The <str<strong>on</strong>g>12th</str<strong>on</strong>g> <str<strong>on</strong>g>Internati<strong>on</strong>al</str<strong>on</strong>g> <str<strong>on</strong>g>Symposium</str<strong>on</strong>g> <strong>on</strong> <strong>District</strong> <strong>Heating</strong> <strong>and</strong> <strong>Cooling</strong>,September 5 th to September 7 th , 2010, Tallinn, Est<strong>on</strong>iaMODELLING USING CONFORMAL COORDINATESIt is rather complicated to calculate the temperaturedecline in twin pipes due to the pipe geometry. A socalled c<strong>on</strong>formal mapping presented in [8] was used tomap the twin pipe geometry <strong>on</strong>to a rectangulargeometry. In the experimental measurements, thesupply <strong>and</strong> return service pipes were assumed to haveequal temperatures in the test-procedure. Then,symmetry is assumed between the four quarters of apipe cross-secti<strong>on</strong>. A quarter of a twin pipe is studied,see Fig. 5. In the x,y-plane, the temperaturedevelopment is described by the heat equati<strong>on</strong>:T T T c ( ( T) ) ( ( T) )t x x y y(1)The (x,y)-coordinates ( z x i y)are transformed tosuitable c<strong>on</strong>formal coordinates ( w u i v)with theaid of line sources <strong>and</strong> so called multipoles.water <strong>and</strong> the right-h<strong>and</strong> boundary against the pollwater. The heat flux in the vertical v-directi<strong>on</strong> is zero <strong>on</strong>the horiz<strong>on</strong>tal boundaries due to symmetry.Fig. 6 Initial temperature distributi<strong>on</strong> in the crosssecti<strong>on</strong>of a pipe quarter in the u, v-plane.In the numerical soluti<strong>on</strong>, the regi<strong>on</strong> is divided into arectangular mesh. The area factor is now the area ofeach of the cells shown in Fig.5. They are shown inFig. 7. The largest cell is the <strong>on</strong>e in the lower left cornerin Fig.5 near the stagnati<strong>on</strong> point (usp). The areas areused to calculate the heat capacity of each cell in the u-v-plane.Fig. 7 Areas of the computati<strong>on</strong>al cells in the x, y –planetransferred to a u, v-plane. The stagnati<strong>on</strong> point is denotedusp.Fig. 5 A quarter of a twin pipe in x-y-plane geometryThe heat equati<strong>on</strong> in the c<strong>on</strong>formal coordinates is:T T T c A( u, v) ( ( T) ) ( ( T) )t u u v vHere, A(u,v) is the area factor in the c<strong>on</strong>formaltransformati<strong>on</strong>.The c<strong>on</strong>sidered regi<strong>on</strong> shown in Fig. 5 is transformedto a rectangular regi<strong>on</strong> in the u, v-plane, see Fig. 6. Inthe figure, the left-h<strong>and</strong> boundary lies against the coil(2)The initial steady-state c<strong>on</strong>diti<strong>on</strong> for a twin pipe withcoil water temperature T w = 81.3ºC immersed into poolwater at T0=19.7ºC is showed in u-v coordinates inFigure 6. Then, the temperature decline of stagnantwater in the twin pipes are calculatedThe density ρ <strong>and</strong> the heat capacity c of thepolyurethane foam are assumed c<strong>on</strong>stant in thetemperature interval studied. The boundarytemperatures at the casing are given by the pooltemperature.The thermal c<strong>on</strong>ductivity λ(T) of the polyurethane foamis determined by the thermal c<strong>on</strong>ductivity at 50ºC λ 50(W/m·K) <strong>and</strong> a coefficient λ‟ to account for a lineartemperature dependence.50 50( T) 1 ' ( T T )(3)93
The <str<strong>on</strong>g>12th</str<strong>on</strong>g> <str<strong>on</strong>g>Internati<strong>on</strong>al</str<strong>on</strong>g> <str<strong>on</strong>g>Symposium</str<strong>on</strong>g> <strong>on</strong> <strong>District</strong> <strong>Heating</strong> <strong>and</strong> <strong>Cooling</strong>,September 5 th to September 7 th , 2010, Tallinn, Est<strong>on</strong>iaEVALUATION OF MEASUREMENTSThe temperature-dependent thermal c<strong>on</strong>ductivity of thepolyurethane foam is obtained by calculating thetemperature decline of the coil water. Certain values ofthe thermal c<strong>on</strong>ductivity of the polyurethane arechosen, λ 50 <strong>and</strong> λ‟. The actual λ(T) are obtained byminimizing the difference between the measured <strong>and</strong>calculated coil temperatures, (4).The difference between the calculated <strong>and</strong> measuredtemperatures for the optimal parameter values of λ 50 , λ‟<strong>and</strong> c are showed in Figure 9. The saw toothdisturbance from the measurements is seen. Thedifference giving the best fit lies in the interval -0.20 to0.25 (ºC). The error is small.The heat capacity c (J·kg -1·K -1 ) of the polyurethanefoam is input to the calculati<strong>on</strong>s. Literature referencesfor the heat capacity of polyurethane foam varies, 1300J·kg -1·K -1 at 50ºC in [9], 1400 J·kg -1·K -1 in [10], 1400-1500 J·kg -1·K -1 for rigid polyurethane foam in [11].The densities <strong>and</strong> heat capacities of water, service pipe<strong>and</strong> insulati<strong>on</strong> were assumed to be c<strong>on</strong>stant in thetemperature interval studied.The optimal parameter values of λ 50 λ‟ <strong>and</strong> c wereobtained by minimizing the difference D (ºC) betweenthe calculated T w (ºC) <strong>and</strong> measured coil temperaturesT w,meas (ºC).D max T ( t) T ( t)for t t t (4)w, calc w, meas1 2A certain time interval, 0.5
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academic access is facilitated as t
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