.com
on 20 Feb 2009 at 5:12
drjfloyd & Kevin,
I also deteced this over-predict of heat loss through the wall when I was
comparing
with a experiment. FDS modelling get a lower temperature when compared to the
experiment in a smoke door leakage test at Warrington. I believe this is
extactly
the reason.
Would you please let me know in which subroutine this fluid-solid heat transfer
is
implemented? as I am very keen to valid this if I can compile the code myself.
Do I need both the FORTRAN and C compiler to compile to a Win-Xp executable
file?
Thanks.
Jason
Original comment by yunlo...@gmail.com
on 20 Feb 2009 at 5:22
No technical difficulties? OK write an algorithm that can examine every
possible
geometry that a user can input and in the context of the flow field and
temperature
gradient pick the appropriate length scale and form of the heat transfer
correlation.
FDS doesn't know that you have input a duct. It only knows that there is a set of
blockages. It is very easy for us as people to look at a geometry and say "OH,
thats
a duct with a diameter of x, I need to use a duct heat transfer correlation" but
getting a computer to do that is not a trivial matter.
We will add a reference to the guide. Wall heat transfer is done in wall.f90.
Compilation instructions can be found on the Wiki page (tab at the top of the
issue
tracker).
Not familiar with that dataset, but what is the total uncertainty in the wall
temperature? This would include uncertainties in HRR, wall properties, leakage,
compartment dimensions, the correlation for h used in FDS, etc. Unless you
prediction is in error by more than the total uncertainty you can't conclude the
model is in error.
Original comment by drjfloyd
on 20 Feb 2009 at 12:49
All -- seems like this discussion has spread across multiple threads. In any
case, I
think everybody has a point, and this discussion is worth having. Jason (not
Floyd) -
- you're working on one particular application. We have to work on everybody's
application and it's hard to configure FDS for every possible geometry. The
trouble
with most mass and heat transfer correlations is that they are geometry
specific,
especially in regards to a characteristic length scale. Usually, we just set
that
length to 1 m for lack of anything better. I think the solution to this problem
is
to make it clearer in the User's Guide how one might change the coefficients of
the
correlations if that is indeed the only issue. Changing the mathematical form
may be
another issue entirely and we'll have to approach on a case by case.
Keep in mind that we do not have strong opinions about the exact form of any
particular correlation. Our selection of one over another usually comes down to
how
much information the correlation requires from the resolvable flow field.
Original comment by mcgra...@gmail.com
on 20 Feb 2009 at 1:32
drjfloyd:
I can adjust the C_forced to account for the coefficient of 0.023 and the
length
scale. Thanks
Kevin,
There is no need to change the form of the formula, only make the length scale
possible to input is OK, as C_forced input is aready there. Thanks for the
solution.
Jason
Original comment by yunlo...@gmail.com
on 20 Feb 2009 at 7:46
Original issue reported on code.google.com by
yunlo...@gmail.com
on 20 Feb 2009 at 12:45