2005 ASME Power Conference Analysis of Turbine Cycle Performance Losses Using Entropy Balance Techniques Sunder Raj Presentation
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This document describes the application of entropy balance to evaluate losses in a sample turbine cycle. It discusses calculating performance based on the first law of thermodynamics and using entropy to determine the effectiveness of energy utilization and quantify losses. A sample turbine cycle is presented and sources of losses are examined, including in the boiler, turbine, feedwater heaters, piping, and boiler feed pump. Entropy increases are used to measure irreversibilities and losses at each component.
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2005 ASME Power Conference Analysis of Turbine Cycle Performance Losses Using Entropy Balance Techniques Sunder Raj Presentation
- 2. Application of Entropy Balance in Evaluating and Quantifying Losses Sample Turbine Cycle Sources Examined – Boiler, Turbine, FW Heaters, Piping, BFP Methodology Applicable to Analyze & Evaluate Losses in Any Power Cycle
- 3. Performance Calculations Based on First Law of Thermodynamics (FLT) For Given Mass Flows & Heat Input, Proper Distribution to Satisfy FLT for Conservation of Mass & Energy FLT - Enthalpy or Quantity of Energy SLT – Entropy or Quality of Energy
- 4. FLT – “You Cannot Get Something for Nothing” SLT – “You Cannot Even Get Everything You Pay For” SLT - “Entropy Ain’t What it Used to Be” FLT to be Satisfied Before Using SLT
- 5. SLT Used to Determine Effectiveness of Energy Utilization For Natural Process, Performance Loss Results in Increase in Entropy Performance Tool Used to Develop Sample Turbine Cycle in Figure 1 Zero Imbalances in Mass & Energy
- 6. 1,847,840 W 544.3 P 1519.02 H 1000.0 F 2,115,387 W 2414.7 P 1460.39 H 1000.0 F 1,727,364 W 1,727,364 W 976 W 1348.11 H 1348.11 H 1460.39 H 3,895 W 1460.39 H 33,144 W 1317.94 H 1436.01 H 69.4 P 251.8 P 3,070 W 31.3 P 12.2 P 5,114 W 1348.11 H 3.9 P 1317.94 H 604.8 P 129.9 P 70,381 W 1348.11 H 10,174 W 1317.94 H 90,123 W 1080.55 H 1,847,840 W 1317.94 H ELEP = 974.72 H UEEP = 990.48 H 5,000 W Cond. Press. = 1.00 in.HgA 1343.23 H 70,381 W 1348.11 H 1,406,539 W 78.5 F 298,308 W Δh = 0.00 47.08 h 214,243 W 84,065 W 332.17 h 81,650 W 79,088 W 74,964 W 90,123 W 1317.94 H 1421.26 H 1286.45 H 1217.77 H 1149.73 H 1080.55 H 4,160 W 1343.23 H 586.6 P 236.7 P 65.3 P 29.4 P 11.4 P 3.7 P 0.0 F TD 0.0 F TD 5.0 F TD 5.0 F TD 5.0 F TD 5.0 F TD 2,115,387 W 1,736,524 W 1,736,524 W 1,406,539 W 1,406,539 W 483.8 F 396.2 F 122.1 P 293.2 F 244.1 F 194.6 F 145.8 F 144.9 F 78.5 F 469.24 h 374.47 h 342.6 F 263.01 h 213.00 h 163.05 h 114.23 h 113.37 h 47.08 h 483.8 F 396.2 F 313.94 h 298.2 F 249.1 F 199.6 F 149.9 F 10.0 F DC 10.0 F DC 10.0 F DC 10.0 F DC 10.0 F DC 214,243 W 298,308 W 81,650 W 160,738 W 235,701 W 329,985 W 406.2 F 359.8 F 2,115,387 W 254.1 F 204.6 F 155.8 F 149.9 F 382.14 h 332.17 h 3018.4 P 222.86 h 172.71 h 123.77 h 329,985 W 117.89 h 349.8 F 149.9 F 326.13 h Δh = 12.19 117.89 h Δh = 0.00 1805 KW ELECT. LOSSES GENERATOR OUTPUT 175,703 KW 30 PSIG H2 0.85 PF WLpExh =1,401,539 853 KW MECH. LOSSES 2146 KW ELECT. LOSSES GENERATOR OUTPUT 160,238 KW 30 PSIG H2 0.85 PF 778 KW MECH. LOSSES STEAM SEAL REGULATOR RHTR 2 3 1 5 6 4 2 5 6 HPT IPT LPT HTR. 1 HTR. 2 BFP HTR. 3 HTR. 4 HTR. 5 HTR. 6 HTR. 7 HDP CP CONDENSER IV
- 7. Steady-State Conditions All Heaters in Normal Operation Zero Blowdown or Makeup No Radiation or Cycle Isolation Losses TG Performance from Published Procedures Fixed Throttle Steam Conditions
- 8. Reheat Steam Conditions Fixed Reheater Pressure Drop 10% IV Pressure Drop 2% LPT Exhaust Pressure 1.0 in.HgA TD’s, DC’s for Heaters Fixed Extraction Piping Pressure Drops Fixed Percentages
- 9. Boiler Feed Pump Discharge Pressure 125% of Throttle Pressure Boiler Feed Pump efficiency 78% Energy addition in Condensate, Heater Drain Pumps Neglected
- 10. Entropy Increases When There is Performance Loss Entropy for Natural Process as a Whole Increases Entropy Cannot be Conserved Measure of Irreversibilities in Process Entropy of Saturated Water Zero at 32F
- 11. Pressure Drop in FW Heater Piping is Isenthalpic (No Heat Losses) Loss in Pressure Increases Entropy Quality of Energy Suffers - Available at Reduced Temperature Entropy Flow – Product of Mass Flow and Specific Entropy (Table 1 in Paper)
- 12. (1) (2) (3) (4) (5)=(1)x(4) Ext.1fromHPT 214,243 604.80 1317.94 1.557641 333,714 Ext.1toHtr.1 214,243 586.66 1317.94 1.560716 334,373 Difference 0 18.14 0.00 0.003075 659 EntropyFlow, Btu/hr-°F Description Pressure, Psia Enthalpy, Btu/lb SpecificEntropy, Btu/lb-°F MassFlow, Lb/hr
- 13. In FW Htr. Entropy Losses Occur due to Heat Transfer Inefficiencies On Shell Side, Decrease in Entropy On Tube Side, Increase in Entropy Net Result is Increase in Entropy If No Losses, Overall Entropy Change Would be Zero
- 14. In Turbine, Losses As Steam Expands Flows leaving – Decrease in Entropy Flow Flows Entering – Increase in Entropy Flow Last Stage Charged With Exhaust Losses
- 15. 3,191,400 S 3,241,311 S 3,197,971 S 3,018,484 S 3,018,484 S 1,495 S 5,968 S 51,165 S 3,257,420 S 69.4 P 5,365 S 31.3 P 12.2 P 7,966 S 3.9 P 3,211,985 S 146,107 S 122,988 S 143,353 S 139,622 S 15,848 S 133,120 S 161,105 S 2,878,271 S 333,714 S SELEP = 2,541,537 S SUEEP = 2,582,535 S 9,871 S Cond. Press. = 1.00 in.HgA 128,624 S 123,460 S 127,074 S Δh = 0.00 334,373 S 146,669 S 143,902 S 140,154 S 133,667 S 161,688 S 586.6 P 236.7 P 65.3 P 29.4 P 11.4 P 3.7 P 8,213 S 0.0 F TD 0.0 F TD 5.0 F TD 5.0 F TD 5.0 F TD 5.0 F TD 1,396,784 S 1,173,864 S 122.1 P 742,776 S 623,510 S 495,706 S 361,043 S 290,441 S 127,074 S 342.6 F 483.8 F 396.2 F 313.94 h 298.2 F 249.1 F 199.6 F 149.9 F 10.0 F DC 10.0 F DC 10.0 F DC 10.0 F DC 10.0 F DC 122,865 S 153,804 S 1,044,106 S 30,501 S 48,367 S 52,908 S 70,916 S 1,051,030 S 70,916 S Δh = 12.19 Δh = 0.00 853 KW MECH. LOSSES 2146 KW ELECT. LOSSES GENERATOR OUTPUT 160,238 KW 30 PSIG H2 0.85 PF 778 KW MECH. LOSSES WLpExh =1,401,539 1805 KW ELECT. LOSSES GENERATOR OUTPUT 175,703 KW 30 PSIG H2 0.85 PF STEAM SEAL REGULATOR RHTR 2 3 1 5 6 4 2 5 6 HPT IPT LPT HTR. 1 HTR. 2 BFP HTR. 3 HTR. 4 HTR. 5 HTR. 6 HTR. 7 HDP CP CONDENSER IV
- 16. Equivalent Loss in Output: ΔKw = (ΔS x TA)/3412.14163 where: ΔS = Entropy Flow, Btu/hr-°F TA = Absolute Sink Temp. = (79.04 + 459.69) = 538.73 °F Table 2 in Paper Shows Losses
- 17. (1) (3) (4) (5) Heat Transferred/Work Done, Btu/hr Equivalent Kw % of Shaft Output % of Total Heat Added 2,096,666,710 614,472 179.921 84.068 371,569,090 108,896 31.885 14.898 25,779,982 7,555 2.212 1.034 2,494,015,782 730,924 214.019 100.000 296,745,990 8,386 2.456 1.147 313,010,510 5,609 1.642 0.767 555,569,681 22,302 6.530 3.051 --------- 36,297 10.628 4.966 --------- 343,784 100.662 47.034 1,328,689,601 389,400 114.019 53.275 1,165,326,181 341,523 100.000 46.725 (2) A. Superheater B. Reheater Equiv. Entropy Change, Btu/hr/ºF 5. Turbine Loss A. HP Turbine 53,117 1. Boiler Output Total Heat Added in Boiler, BFP 4,629,428 C. LP Turbine 8. Turbine Power Output 2,163,095 7. Condenser Loss 2,466,333 141,251 6. Theoretical Cycle Loss 2,177,411 B. IP Turbine 3,891,863 689,712 35,523 Description 2. Boiler Feed Pump 47,853 Total Turbine Loss 229,891
- 18. (1) (3) (4) (5) Heat Transferred/Work Done, Btu/hr Equivalent Kw % of Shaft Output % of Total Heat Added 200,488,736 35,196 10.306 4.815 200,488,736 (33,394) (9.778) (4.569) --------- 1,802 0.528 0.247 102,259,191 19,394 5.679 2.653 102,259,191 (18,272) (5.350) (2.500) --------- 1,122 0.328 0.153 664,105,674 --------- 1,298 0.380 0.178 86,842,156 18,831 5.514 2.576 86,842,156 (17,904) (5.243) (2.450) --------- 926 0.271 0.127 86,746,678 20,178 5.908 2.761 86,746,678 (19,308) (5.653) (2.642) --------- 871 0.255 0.119 84,776,686 21,261 6.225 2.909 84,776,686 (20,387) (5.970) (2.789) --------- 874 0.256 0.120 93,241,518 25,793 7.552 3.529 88,143,676 (23,982) (7.022) (3.281) --------- 1,812 0.530 0.248 --------- 8,704 2.549 1.191 (2) 3. Feedwater Heaters Heat Transfer Loss A. Heater 1 Tube Side Equiv. Entropy Change, Btu/hr/ºF Tube Side 222,920 (211,508) 11,412 Shell Side Overall Heat Transfer Loss in Heater 1 B. Heater 2 122,834 (115,729) 7,105 Shell Side 8,219 Shell Side (113,401) Overall Heat Transfer Loss in Heater 2 C. Heater 3 (Deaerator) Overall Heat Transfer Loss in Heater 3 D. Heater 4 Tube Side 119,267 Shell Side (122,288) Overall Heat Transfer Loss in Heater 5 5,516 5,866 E. Heater 5 Tube Side 127,804 Overall Heat Transfer Loss in Heater 4 Shell Side (129,126) Overall Heat Transfer Loss in Heater 6 5,536 F. Heater 6 Tube Side 134,662 Shell Side (151,892) Overall Heat Transfer Loss in Heater 7 11,474 G. Heater 7 Tube Side 163,366 Total Heat Transfer Loss in Heaters 55,128 Description
- 19. (1) (3) (4) (5) Heat Transferred/Work Done,Btu/hr Equivalent Kw % of Shaft Output % ofTotal HeatAdded --------- 104 0.030 0.014 --------- 89 0.026 0.012 --------- 75 0.022 0.010 --------- 87 0.025 0.012 --------- 84 0.025 0.012 --------- 86 0.025 0.012 --------- 92 0.027 0.013 --------- 616 0.180 0.084 (2) Equiv.Entropy Change, Btu/hr/ºF TotalHeatersExt.PipingLoss 3,903 4.FeedwaterHeatersExt.PipingLoss A.Heater1Ext.PipingLoss 659 E.Heater5Ext.PipingLoss 532 B.Heater2Ext.PipingLoss 562 C.Heater3Ext.PipingLoss 472 549 Description F.Heater6Ext.PipingLoss 546 G.Heater7Ext.PipingLoss 583 D.Heater4Ext.PipingLoss
- 20. Quantification of Losses Using Entropy Balance Using Economic Data, Equipment Mods or Upgrades May be Prioritized Detailed Performance Modeling To Consider Additional Effects - Pressure Drops Within Heaters, Heat Losses From Piping, etc.