Table 3 Description of the modeled plant components

Evaporator

Assumed design data*: d_i = 12 mm, t = 2 mm, λ_W = 50 W/(m K), n_tubes = 344, n_pass = 2, s_L = 1.45 d_o, s_T = 1.45 d_o, s_B = D_i,Sh, staggered arrangement, A_HX = 202 m²

Assumed fouling: Rf_H = 0.2 10⁻³ m² K/W, Rf_C = 0.2 10⁻³ m² K/W

Preheating: heat transfer tube side = 1-phase turbulent pipe flow^a, heat transfer & pressure drop shell side = 1-phase flow shell-and-tube with baffles^b

Evaporation: heat transfer tube side = 1-phase turbulent pipe flow^a, heat transfer shell side = pool boiling^c, pressure drop shell side = 0.01 bar;

Superheating: heat transfer tube side = 1-phase turbulent pipe flow^a, heat transfer shell-side = 1-phase flow across tube bundle^d; flow correction factorⁱ

Recuperator

Assumed design data*: d_i = 24.4 mm, t = 2 mm, λ_W = 50 W/(m K), n_tubes = 26, n_pass = 4, s_F = 3.18 mm, δ_F = 0.4 mm, h_F = 8.3 mm, λ_F = 500 W/(m K), inline arrangement, A_HX = 478 m²

Assumed fouling: Rf_H = 0.18 10⁻³ m² K/W, Rf_C = 0.1 10⁻³ m² K/W

Heat transfer: heat transfer & pressure drop tube side = 1-phase turbulent pipe flow^a,f, heat transfer & pressure drop shell side = 1-phase flow across finned-tube bundles^e,g, flow correction factor for crossflowⁱ

Condenser

Assumed design data*: d_i = 14.8 mm, t = 1.6 mm, λ_W = 50 W/(m K), n_tubes = 672, A_HX = 551 m²

Assumed fouling: Rf_C = 0.17 10⁻³ m² K/W

Heat transfer: heat transfer tube side = 1-phase turbulent pipe flow^a, heat transfer shell side = condensation on horizontal tube bundle^h, pressure drop shell side = 0.01 bar; flow correction factorⁱ

Dry cooler

Assumed design data*: d_i = 11 mm, t = 1.6 mm, λ_W = 50 W/(m K), n_pass = 1, n_rows = 5, s_L = 2.3 d_o, s_T = 2.0 d_o, s_F = 2.65 mm, δ_F = 0.25 mm, h_F = 8.3 mm, λ_F = 140 W/(m K), staggered arrangement, A_V/A_C = 0.25, A_C = 120 m²; η_el,V = 0.75

Heat transfer: heat transfer tube side = 1-phase turbulent pipe flow^a, heat transfer air side = 1-phase flow across finned-tube bundle^e,g

Turbogenerator

Model: Nozzle stage = Laval-nozzle with constant minimum cross-section,

turbine wheel = variable isentropic efficiency

Assumed design data*: η_is,T = 0.75, η_el,TG = 0.85; A_noz = 2260 mm²

Operational data: variable η_is,T based plant data evaluation (see Fig. 14),

Working fluid pump

Pressures and volume flow rate from process calculation; η_{el, P} = 0.8, η_is,P = 0.75

Hot water and cooling water pump

Power consumption characteristic based on real data as a function of volumetric flow rate