Science – Society – Technology
From: Making use of geothermal brine in Indonesia: binary demonstration power plant Lahendong/Pangolombian
Component | Description |
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Evaporator | Assumed design data*: di = 12 mm, t = 2 mm, λW = 50 W/(m K), ntubes = 344, npass = 2, sL = 1.45 do, sT = 1.45 do, sB = Di,Sh, staggered arrangement, AHX = 202 m2 Assumed fouling: RfH = 0.2 10−3 m2 K/W, RfC = 0.2 10−3 m2 K/W Preheating: heat transfer tube side = 1-phase turbulent pipe flowa, heat transfer & pressure drop shell side = 1-phase flow shell-and-tube with bafflesb Evaporation: heat transfer tube side = 1-phase turbulent pipe flowa, heat transfer shell side = pool boilingc, pressure drop shell side = 0.01 bar; Superheating: heat transfer tube side = 1-phase turbulent pipe flowa, heat transfer shell-side = 1-phase flow across tube bundled; flow correction factori |
Recuperator | Assumed design data*: di = 24.4 mm, t = 2 mm, λW = 50 W/(m K), ntubes = 26, npass = 4, sF = 3.18 mm, δF = 0.4 mm, hF = 8.3 mm, λF = 500 W/(m K), inline arrangement, AHX = 478 m2 Assumed fouling: RfH = 0.18 10−3 m2 K/W, RfC = 0.1 10−3 m2 K/W Heat transfer: heat transfer & pressure drop tube side = 1-phase turbulent pipe flowa,f, heat transfer & pressure drop shell side = 1-phase flow across finned-tube bundlese,g, flow correction factor for crossflowi |
Condenser | Assumed design data*: di = 14.8 mm, t = 1.6 mm, λW = 50 W/(m K), ntubes = 672, AHX = 551 m2 Assumed fouling: RfC = 0.17 10−3 m2 K/W Heat transfer: heat transfer tube side = 1-phase turbulent pipe flowa, heat transfer shell side = condensation on horizontal tube bundleh, pressure drop shell side = 0.01 bar; flow correction factori |
Dry cooler | Assumed design data*: di = 11 mm, t = 1.6 mm, λW = 50 W/(m K), npass = 1, nrows = 5, sL = 2.3 do, sT = 2.0 do, sF = 2.65 mm, δF = 0.25 mm, hF = 8.3 mm, λF = 140 W/(m K), staggered arrangement, AV/AC = 0.25, AC = 120 m2; ηel,V = 0.75 Heat transfer: heat transfer tube side = 1-phase turbulent pipe flowa, heat transfer air side = 1-phase flow across finned-tube bundlee,g |
Turbogenerator | Model: Nozzle stage = Laval-nozzle with constant minimum cross-section, turbine wheel = variable isentropic efficiency Assumed design data*: ηis,T = 0.75, ηel,TG = 0.85; Anoz = 2260 mm2 Operational data: variable ηis,T based plant data evaluation (see Fig. 14), |
Working fluid pump | Pressures and volume flow rate from process calculation; ηel, P = 0.8, ηis,P = 0.75 |
Hot water and cooling water pump | Power consumption characteristic based on real data as a function of volumetric flow rate |