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>iaapplicati<strong>on</strong>s. Low-temperature district heating systemsare defined as networks where fluids at a temperaturebelow 50 °C are used, while a medium-temperaturedistrict heating system is defined as using fluids attemperatures not higher than 70 °C [11, 12].Steady-state heat losses from pre-insulated buriedpipes are generally treated by use of the followingequati<strong>on</strong> [10], which is valid for each pipe-i:where Uij is the heat transfer coefficient between pipe-i<strong>and</strong> pipe-j, Tj is the temperature of the water in pipe-j<strong>and</strong> T0 is the temperature of the ground. In case of twoburied pipes, which is the most comm<strong>on</strong> applicati<strong>on</strong> inthe DH sector, the heat losses can be calculated asfollows, respectively for the supply pipe <strong>and</strong> the returnpipe, where T1 is the supply temperature <strong>and</strong> T2 is thereturn temperature.(1)Supply pipe: (2)Return pipe: (3)Equati<strong>on</strong>s (2) <strong>and</strong> (3) show how the heat transfer fromeach pipe can be seen as linear superimpositi<strong>on</strong> of twoheat fluxes, the first <strong>on</strong>e describing the heat transferbetween the pipe <strong>and</strong> the ground, the sec<strong>on</strong>d <strong>on</strong>erepresenting the heat transfer between the supply pipe<strong>and</strong> the return pipe. The equati<strong>on</strong>s can also bere-arranged in the following way:thermal coefficient, which is functi<strong>on</strong> of the temperaturein this case. U-values are dependent both <strong>on</strong>temperature <strong>and</strong> time. If the time-dependency due tothe ageing of the foam can be restrained by introducingeffective diffusi<strong>on</strong> barriers, that is not true for theintrinsic dependency <strong>on</strong> temperature. It is practice toevaluate the steady state heat loss applying a thermalc<strong>on</strong>ductivity value that corresp<strong>on</strong>ds to a hypothesizedmean temperature of the insulati<strong>on</strong>. Nevertheless weneed models based, for example, <strong>on</strong> the finite elementmethod (FEM) when complex geometries or a highdegree of detail are requested.Temperature dependant thermal c<strong>on</strong>ductivity ofPUR insulati<strong>on</strong> foamIn this paragraph the authors want to explain <strong>and</strong>dem<strong>on</strong>strate the importance of taking into account thetemperature-dependency of the thermal c<strong>on</strong>ductivity ofthe insulati<strong>on</strong> (lambda-value). The temperaturegradient in the insulati<strong>on</strong> foam in the radial directi<strong>on</strong> isoften higher then 10 °C/cm, meaning that the thermalc<strong>on</strong>ductivity of the material locally varies remarkably. Inthe example shown Figure 2, it varies more than 10%of the prescribed mean value. This affects themagnitude of the heat transfer. C<strong>on</strong>sidering a life cycleassessment of a DH system, the main impact to theenvir<strong>on</strong>ment is represented by heat losses [13]. Thethermal c<strong>on</strong>ductivity of the insulati<strong>on</strong> material inpre-insulated DH pipes is usually stated at atemperature of 50 °C. The lambda-coefficients werechosen according to the available data at the end of2009; the lambda-value at 50 °C for straight pipes,axial c<strong>on</strong>tinuous producti<strong>on</strong> was set to 0.024 W/(mK)<strong>and</strong> for flexible pipes to 0.023 W/(mK). Since April 2010new results are available [14]. It is preferable to have amodel that takes into account the temperaturedependencyof the thermal c<strong>on</strong>ductivity of theinsulati<strong>on</strong> foam. The calculati<strong>on</strong>s in this paper use thefollowing expressi<strong>on</strong>, if not differently stated. It derivesfrom experimental data [15]:λ(T) = 0.0196734 + 8.0747308 . 10-5.T [W/(mK)] (1)Supply pipe: (4)Return pipe: (5)Equati<strong>on</strong>s (4) <strong>and</strong> (5) show how the heat transfer fromeach pipe can be calculated by use of <strong>on</strong>ly <strong>on</strong>e linearFigure 2: Thermal c<strong>on</strong>ductivity in the insulati<strong>on</strong>, horiz<strong>on</strong>talcross-secti<strong>on</strong> of the pipe. Pipe: Aluflex 16-16/110,temperatures supply/return/ground 55/25/8 °C.83
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>iaTemperature field in the soil around the pipeIn this paper we address the questi<strong>on</strong> of how to createa simple yet detailed FEM model for steady state heatloss calculati<strong>on</strong>s. The overall heat transfer resistancebetween the DH water <strong>and</strong> the envir<strong>on</strong>ment is mainlycomposed of the thermal resistance of the insulati<strong>on</strong><strong>and</strong> the thermal resistance of the soil; compared tothese two factors, the thermal resistances of the pipewall <strong>and</strong> the c<strong>on</strong>vective resistance at the surface waterpipeare in practice negligible. The insulati<strong>on</strong> foamalways offers the greatest share in the overallinsulati<strong>on</strong> effect. The c<strong>on</strong>tributi<strong>on</strong> of the soil is smaller<strong>on</strong> small-sized pipes than <strong>on</strong> large-sized pipes. Theshare is smaller in Insulati<strong>on</strong> Series 2 <strong>and</strong> 3 [3]. Theheat c<strong>on</strong>ductivity coefficient of the soil is the mainparameter affecting the thermal resistance of the soilitself, <strong>and</strong> its value is often unknown in practice.In thecalculati<strong>on</strong>s we chose a value of 1.6 W/(m.K). The soiltemperature influences heat losses from DH pipes. Thesoil layer around the heating pipes slightly warms uparound the pipes. The evaluati<strong>on</strong> of the temperaturefield in the soil is a prerequisite to create a realisticmodel for calculati<strong>on</strong>s of heat losses. Finite ElementMethod (FEM) simulati<strong>on</strong>s were carried out <strong>and</strong>temperature c<strong>on</strong>diti<strong>on</strong>s in the soil around a typical DHservice pipe, suitable for low-temperature applicati<strong>on</strong>swere evaluated over a 10-year period.Table 1: Thermal properties of materials.λ [W/(m∙K)] ρ [kg/m³] C p [J/(kg∙K)]λ soil 1.6 ρ soil 1600 C p_soil 2000λ PE 0.43 ρ PE 940 C p_PE 1800Combined heat <strong>and</strong> moisture transfer is disregarded.The material properties are homogeneous <strong>and</strong> phasechanges, i.e. freezing <strong>and</strong> thawing were notc<strong>on</strong>sidered. Table 1 lists the material properties, usedas input values also for the following models; a sketchof the slab-model, where the boundary c<strong>on</strong>diti<strong>on</strong>s aredescribed, can be seen in Figure 3.Figure 3: Sketch of the model. Dimensi<strong>on</strong>s are in [mm].FEM modelA rectangle representing a semi-infinite soil domain(width: 10–20 m, height: 20–40 m) is the most usedgeometry to model the ground in heat loss calculati<strong>on</strong>s[18, 19]. In this paper a finite, circular soil domain wasapplied, instead. Its diameter is 0.5 m <strong>and</strong> it is equal tothe distance between the surface <strong>and</strong> the centre of thecasing pipe. Calculati<strong>on</strong>s show that the introducedsimplificati<strong>on</strong> hardly affects the accuracy of the results.The mesh model <strong>and</strong> an example of the temperaturefield in a small size twin pipe are shown in Figure 4.λ PUR 0.023λ PEX 0.38ρ PURρ PEX60 C p_PUR 1500938 C p_PEX 550λ Steel 76ρ Steel8930C p_Steel480λ Cu 400 ρ Cu 8930 C p_Cu 385The simulati<strong>on</strong> calculated the soil temperature atvarious x-coordinates from a commercial branch pipe.The selected pipe was the Aluflex twin pipe 16-16/110.Temperatures were set at 55 °C <strong>and</strong> 25 °C,respectively for the supply pipe <strong>and</strong> the return pipe.The heat transfer coefficient at the ground surface wasassumed to be 14.6 W/(m2K), including c<strong>on</strong>vecti<strong>on</strong> <strong>and</strong>radiati<strong>on</strong> [16]; we set the outdoor air temperatureduring the year according to the harm<strong>on</strong>ic functi<strong>on</strong> validfor the Danish climate [17]: M T air 8.0 8.5 sin2 (6) 12 Figure 4: Mesh model of a pre-insulated twin pipeembedded in the ground (top <strong>and</strong> left). Temperature fieldin Aluflex twin pipe 16-16/110 (bottom-right); temperaturesupply/return/ground: 55/25/8 °C.In [3], where FEM simulati<strong>on</strong>s were performed, it isstated that for media pipes size from DN 50 to DN 400,the deviati<strong>on</strong> of the lineal thermal coefficient betweenthe piggy-back laying (arranging the supply pipe belowthe return pipe) <strong>and</strong> the traditi<strong>on</strong>al system (horiz<strong>on</strong>tallaying) is less than 1%. The same c<strong>on</strong>clusi<strong>on</strong> can bestated for twin pipes; this is c<strong>on</strong>firmed by calculati<strong>on</strong>s84
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to heating costs of 14,5 ct/kWh. Th
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academic access is facilitated as t
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1. CHP system operation in A2. Ther
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is covered by operating HOB. In oth
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produce heat and electricity. Fluct
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production and provide for marginal
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In addition, it can also be observe
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Stockholm district heating system a
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The values presented do of course l
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