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DESIGN, INSTALLATION, AND TEST OF A STEAM INJECTION SYSTEM ON AN EARLY FRAME 3 GAS TURBINE IN A COMBINED CYCLE PIPELINE COMPRESSOR STATION 143 of steam into the annulus around the liner, to ensure that the 36 steam jets did not impinge on the liner wall, and to ensure that maximum design steam rate of 30,000 pph would not be exceeded, a flow analysis through the liner casing steam manifold system (Figure 13) was conducted. iii ,04 ... �w.. CROSS-OVER PIPE STEAM INLET NOZZLE BLOCK 283° MANIFOLD Figure 13. Steam Supply Model. z iii <( :I:":: .02 a:0 ..:I: Qz t; .01 ..w � :;; The effect of approach velocity and wall thickness on discharge coefficients was included using the method suggested by McGree ham [17]. Maximum steam jet penetration into compressor deliv ery air flowing through the annulus between the liner casing and the liner was calculated using the experimentalmodification found by Abuaf, et a!., to Lefebvre's proposed expression [18]. This maximum penetration was at a distance of three diameters down stream of the hole. With an injection hole diameter of 13/64 in, maximum penetration was held to 0.96 in at maximum stream flow of 30,000 pph. The variation in mass flow through the 18 holes equispaced around the circumference of the liner casing was limited to± 6.0 percent, as shown in Figure 14. To minimize steam velocity through the lined flexible hoses, the orifices supplying the six and 30 hole manifolds were sized to pass a total of 30,000 pph steam with the steam throttle valve 100 percent open. This results in a pressure in the flexes of about 425 psia, and a pressure drop across the supply orifices of 300 psi. The large restriction in each liner manifold forces equal flow to each liner.Therefore, steam supply system design ensured that equal steam would flow to each liner, and would be uniformly distrib uted around each liner. Injection steam was taken from a nearby three inch starting turbine supply line and routed to the turbine, as shown in Figure 15. In addition to the requirement for steam flow measurement and Figure 15.lnjection Steam Supply System. Average combustor exit temperature for the MS 3002 turbine was 1450°F; therefore, it was decided to add an adjustable moni toring thermocouple in the downstream end of each liner, as shown in Figure 16, to see if changes in combustion characteristics could be detected as increasing quantities of steam were injected. TEST RESULTS Steam was injected into Unit 5 on November 27, 1990 in gradually increasing quantities (up to 13,000 pph), and all avail able engine data were recorded. Turbine output increased approx imately as expected as the quantity of injection steam was increased, while exhaust temperature spread jumped about 50°F, once more than 10,000 pph of steam was injected (Figure 17). Exhaust spread without steam injection was l20°F which is somewhat higher than normal. Therefore, increase in the spread to 170°F was worrisome. To gain additional information, the new combustor thermocou ples were wired in, adjusted to their maximum penetration of 3.5 in inside the liner (Figure 16a), and at base load without steam injection, a surprisingly high 900°F temperature spread was mea sured, as shown in Figure 18. A photograph of a MS 3002 liner (Figure 19a), shows the placement of primary, secondary, and the four, 2ljg in diam. dilution air holes. The combustor thermocouple was located 13 in LINER CASING COMBUSTION LINER Figure 14. Mass Flow Variation Through Steam Injection Holes. control, protection against water injection was provided by includ ing a "knockout" drum and steam trap. The "knockout" drum, designed as a cyclone separator, removes water droplets and particulates from the vapor, and provides an accumulator volume for upset conditions. 0:I: w ".. .03 <(w !;; INJECTION STEAM (1,000 PPH)PDF Image | STEAM INJECTION SYSTEM ON AN EARLY FRAME 3 GAS TURBINE IN A COMBINED CYCLE PIPELINE COMPRESSOR STATION
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