By Ryszard Bartnik
Conversion of Coal-Fired energy Plant to Cogeneration and Combined-Cycle offers the method, calculation techniques and instruments used to aid company making plans for adapting strength stations to cogeneration and combined-cycle forms.
The authors learn the optimal choice of the constitution of warmth exchangers in a 370 MW energy block, the constitution of warmth restoration steam turbines and gasoline generators. Conversion of Coal-Fired strength Plant to Cogeneration and Combined-Cycle additionally addresses the issues of changing current energy crops to dual-fuel gas-steam combined-cycle applied sciences coupled with parallel structures.
Conversion of Coal-Fired energy Plant to Cogeneration and Combined-Cycle is an informative monograph written for researchers, postgraduate scholars and coverage makers in energy engineering.
Read Online or Download Conversion of Coal-Fired Power Plants to Cogeneration and Combined-Cycle: Thermal and Economic Effectiveness PDF
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Extra resources for Conversion of Coal-Fired Power Plants to Cogeneration and Combined-Cycle: Thermal and Economic Effectiveness
Example text
8 100 120 140 160 180 200 220 240 Mass stream of steam into LP section [kg/s] Fig. 11 Internal efficiency of the LP section of the turbine in the function of steam stream into LP casing it was assumed that the pressure losses are constant in them. 5). For the pipelines joining the turbine with HP heaters the calculated pressure drops in the function of the mass stream of steam through them are presented in Figs. 13. The product of heat transfer coefficient and heating surface (kFn) has been determined for each of the heaters for the operation of the power unit with the rated capacity NelST ¼ 370 MW: They can be considered as constant over the entire range of the variability of water and steam mass flows.
3b) _ GT À ðtHP þ DT HP Þ ¼ m_ s ðhs À h0 Þ þ m_ r ðhp À hr Þ C½t out s min r s _ HP þ DT HP À ðtIP þ DT IP Þ ¼ m_ s ðh0 À h0 Þ þ m_ r ðhr À h0 Þ C½t s r r s min s min ð2:56Þ ð2:57Þ while the stream of the thermal capacity of the flue gas is expressed by the equation GT tout C_ ¼ m_ GT cGT fg " fg jtamb ¼ and: hpr ; hr, hs GT _ ðPðNCVÞÞ gas jt amb À N el tGT out À tamb ¼ N GT el ð1 À gGT Þ gGT ðtGT out À t amb Þ ð2:58Þ specific enthalpy of the intermediate-and high-pressure superheated steam (the specific enthalpy of the intermediate-pressure superheated steam hpr is determined for the temperature of tpr t1 ¼ t3 and pressure ppr p2 ; enthalpy hr for the temperature 28 0 2 Selection of Optimal Heating Structures 0 h s ; hr HP tIP s ; ts HP DT IP min ; DT min of tr tHP and pressure of pr = ppr p2 ; enthalpy hs for the s temperature of ts : t1 and pressure ps : p1); the specific enthalpy of water at the bubbly flow point (x = 0) in the intermediate-and high-pressure sections of the heat recovery steam generator; temperature of saturation in the condenser of the intermediateand high-pressure section of the heat recovery steam generator p (temperature tIP s corresponds to the pressure of pr ¼ pr p2 ; the HP temperature ts to the pressure ps : p1); pinch point of the intermediate- and high-pressure sections of the heat recovery steam generator.
900 100 120 140 160 180 200 220 Steam mass flow into the condenser of main turbine [kg/s] Fig. e. 5% mechanical efficiency of the turbine. 6 KQ1, KQ2 Condensers in Main and Auxiliary Turbines It is necessary to determine the characteristic of the temperature of cooling water fed into it in the function of the ambient temperature (Fig. 17). In accordance with the exploitation instructions of the turbine it was assumed that the temperature of the cooling water for the operation of the power unit with the rated capacity may not drop below 15°C.