Research Article
A Thermodynamic Analysis of Two Competing Mid-Sized Oxyfuel Combustion Combined Cycles
Table 6
Assumptions used in cycle simulations.
| Compressor polytropic efficiency | 0.91 | Compressor mechanical efficiency | 0.99 | Combustor pressure drop | 4% | Turbine polytropic efficiency | 0.90 | Power turbine polytropic efficiency | 0.89 | Gas turbine mechanical efficiency | 0.99 | Generator electricity efficiency | 0.985 | Generator mechanical efficiency | 0.994 |
| Lower heating value for fuel | 46885 kJ/kg | Fuel temperature | 15∘C | Fuel compressor isentropic efficiency | 0.80 |
| Ambient temperature | 15∘C | Ambient pressure | 1.013 bar | Ambient humidity | 60% |
| Condenser pressure | 0.045 bar | HRSG heat exchangers , hot side | 0.001 bar | HRSG heat exchangers , cold side | 0.9 bar | Steam turbine isentropic efficiency | 0.89 | Superheater, LP, | 10 K | Superheater, HP, minimum | 25 K | Evaporator | 10 K | HP steam pressure | 140 bar | HP steam maximum temperature | 560∘C | LP steam pressure | 7 bar |
| Pump efficiency | 0.7 | Pump mechanical efficiency | 0.9 | Deaerator operating pressure | 1.21 bar | Deaerator saturation temperature | 105∘C |
| ASU power consumption | 735 | O2 purity | 95% | O2 compressor polytropic efficiency | 0.88 | ASU delivery pressure | 1.2 bar | ASU delivery temperature | 30∘C | Carbon dioxide compression power | 350 | Condenser efficiency, maximum | 0.85 |
| Gross power output | 100 MW |
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