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148 PROCEEDINGS OF THE TWENTY-FIRST TURBOMACHINERY SYMPOSIUM 65 60 55 � 500 �- Figure 31. Relationship between Combustor Temperature and Compressor Delivery Temperature with Steam Injection. Thus, it may be concluded that; changes in exhaust and combus tor temperature profiles measured as steam was injected, were caused by steam mixing within different combustion zones, and the resulting changes in temperature profiles within the liners must have been large to cause the detected temperature changes. To see if the large changes in combustion patterns affected engine performance, the performance program described earlier in the paper was utilized. Three March 13, 1991, runs without steam injection were matched, then using that model, performance with out, and with steam injection was predicted by duplicating measured: • ambient temperature • barometric pressure • compressor turbine speed, and • exhaust temperature, with power turbine speed matched to the March 13 th power turbine load vs speed curve. Inherent in the prediction method was the assumption that altered (by steam) combustion patterns did not affect: • combustion efficiency (held at 100 percent), • compressor turbine swallowing capacity or efficiency, • power turbine swallowing capacity or efficiency, • inter-turbine or exhaust diffuser recoveries. Measured to predicted changes are compared in Figures 32 and 33 in the primary indicators of turbine performance, as steam was injected. The increase in power was greater than predicted for all quantities of injected steam, fuel consumption generally increased less than expected, compressor delivery pressure was close to expected, and the power turbine vane closed a little more than predicted. In general, the MS 3002 B gas turbine responded to steam injection somewhat better than predicted. The precise cause of this improved performance could not be deduced from the available data. It is postulated that the improvement was either due to the axial compressor's efficiency being greater than assumed at the higher pressure ratios accompanying steam injection, or due to the compressor turbine's efficiency increasing with the different com bustor outlet patterns accompanying steam injection. Finally, increased exhaust temperature spread caused by injec tion of steam into the secondary and primary combustion regions (at overall SFRs up to 5.3:1) did not degrade the combustor or hot end performance. OPERATING GUIDELINES The steam injection system is available for operation on an "as needed basis" for peaking service. The pipeline operating condi tions are evaluated by the gas control dispatcher to determine if :> !'" u- � ------- WITH:THERMOCOUPLES RETRACTED OMEASUREMENT AT WITH 100% STEAM MIXING WITH 100% AXIAL DISTANCE FIIOM INJECTION STEAM HOLES IN LINER CASING IINCHESJ 10 15 20 0: ::;; ,_w > a:w �w 0 a: 70 f/)0 f/)wa:.. 0::; u 0w # DILUTION AIR IFOSTEAM L_ PRIMARY _j SECONDARY LINERAlR INJ£CTIONHOLES DILUTION (OF JET COMBUSTOR lliERMOCOUPlE 0: ::;; 0 �a: 0Iii :> "' ::;; 8w" �w 5 10 STEAM INJECTION 11,000 PPH) Figure 29. Jet Penetrating into a Crossflow. centerline trajectories were calculated using Equation 7 from Abuaf, et a!. [18], for increasing quantities of steam injection, and the results plotted along with combustion liner air flow, in Figure 30. 1 5 20 2 5 y -HORSESHOE VORTEX A'/ CROS8-FLOW VORTEX Figure 30. Steam Injection Jets Penetrating Liner Supply Air. At 5000 pph steam, the calculated centerline trajectory falls entirely within dilution air. However, at 10,000 pph steam, the jet centerline intersects the boundary between secondary and dilution air about four inches downstream of the injection holes in the liner casing. At 15,000 pph, injection steam jets penetrate entirely through dilution air into secondary air. To test this sequence, the temperature rise due to mixing 100 percent injection steam with 100 percent dilution air was calcu latedandplottedinFigure31.Itwasimmediatelyobviousthatthe sequence of events is true, namely: • from 0 to 11,600 pph, all the steam mixes with dilution air, • from 11,600 pph to 14,000 pph, progressively more of the injected steam penetrates into secondary air, leaving less steam to mix with dilution air, and • beyond 14,000 pph steam, all of the steam has penetrated through dilution air into secondary and primary air. ' 75 ---------PDF Image | STEAM INJECTION SYSTEM ON AN EARLY FRAME 3 GAS TURBINE IN A COMBINED CYCLE PIPELINE COMPRESSOR STATION
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