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>iaheating load periods; hence by-pass at the criticalc<strong>on</strong>sumers are not necessary <strong>and</strong> the exergy loss dueto the mixing of warm water into the return line isavoided. Furthermore the water flow in the return linehas the same directi<strong>on</strong> as in the supply line (clockwisein the example), so that the smallest size for the returnpipes are expected in corresp<strong>on</strong>dence to the biggestsize for the supply size, <strong>and</strong> vice versa. This results inlower local pressure differences between supply <strong>and</strong>return lines <strong>and</strong> savings in operati<strong>on</strong>al costs, thanks tolower heat losses. This is shown in Table 4 <strong>and</strong> Table5, by means of two examples: the first <strong>on</strong>e refers to asmall to medium-size distributi<strong>on</strong> network, the sec<strong>on</strong>d<strong>on</strong>e to a bigger <strong>on</strong>e, being capable to supply four timesmore energy than the previous <strong>on</strong>e.Triple branch pipesThe development of an optimized triple pipe soluti<strong>on</strong> forlow-energy applicati<strong>on</strong>s is reported to show thepotentiality of utilizing detailed models for steady-stateheat loss calculati<strong>on</strong>. In this survey focus was given <strong>on</strong>the choice of media pipes diameters as small aspossible. The triple pipe geometry is based <strong>on</strong>modificati<strong>on</strong>s of the 14-14/110 (outer diameters in [mm]of respectively supply pipe, return pipe, casing) twinpipe design which has been reported in [18]. Fourgeometrical variati<strong>on</strong>s have been c<strong>on</strong>sidered (seeFigure 8) <strong>and</strong> the Cartesian coordinates describing theplacement of media pipes inside the casing are listed inTable 6.Table 4: Comparis<strong>on</strong> between a distributi<strong>on</strong> networkbased <strong>on</strong> twin pipe (DN40-40 <strong>and</strong> DN80-80) with adistributi<strong>on</strong> network based <strong>on</strong> double pipe (DN40-80 <strong>and</strong>DN80-40). Supply/return/ground temperature: 55/25/8 °C.Size(DN)Heat loss [W/m]Sup. Ret. Tot.Total(system) [%]40-40 -6.24 0.04 -6.20 Twin:80-80 -7.66 0.07 -7.59 -13.7940-80 -5.55 0.05 -5.5880-40 -7.41 0.05 -7.36Double:-12.94Table 5: Comparis<strong>on</strong> between a distributi<strong>on</strong> networkbased <strong>on</strong> twin pipe (DN100-100 <strong>and</strong> DN200-200) with adistributi<strong>on</strong> network based <strong>on</strong> double pipe (DN100-200<strong>and</strong> DN200-100). Supply/return/ground: 55/25/8 °C.Size(DN)Heat loss [W/m]Sup. Ret. Tot.100-100 -7.83 -0.55 -8.39200-200 -8.92 0.24 -8.68Total(system)Twin:-17.06100-200 -6.4 0.08 -6.36 Double:200-100 -8.07 -0.03 -8.69 -15.056.1[%]11.8We c<strong>on</strong>sidered an optimal placement of the mediapipes in case of double pipes, thus asymmetricalinsulati<strong>on</strong> is applied. The total amount of insulati<strong>on</strong> isused both in the twin pipe-based distributi<strong>on</strong> network<strong>and</strong> in the double pipe-based <strong>on</strong>e, so that theinvestment costs are equal in both cases. Results showthat the heat loss can be reduced by 6% by means ofdouble pipes instead of twin pipes for the low tomedium-size distributi<strong>on</strong> network. Even higher energysavings (around 12%) are possible in the case of thelarge-size distributi<strong>on</strong> network.Figure 8: four different geometries for a triple service pipetype Aluflex 14-14/110.Table 6: placement of media pipes inside the casing forfour triple pipe geometries, type Aluflex 14-14-20/110.Variati<strong>on</strong>Pipe 1(Sup.)Coordinates (x, y) [mm]Pipe 2(Ret.)Pipe 3(Sup. orre-circ.)A (14;-14) (0;20.5) (-14;-14)B (10;-14) (0;20.5) (-21;-7)C (3;-14) (0;20.5) (-21;-7)D (0; 0) (0;25) (0;-28)The results of FEM simulati<strong>on</strong>s are listed in Table 7 forthe four geometries (A, B, C, D) <strong>and</strong> the threeoperati<strong>on</strong>al modes (I, II, II), previously described. Sincemode II occurs in case of no dem<strong>and</strong> of space heating<strong>and</strong> then outside of the heating seas<strong>on</strong>, simulati<strong>on</strong>swere additi<strong>on</strong>ally performed with a more realistictemperature of the ground during that period(14 °C),c<strong>on</strong>sidering Danish weather. This gives also aninsight in the effect of ground temperature throughoutthe year.87
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>iaTable 7: Steady state heat losses of triple pipes typeAluflex 14/14/110 for 4 geometries <strong>and</strong> 3 operati<strong>on</strong>almodes. Temperature supply/recirculati<strong>on</strong>/return/ground:55/55/25/8 °C.ModeI(DHWtapping)II(supply-tosupplyrecirculati<strong>on</strong>)III(spaceheating)Table 8: Steady state heat losses of triple pipes typeAluflex 14/14/110 for 4 geometries <strong>and</strong> operati<strong>on</strong>al modeII. Temperature supply/recirculati<strong>on</strong>/ return/ ground:55/55/25/14 °C.II(supply-tosupplyrecirculati<strong>on</strong>)Geom.Geom.Pipe1Pipe1Heat loss [W/m]Pipe2Heat loss [W/m]Pipe2Pipe3Pipe3Tot.A 2.67 -0.08 2.67 5.30B 2.91 -0.29 2.75 5.38C 2.52 -0.22 2.74 5.06D 2.46 0.05 2.74 5.24A 2.67 / 2.67 5.34B 2.69 / 2.85 5.55C 2.48 / 2.70 5.18D 2.49 / 2.75 5.25A 3.46 0.48 / 3.95B 3.39 0.43 / 3.83C 3.41 0.35 / 3.76D 3.53 -0.01 / 3.53Tot.A 2.35 / 2.35 4.70B 2.37 / 2.51 4.88C 2.39 / 2.63 5.02D 2.20 / 2.42 4.62We c<strong>on</strong>clude that an absolute best design for theservice triple pipe does not exist, but it depends <strong>on</strong> theoperati<strong>on</strong>al mode that is chosen as critical. In fact theresults reported in Table 7 <strong>and</strong> Table 8 show thatgeometry C gives the lowest total heat loss foroperati<strong>on</strong>al modes I <strong>and</strong> II, while geometry D has thebest thermal performance for operati<strong>on</strong>al mode III <strong>and</strong>for operati<strong>on</strong>al mode II, if a temperature of the soil of14 °C is c<strong>on</strong>sidered. It has to be underlined that,c<strong>on</strong>sidering the operati<strong>on</strong>al mode III, geometry Dshows no heating of return water; this is a situati<strong>on</strong>always desirable, although it has a slightly higher heatloss from the supply pipe than the other geometries. Itis proved that usually operati<strong>on</strong>al mode I occurs forless than 1 h/day [20]. Moreover the temperature dropin the supply pipe to the DHW heat exchanger is criticalin low-temperature applicati<strong>on</strong>s, so that it is str<strong>on</strong>glyrecommended to minimize the heat loss from thismedia pipe. C<strong>on</strong>sidering all this <strong>and</strong> the fact that modeIII is the most likely during the heating seas<strong>on</strong> <strong>and</strong>88mode II is the most likely outside heating seas<strong>on</strong>, thec<strong>on</strong>clusi<strong>on</strong> is that geometry D is preferable.CONCLUSIONSThe soil temperature at 0.5 m below the surface variesbetween 2 °C in January-February <strong>and</strong> 14 °C inJuly–August, for Danish c<strong>on</strong>diti<strong>on</strong>s. This knowledgecan be used to better predict the winter peak load <strong>and</strong>the temperature drop in the distributi<strong>on</strong> line duringsummer.The slab-model for steady state heat loss calculati<strong>on</strong>scan be replaced, in case of small sizedistributi<strong>on</strong>/service pipes, by a model where the effectof the soil is represented by a circular soil layer aroundthe district heating pipe.The results c<strong>on</strong>firm that the vertical placement of twinmedia pipes inside the insulati<strong>on</strong> barely affects the heattransfer, in comparis<strong>on</strong> to the horiz<strong>on</strong>tal placement; thedifference between the two c<strong>on</strong>figurati<strong>on</strong>s is less than2% for the c<strong>on</strong>sidered cases.We proposed a FEM model that takes into account thetemperature-dependency of the thermal c<strong>on</strong>ductivity ofthe insulati<strong>on</strong> foam; in this way we enhanced theaccuracy of the heat transfer calculati<strong>on</strong> am<strong>on</strong>g pipesembedded in the same insulati<strong>on</strong>.We applied the model to propose optimized design oftwin pipes with asymmetrical insulati<strong>on</strong>, double pipes<strong>and</strong> triple pipes. We proved that the asymmetricalinsulati<strong>on</strong> of twin pipes leads to lower heat loss fromthe supply pipe (from -4% to -8%), leading to a lowertemperature drop; next the heat loss from the returnpipe can be close to zero.It is possible to cut the heat losses by 6–12% if anoptimal design of double pipes is used instead oftraditi<strong>on</strong>al twin pipes, without increasing the investmentcosts.The development of an optimized triple pipe soluti<strong>on</strong>was also reported. It is suitable for low-energyapplicati<strong>on</strong>s with substati<strong>on</strong>s equipped with heatexchanger for instantaneous producti<strong>on</strong> of DHW.REFERENCES[1] S. Fr<strong>on</strong>ing, ―Low energy communities with districtheating <strong>and</strong> cooling‖, 25 th C<strong>on</strong>ference <strong>on</strong> Passive<strong>and</strong> Low Energy Architecture, Dublin (2008).[2] S. F. Nilss<strong>on</strong> et al., ―Sparse district heating inSweden‖, Applied Energy 85 (2008), pp. 555–564.[3] F. Schmitt, H.W. Hoffman, T. Gohler, Strategies tomanage heat losses – technique <strong>and</strong> ec<strong>on</strong>omy,IEA-DHC ANNEX VII, (2005).[4] P.K. Olsen, B. Bøhm, S. Svendsen et al., ―Anew-low-temperature district heating system for
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