25 06 18sol

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Problem 1 turbine inlet mass flow rate, stream 10 30.000 kg/s p1 100.000 bar T1 500.00 °C p5 40.000 bar T5 500.00 °C pressure drop admission valve 5.000 bar p6 0.050 bar p7 0.050 bar p4 40.000 bar boiler thermal effiicency 0.9100 isentropic efficiency turbine 0.9200 electric generator efficiency 0.9850 shaft mechanical efficiency (turbine) 0.9900 hydraulic efficiency pump 0.8700 water‐side pressure drop regenerator 2.000 bar % pressure drop boiler 20.00 mechanical and electrical efficiency pump 0.9500 T9 240.00 °C p10 40.000 bar T11 40.00 °C TphsvX °C bar kJ/kg kJ/kg‐K m3/kg 1 500.00 100.000 3 375.06 6.5993 1.0000 2 497.60 95.000 3 375.06 6.6211 1.0000 3iso 359.34 40.000 3 116.47 6.6212 1.0000 3 367.79 40.000 3 137.16 6.6536 1.0000 4 367.79 40.000 3 137.16 6.6536 1.0000 5 500.00 40.000 3 445.84 7.0919 1.0000 6iso 250.36 40.000 2 162.32 4.8499 0.6273 6 32.88 0.050 2 265.00 7.4274 0.8779 7 32.88 0.050 137.77 0.4763 0.001005 0.0000 8 33.66 127.000 152.43 0.4826 0.0000 9 240.00 125.000 1 038.69 2.6823 0.0000 10 367.79 40.000 3 137.16 6.6536 1.0000 11 40.00 40.000 171.08 0.5710 0.0000 12 32.88 0.050 171.08 0.0137 mass flow rate of stream 10 8.964 kg/s from energy balance of the regenerator where m10 is the only unknown mass flow rate of stream 4 to RH 21.036 kg/s as diffrence: m4 = m3 ‐ m10 electirc power of steam turbine 31 182.6 kW from energy balance of turbine: (m3*(h2‐h3)+m6*(h5‐h6))*eff_el*eff_mecc pump electirc power 487.6 kW from energy balance of pump: m8*(h8‐h 7)/(eta_mecc*eta_el) net electric power 30 694.9 kW Pel_turbo‐Pel_pump cycle thermal power 76 584.3 kW energy balance of boiler tubes: m1 *(h1‐h9)+mRH*(h4‐h5) fuel thermal power 84 158.6 kW net electric efficiency 36.47 % Data point Problem 2 Problem data Data from chart/tables Evaporation temperature, Teva…