active sidewalk weather management
TRANSCRIPT
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Active Sidewalk
Weather ManagementHeat Transfer Final Project
Joseph Cooper, Tyler Ludwig, Stephen Wess
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Abstract
We are looking to analyze a system to whichwill prevent snow accumulation on a given
surface. In our system the surface of analysis
consists of a concrete sidewalk withinsulating base structure (CEMATRIXinsulating cement, gravel, and soil). Two
main options to consider are heating thesystem using buried electrical wires or we
may utilize a working fluid that flowsthrough internal pipes. Due to the high cost
of electricity, we elected to analyze a systemconsisting of hydronic fluid and buried
pipes. The goal of our analysis is to find theamount of heat flux needed to operate in
Rochester winter conditions, as well asidentifying the fluid temperature, depth, and
spacing of the pipes.
Problem Statement
During winter, snow accumulation bringsalong hassles as well as danger. Snow and
ice can cause people to slip and hurtthemselves on a number of different levels.
Removal of snow and the melting of icebecomes time consuming, labor intensive,
and also costly due to the need to own ashovel or snow blower, and maintain a stock
of salt to keep the walkway of ice and snowbuildup. The downfall of salt is that it
creates a mess, is harsh on the environment,and becomes ineffective at temperatures
below - 9C.
Our proposed solution to the problem athand is a heated sidewalk comprised of
working fluid flowing through pipes that lay
within the concrete. The working fluid is tobe heated, and pumped through the pipeswith the goal of maintaining a sidewalk
surface temperature above 0C, and runningat steady state with a given snowfall rate.
We will not consider melting a certain depthof accumulated snow as our analysis will
focus on an active system.
System Model
Below is a figure depicting the cross-section
of the system followed by a table of thermalconductivity values used in our analysis.
Assumptions:
Steady State.
Negligible contact resistances in
substrate Constant properties
No heat loss through sides of
sidewalk section (symmetry) Assume known temperature at frost
line (0C). Heat loss through surface includes
convection, radiation, and heat flux
to melt the snow at given rate Non-uniform surface temperature
Working fluid temperature drop isnegligible
Pipe wall temperature = working
fluid temperature
Material ThermalConductivity
(W/mK)
Cement 0.72
Cematrix 0.10
Gravel 2.40
Soil 0.52
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Theory
Before the heat required from our system to
melt snow can be determined, the conditionsfor which the system is designed to
successfully handle must be set forth.
Ideally, the system will be able to effectivelymeet the demands of a severe winter storm
in Rochester. Conditions were chosen basedon a heavy snowfall during the coldest
period of the year. Meteorological datashows that Rochester experiences its coldest
temperatures during January, with anaverage low temperature of -7.5C. The
average wind speed in January is 5.2m/s.The National Weather Service defines a
snowfall rate of 1.3cm/hr as a heavysnowfall rate that garners a winter storm
warning. Our analysis will take place underthese conditions.
The heat flux required by the system
consists of the flux necessary to preventsnowfall accumulation and the flux lost to
surroundings through conduction,convection, and radiation.
The total heat flux is represented by thefollowing expression:
" " " " " "Tot s m h e bq q q q q q= + + + +
The first term, "s
q ,is the heat flux required
raise the temperature of the falling snowfrom -7.5C to 0C, plus the heat flux
required to raise the temperature of themelted snow from 0C to 0.56C (a
generally accepted as the film temperature atwhich the liquid must be before evaporation
occurs).
2 2, ," [ ( ) ( )]
s H O P ice s a P H O f aq S C t t C t t = +
Where tsis the melting temperature of snow,ta is the ambient air temperature, and tf =
0.56C.
S is the snowfall rate in equivalent depth ofwater.
2( )H O
Rate
snow
S s
=
An expression used for determining the
density of snow, given the ambienttemperature is great than -13C is:
Where Ta is the ambient air temperature, andUis the wind velocity. The density of snow
at our defined condition: 114.02 kg/m3. Thisresults in a snowfall rate in equivalent depth
of water (S) = 4.118e-07 m/s. Assuming
constant specific heats (,P ice
C = 2100 J/kgK,
2,P H OC = 4217 J/kgK) and constant density
of water (1000 kg/m3), "s
q =7.46 W/m2.
"m
q is the heat flux required to melt the
snow.
2
"m H O sq Sh=
Where hs is the heat of fusion of snow
(334 kJ/kg). For the conditions specified,"m
q =137.53 W/m2.
"hq is the heat flux lost to surroundings
through convection and radiation. Becausewe are not assuming the surface to be
isothermal due to the spacing of the tubing,we must use a finite difference method to
determine this heat loss. However, if weassume for now that the surface is in fact
isothermal, we can arrive a baseline valuefor this heat flux. This value represents the
heat flux lost if the tubing below the surfaceof the concrete had no spacing (impractical
due to installation cost!) thus causing theentire surface to be at 0.56C. The
convection coefficient calculated in order toevaluate this flux will be used as the
1.15 1.7500{1 0.951exp[ 1.4(278.15 ) 0.008 ]}snow a
T U
=
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convection coefficient in the finite
difference model. The expression for "hq is:
4 4" ( ) ( )h c f a s f aq h t t T T = +
The convection coefficient hc must bedetermined by applying an appropriatecorrelation function. In order to select the
correct correlation function, it is necessaryto first determine the Reynolds number.
L
air
ULRe =
Where Uis the wind speed (5.2m/s),L is the
width of the sidewalk (1.5m), andair
is the
air kinematic viscosity (13.17e-6 m2/s). Thisgives a Reynolds number of 5.92e5(turbulent) with the transition from laminar
to turbulent flow occurring near 1.27macross the sidewalk surface.
Because the airflow over the sidewalk is not
entirely laminar or turbulent, the correlationfunction used will be for a mixed condition.
In our finite difference analysis, we expectto see a varying temperature across the
surface of the sidewalk. However, thecorrelation function we will use to determine
hcis valid for an isothermal plate. In reality,the temperature differences over the surface
will affect the heat flux, but we will assumethat the temperature difference is not
significant enough to invalidate thecorrelation function. The correlation
function used is:
4/5 1/3(0.037 871)L L
Nu Re Pr=
Pris the Prandtl number for air (0.715). Theaverage Nusselt number = 594.35.
air L
c
k Nuh
L=
The conductivity of the surrounding air =0.02385 W/mK. This results in a convection
coefficient of 9.45 W/m2K. This is the value
that will be used in the finite difference
model. The baseline flux due to convectionis simply hc(0.56 - -7.5) = 76.17 W/m
2.
The contribution of radiation to "hq
is
4 4( )s f aT T , where the emissivity of
concrete (s ) = 0.88. The temperature of the
surrounding (Ta) can be assumed equal tothe ambient air temperature while
precipitation is occurring.The baseline heatflux due to radiation = 31.56 W/m
2. With
the radiation and convection losses
combined, "hq = 107.73. We expect the
results from the finite difference model to
exceed this value due to points on thesurface of the sidewalk at temperatures
greater than 0.56C.
The fourth heat flux term contributing to the
total heat flux is "e
q , the heat flux necessary
to evaporate the melted snow. The followingexpression can be used to calculate this flux.
" ( )e air m f a wq h W W h=
In this expression, hw
is the heat of
vaporization for water (2502 kJ/kg). Themass transfer coefficient, hm for the water
evaporating into the air.
2/3
,
cm
air p air
hPrh
Sc c
=
Sc is the Schmidt number, a dimensionlessparameter that depends on the kinematic
viscosity of the air and the mass diffusion
coefficient of water vapor into air.
airSc
D
=
The mass diffusion coefficient can be
plotted as a function of temperature. For airat a temperature of -7.5C, D 2.0e-5 m
2/s.
Therefore, Sc = 0.6583.
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The density of air at -7.5C = 1.3042 kg/m3,
the specific heat of the air = 1006.4 J/kgK.
Recalling that the Prandtl number = 0.715and hc = 9.45 W/m
2K, we calculate hm to be
0.0076 m/s.
Wf and Wa represent the humidity ratios at
the surface of the evaporating water and thesurrounding air, respectively.
0.622V
V
PW
P P
=
WherePis the atmospheric pressure and PV
is the saturation pressure of air a giventemperature. Wais to be evaluated at the dew
point temperature of the ambient air. For thecalculation, the average dew point in
Rochester during January was used (-7.3C).Wf is evaluated at the liquid film
temperature, 0.56C.
PVat -7.3C = 381.3 N/m2, andPVat 0.56C
= 639.9 N/m2. This gives Wf = 0.003953 &
Wa = 0.002350.
Collecting these terms and solving for "e
q
gives a heat flux required to evaporate the
melted snow equal to 47.9 W/m2.
The final term adding to the total heat flux is
the back loss, "bq . This is the loss through
the concrete down to the ground below.
There is no standard method for calculatingthis value. Generally, this heat flux is
between 5% and 20% for a well insulatedsystem. This will be verified with the finite
difference model.
Summing all of the heat flux terms(excluding "bq ), we arrive at a total heat
flux of 300.6 W/m2. Once again, this is a
baseline, preliminary heat flux calculation.We expect the actual heat flux found using
the finite difference model to be greater thanthis value.
Finite Difference Derivation & Modeling
To analyze the temperature distribution in
the system, a finite difference model wascreated. The analysis of the system was
done at a steady state condition as ourinterest in the characteristic behavior of the
system occurs at steady state.
To perform this analysis, a small section ofthe overall system was selected taking
advantage of symmetry to simplify andexpedite the solution algorithm.
The simplified section
bisected one pipe in thevertical plane and
extended to the midpointbetween two pipes, thus
symmetry can be used onboth the right and left
edges of the grid. Thesurveyed section was
divided into a gridconsisting of equally
spaced x and y indices.Due to the scale of our
system, a grid size of 5
units/cm was used. Itmust be noted that thenumber of grid points in
the x direction wasdependent on the spacing
between the pipes, and was accounted forwhen writing the finite difference algorithm.
An energy balance was performed to deriveequations representing the steady state
temperature at each node. Specialconsiderations were employed whenencountering symmetry and material
junctions where a more complex equationwas required. The following displays the
progression and derivation of each of thefoundational equations used in our analysis.
Y
X
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x =y
+k2 (Tm,n1) (3k1 + k2 )Tm,n = 0
k1(T
m,n+1+T
m1,n+T
m+1,n)
Foundational Equations
(1)
(2)
(3)
(4)
Surface Nodes
(5)
(6)
To facilitate the linear solver used in thisanalysis, the radiation term was reduced to a
linear approximation with Tm,napproximated as the film temperature of
water before it evaporates, 0.56C.
(7)
(8)
(9)
Interior Nodes
(10)
(11)
* For symmetry, nodes at left or rightboundary account for symmetry by
multiplying the temperature of the nodeopposite the symmetry line by a factor of 2.
This approach applies to all symmetrynodes, including the top surface.
Material Junction Nodes
(12)
Where k1, k2 are the conduction coefficientsfor the two materials at the junction.
Pipe Boundary
For the pipe boundary, the actual known
pipe temperatures (the nodes represented ata constant temperature, Tpipe) were
subtracted from the solution matrix and werere-infused in their original location after the
surrounding node temperatures werederived. This allowed the final contour plot
to represent the known pipe temperature aswell as the resulting surrounding
temperatures.
To infuse the presence of the pipe into the
finite difference matrix, the numerical pipetemperature was added to the right hand side
of the finite difference equation for the nodeequations that bordered the pipe, thus
allowing for a boundary condition thatrepresented the actual pipe temperature. This
entire process was automated using analgorithm based upon the pipe geometry and
location.
The Matlab Solution
The implementation of the finite differencemethod in Matlab provided an efficient
solution and sufficient parameter variationcapabilities. The solution script utilized
Matlabs matrix expertise to intelligentlysort through each nodal location and apply
the correct nodal formula. This wasaccomplished by writing nodal equations
based upon the matrix indices and a positionalgorithm. The subtraction of the pipe
temperatures mentioned above were thenemployed and the resulting matrix was
simplified with a solver function. Due to the
q = qsnow + h(T Tm,n )+ (T4
T4
m,n )
q = qsnow + h(T Tm,n )+ hrad(T Tm,n )
Ein = Eout
q(i)(m,n) + q(x y) = 0i=14
q(node)(m,n) = k()
Tnode Tm,n
q = 0Tm,n+1
+Tm,n1
+Tm+1,n
+Tm1,n
4Tm,n
= 0
Tm,n1 +Tm+1,n +Tm1,n 3Tm,n +
x
kq = 0
q = qsnow +U(T Tm,n )
q = qsnow + h(T Tm,n )
+(T
2T
4
m,n )(T Tm,n )(T Tm,n )
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small grid size, the variable count of oursystem reached upwards of 12,000, yet
Matlab was able to provide a solution thataveraged a 5-minute run time.
It must be mentioned that during thisanalysis, an initial assumption was made
concerning the frost line temperature. Wechose to assume that the temperature at the
frost line was known, thus completing ourboundary conditions. After successful
solutions were performed, we investigatedthe veracity of this assumption by varying
the analysis depth and comparing theresulting change in temperature at the
baseline. After several trials, we determinedthat any extension past the 0.8 m frost line
yielded approximately a 0.01% change intemperature at the baseline. Thus, we
validated our assumption and focused ourefforts on other areas of our analysis.
After a final solution was reached, creating a
contour plot of the system temperatureprofile was quite simple. The pipe
temperatures that were removed earlier werere-inserted to the temperature matrix and the
simplified system was propagated to
construct the entire system.
Results
We ran several configurations of our system,varying depth, pipe, separation and fluid
temperature. Our primary goal was to
achieve a minimum temperature of 0.56Cat the surface, which occurs at the surface
midpoint between two pipes. To beginnarrowing our result, the depth was
decidedly fixed to 6 cm, while the depth andfluid temperature were varied. As expected,
the farther the pipe separation, the more heatflux was lost to the surroundings. This is
caused by an increased temperature gradientacross the surface as the minimum surface
temperature is maintained. The results ofseveral trials can be seen in Figure 3 in the
Figures & Plots section of this report.
While many configurations exist for thissystem, our final solution was taken at a
depth of 5cm, pipe separation of 12 cm, and
fluid temperature of 28.5C. The resulting
heat flux lost through the surface and ground
were 315.85 W/m2
K and 16.77 W/m2
Krespectively. Studies have shown thatsimilar systems expect approximately
5-20 % loss through the ground; our well-insulated system loses 5.04 % and
corroborates this benchmark.
Taking into account the earlier derived valueof 192.89 W/m
2K of heat flux required to
melt the snow, the total heat flux lost viaconvection and radiation in our system
amounts to 122.96 W/m2K. This correlates
to our earlier baseline calculation of 107.7
W/m2K, and is reasonably higher given the
existing temperature gradient along the
surface. The graphical results of our finalsolution are plotted below in figure 1.
With our analysis complete, we can estimate
the heat loss in any given length ofsidewalk. Our total heat flux lost, through
the surface and the ground is 332.62W/m
2K.
Just for good measure, let us consider asidewalk of length 9 meters and 1.5 meters
wide. Our heat lost would be:
Watts
Qlost =1.5L *332.62
Qlost =1.5(9)*332.62 = 4490.37
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Figure 1Contour of 1m Sidewalk Section
Figures & Plots
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Figure2
AveragedIsothermsof1mSidewalkSection
Figure 3Pipe Spacing vs Q
C
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Discussion of Results, Possible
Improvements
Improvements of our analysis would involvesolving for the heat, energy, and time
required to get the system up and running atsteady state from a starting point of ground
temperature. Another large case would be tostart from ground temperature with an
accumulation already standing on thesidewalk surface, which may increase start
up to steady state time and energyexponentially.
Conclusion
In conclusion, our resulting values from the
analysis discussed, compare favorably torealistic values estimated by printed articles
and informational sources. A system such asthe one analyzed is a real world possibility
and is already implemented for variouscircumstances requiring heating. For
example, the heating of floors in some up-scale homes are done using a heated
working fluid flow through piping imbedded
into the floor.
Citations
Cematrix.com. Edited by Cematrix
Corporation. Accessed 10/27/11.
http://www.cematrix.com/docs/technical/physical_properties2009mar04.pdf
Diffusion Coefficient for Air-Water Vapor
Mixtures Web. 02 Nov. 2011.
Galloway, Kevin; Landolt, Scott;
Rasmussen, Roy. Using liquid-equivalent snow gauge
measurements to determine snowdepth - Preliminary Results Nov.
2006
Incropera, Frank P., David P. Dewitt,Theodore L. Bergman, and Adrienne
D. Lavine. Fundamentals of Heatand Mass Transfer. 6th ed. Hoboken,
NJ: John Wiley & Sons, 2007.
Ramsey, James W. Development of SnowMelting Load Design Algorithms and
Data for Locations Around theWorld Vol. 1,ASHRAE1999
"Water Vapor and Vapor Pressure." Web.
07 Nov. 2011..
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A1:FiniteDifferenceScript% Active Sidewalk Heating Finite Difference
clcclear all
close all
ticDepth_of_Field=.8; % mradius=5; % gridsrad_vec=[2 3 4 5 5 5];emissivity=.88;steff_boltz=5.67e-8;Pipe_Depth=5; % cmPipe_Separation=12; % cmDelta_x=.002; % m
Ysize=Depth_of_Field*500;Xsize=Pipe_Separation/2*5+1;
Tpipe=28.5; % CTpipe2=-Tpipe; % CTsurfC=-7.5; % CTsurfK=TsurfC+273.15; % KFrostLine=0; % CHsurf=9.451; % W/m^2KRsurf=3.9153; % W/m^2KUsurf=Hsurf+Rsurf; % W/m^2KQsnow=192.8894; % W/m^2Kkc=.72;kcm=.1;kgr=2.4;
ks=.52;Dcematrix=15; % cmDgravel=Dcematrix+5; % cmDsoil=Dgravel+30; % cm
% Allocate MemoryFDM=zeros(Xsize*Ysize,Xsize*Ysize);Q=zeros(Xsize*Ysize,1);
% Write the Eqautions to a Matrixfor j=1:Xsize
for i=1:Ysizepos=(i+Ysize*(j-1));
% Top Left Nodeif i==1 && j==1
FDM(pos,pos)=-(3+(Delta_x*Usurf)/kc);FDM(pos,pos+Ysize)=2;FDM(pos,pos+1)=1;Q(pos)=(Qsnow -Usurf*TsurfC)*(Delta_x/kc);
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% Top Right Nodeelseif i==1 && j==Xsize
FDM(pos,pos)=-(3+(Delta_x*Usurf)/kc);FDM(pos,pos-Ysize)=2;FDM(pos,pos+1)=1;Q(pos)=(Qsnow -Usurf*TsurfC)*(Delta_x/kc);
% Top Middle Nodeselseif i==1
FDM(pos,pos)=-(3+(Delta_x*Usurf)/kc);FDM(pos,pos+Ysize)=1;FDM(pos,pos-Ysize)=1;FDM(pos,pos+1)=1;Q(pos)=(Qsnow -Usurf*TsurfC)*(Delta_x/kc);
% Top Left Node of Material Junctionelseif (i==5*Dcematrix | i==5*Dgravel | i==5*Dsoil) & j==1
if rem(5*i,Dcematrix)==0k1=kc; k2=kcm;
elseif rem(5*i,Dgravel)==0
k1=kcm; k2=kgr;elseif rem(5*i,Dsoil)==0k1=kgr; k2=ks;
end
FDM(pos,pos)=-(3*k1+k2);FDM(pos,pos+Ysize)=2*k1;FDM(pos,pos+1)=k2;FDM(pos,pos-1)=k1;
% Top Right Node of Material Junctionelseif (i==5*Dcematrix | i==5*Dgravel | i==5*Dsoil) & j==Xsize
if rem(5*i,Dcematrix)==0k1=kc; k2=kcm;
elseif rem(5*i,Dgravel)==0k1=kcm; k2=kgr;
elseif rem(5*i,Dsoil)==0k1=kgr; k2=ks;
end
FDM(pos,pos)=-(3*k1+k2);FDM(pos,pos-Ysize)=2*k1;FDM(pos,pos+1)=k2;FDM(pos,pos-1)=k1;
% Top Middle Nodes of Material Junctionelseif (i==5*Dcematrix | i==5*Dgravel | i==5*Dsoil)
if rem(5*i,Dcematrix)==0k1=kc; k2=kcm;
elseif rem(5*i,Dgravel)==0k1=kcm; k2=kgr;
elseif rem(5*i,Dsoil)==0
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k1=kgr; k2=ks;end
FDM(pos,pos)=-(3*k1+k2);FDM(pos,pos+Ysize)=k1;FDM(pos,pos-Ysize)=k1;FDM(pos,pos+1)=k2;FDM(pos,pos-1)=k1;
% Bottom Left Nodeelseif i==Ysize && j==1
FDM(pos,pos)=-4;FDM(pos,pos+Ysize)=2;FDM(pos,pos-1)=1;Q(pos)=-FrostLine;
% Bottom Right Nodeelseif i==Ysize && j==Xsize
FDM(pos,pos)=-4;FDM(pos,pos-Ysize)=2;
FDM(pos,pos-1)=1;Q(pos)=-FrostLine;
% Bottom Middle Nodeselseif i==Ysize
FDM(pos,pos)=-4;FDM(pos,pos-1)=1;FDM(pos,pos-Ysize)=1;FDM(pos,pos+Ysize)=1;Q(pos)=-FrostLine;
% Left Side Nodeselseif j==1
FDM(pos,pos)=-4;FDM(pos,pos+Ysize)=2;FDM(pos,pos-1)=1;FDM(pos,pos+1)=1;
% Right Side Nodeselseif j==Xsize
FDM(pos,pos)=-4;FDM(pos,pos-Ysize)=2;FDM(pos,pos-1)=1;FDM(pos,pos+1)=1;
% Interior Nodeselse
FDM(pos,pos)=-4;FDM(pos,pos+1)=1;FDM(pos,pos-1)=1;FDM(pos,pos+Ysize)=1;FDM(pos,pos-Ysize)=1;
end
rad_vec=[2,3,4,5,5,5];
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DfromTop=5*Pipe_Depth+1;LfromEdge=(Pipe_Separation/2)*5+1-radius;
% Insert Pipe Temperaturesif i==DfromTop-2 && j==(LfromEdge-1)
Q(pos:(pos+2*rad_vec(1)))=-Tpipe;
elseif i==(DfromTop-3) && j==(LfromEdge)Q(pos)=-2*Tpipe;Q(pos+2*rad_vec(2))=-2*Tpipe;
elseif i==(DfromTop-4) && j==(LfromEdge+1)Q(pos)=-2*Tpipe;Q(pos+2*rad_vec(3))=-2*Tpipe;
elseif i==(DfromTop-5) && j==(LfromEdge+2)Q(pos)=-2*Tpipe;Q(pos+2*rad_vec(4))=-2*Tpipe;
elseif i==(DfromTop-6) && j==(LfromEdge+3)Q(pos)=-Tpipe;Q(pos+2*rad_vec(5)+2)=-Tpipe;
elseif i==(DfromTop-6) && j==(LfromEdge+4)Q(pos)=-Tpipe;Q(pos+2*rad_vec(6)+2)=-Tpipe;
elseif i==(DfromTop-6) && j==(LfromEdge+5)Q(pos)=-Tpipe;Q(pos+2*rad_vec(6)+2)=-Tpipe;
end
endend
% Subtract Known Temperaturesfor j=Xsize:-1:1
for i=Ysize:-1:1pos=(i+Ysize*(j-1));
if i==(DfromTop-rad_vec(6)) && j==XsizeFDM(:,pos:(pos+2*rad_vec(6)))=[];FDM(pos:(pos+2*rad_vec(6)),:)=[];Q((pos):(pos+2*rad_vec(6)))=[];Qpos(6)=pos-1;
elseif i==(DfromTop-rad_vec(5)) && j==(Xsize-1)FDM(((pos):(pos+2*rad_vec(5))),:)=[];FDM(:,((pos):(pos+2*rad_vec(5))))=[];Q((pos):(pos+2*rad_vec(5)))=[];Qpos(5)=pos-1;
elseif i==(DfromTop-rad_vec(4)) && j==(Xsize-2)FDM(((pos):(pos+2*rad_vec(4))),:)=[];FDM(:,((pos):(pos+2*rad_vec(4))))=[];
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Q((pos):(pos+2*rad_vec(4)))=[];Qpos(4)=pos-1;
elseif i==(DfromTop-rad_vec(3)) && j==(Xsize-3)FDM(((pos):(pos+2*rad_vec(3))),:)=[];FDM(:,((pos):(pos+2*rad_vec(3))))=[];Q((pos):(pos+2*rad_vec(3)))=[];Qpos(3)=pos-1;
elseif i==(DfromTop-rad_vec(2)) && j==(Xsize-4)FDM(((pos):(pos+2*rad_vec(2))),:)=[];FDM(:,((pos):(pos+2*rad_vec(2))))=[];Q((pos):(pos+2*rad_vec(2)))=[];Qpos(2)=pos-1;
elseif i==(DfromTop-rad_vec(1)) && j==(Xsize-5)FDM(((pos):(pos+2*rad_vec(1))),:)=[];FDM(:,(pos):(pos+2*rad_vec(1)))=[];Q((pos):(pos+2*rad_vec(1)))=[];Qpos(1)=pos-1;
endend
end
%SolveTmat=FDM\Q;T_pipe_ref=zeros(size(Tmat,1),1);
% Format the ResultsT_rem=54;for i=length(rad_vec):-1:1
Tadd=rad_vec(i)*2+1;
Adjust=T_rem-Tadd;T_rem=T_rem-Tadd;
Tmat1=[(Tmat((1:(Qpos(i)-Adjust)),1))'];Tmat2=[(Tpipe.*ones(1,2*rad_vec(i)+1))];Tmat3=[(Tmat((Qpos(i)-Adjust+1):length(Tmat)))'];Tmat=[Tmat1 Tmat2 Tmat3];Tmat=Tmat';
T_pipe_ref1=[(T_pipe_ref((1:(Qpos(i)-Adjust)),1))'];T_pipe_ref2=[(Tpipe2.*ones(1,2*rad_vec(i)+1))];T_pipe_ref3=[(T_pipe_ref((Qpos(i)-Adjust+1):length(T_pipe_ref)))'];T_pipe_ref=[T_pipe_ref1 T_pipe_ref2 T_pipe_ref3];T_pipe_ref=T_pipe_ref';
end
T_Plot1=[];T_Plot2=[];for i=1:XsizeT_Plot1(:,i)=Tmat(1+(i-1)*Ysize:i*Ysize);T_Plot2(:,i)=T_pipe_ref(1+(i-1)*Ysize:i*Ysize);
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end
T_Plot=T_Plot1;x=[T_Plot flipdim(T_Plot,2)];x=[x x x x x x x x];
figure(1)contourf(flipdim(x,1))colorbarset(gcf,'position',[13 611 1084 1295])figure(2)imagesc(x)colorbarset(gcf,'position',[13 611 1084 1295])toc
% Heat Flux Through Top & Bottom SurfacesQ_Top=[];Q_Bot=[];for j=1:Xsize
Q_Top=[Q_Top (Usurf*(x(1,j)-TsurfC)+Qsnow)];Q_Bot=[Q_Bot ((T_Plot(70,j)-T_Plot(400,j))/(.002*5/kc+.002*25/kcm+.002*150/kgr+.002*150/ks))];endQ_Top=mean(Q_Top)Q_Bot=mean(Q_Bot)Q_Tot=Q_Top+Q_Bot;
load gongsound(y,Fs)
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A2:Misc.Calculations% Heat Transfer Project scriptclcclear
% finding the density of snowTa = 273.15 - 7.5; % KelvinU10 = 5.2; % m/srhoSnow = 500*(1 - 0.951*exp(-1.4*(278.15 - Ta)^(-1.15) -0.008*U10^1.7)); % kg/m^3
% Finding equivalent rate of liquid precipitation.Snow_Rate = 0.013; % m/hrrhoH2O = 1000; % kg/m^3s = Snow_Rate/(3600*(1000/rhoSnow)); %m/hr
% Calculating
CpIce = 2100; % [J/kg*K]CpH2O = 4217; % [J/kg*K]tf = 273.15 + .56; % liquid film temperature [K] for melted snowts = 273.15; % melting temperature [K]
qs = rhoH2O*s*(CpIce*(ts - Ta) + CpH2O*(tf - ts)); % [W/m^2]
hf = 334000; % heat of fusion for water [J/kg]
qm = rhoH2O*s*hf; % [W/m^2]
% calculating Convection coefficient
% calculate Reynolds number based on worst case (wind across short edgeofsidewalk.)
kin_Visc = 13.1666e-06; % kinematic vis. @ walkway film temp(269.4K)[m^2/s]
w = 1.5; % sidewalk width [m]ReL = U10*w/kin_Visc; % Reynolds NumberPr = 0.715; % Prandtl NumberNuL = (0.037*ReL^(4/5) - 871)*Pr^(1/3); % Nusselt Numberkair = 0.023852; % thermal conductivity of air [W/m*K]hc = kair*NuL/w; % convection coefficient
CpAir = 1006.4; % [J/kgK]rhoAir = 1.3042; % kg/m^3
D = 2.0e-5; % mass diffusion coefficient of H2O into airSc = kin_Visc/D; % Schmidt Number
hm = (Pr/Sc)^(2/3)*hc/(rhoAir*CpAir); % mass transfer coefficient [m/s]
Wf = 0.00398; % Humidity ratio, air at 0.56 deg C assumed tf ofliquidWa = 0.00205; % Humidity ratio, ambient airhfg = 2501525; % Heat of vaporization at 0 deg C for H2O
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qe = rhoAir*hm*(Wf - Wa)*hfg
e = 0.88; % emissivitySB = 5.67e-8; % Stefan-Boltzman Constant
% Radiation coefficient (estimation)hr = e*SB*(273.71^2 + Ta^2)*(273.71 + Ta);
% Baseline heat lost through convection and coefficientqh = hc*(0.56 - -7.5) + SB*e*((273.15+0.56)^4 - Ta^4)
% Baseline heat fluxqtot = qs + qm + qe + qh% Baseline heat lossQ = qtot*1.5*9