US3769795A - Multipressure steam system for unfired combined cycle powerplant - Google Patents

Multipressure steam system for unfired combined cycle powerplant Download PDF

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US3769795A
US3769795A US00236916A US3769795DA US3769795A US 3769795 A US3769795 A US 3769795A US 00236916 A US00236916 A US 00236916A US 3769795D A US3769795D A US 3769795DA US 3769795 A US3769795 A US 3769795A
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feedwater
evaporator
pressure evaporator
steam
heat
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E Rostrom
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TURBO POWER AND MARINES SYST I
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TURBO POWER AND MARINES SYST I
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • F01K23/108—Regulating means specially adapted therefor
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Definitions

  • An exhaust heat recovery steam generator is utilized exclusively to develop shaft power to drive a load and includes a high pressure evaporator, low pressure evaporator and deaerator evaporator positioned in that order in the exhaust stack and has provisions for providing deaerated feedwater to each evaporator.
  • the deaerated feedwater is conducted through a split flow system to the low pressure and high pressure evaporator, and preferably also to the deaerator evaporator, to permit individual chemical treatment of the feedwater being provided exclusively to each evaporator so that deaerated and optimally chemically treated feedwater can be passed through each evaporator to abate corrosion and fouling therein.
  • the feedwater is passed through each evaporator at a temperature above the condensation point of the exhaust gas passing thereover. All'steam generated by the low pressure and high pressure evaporators is provided exclusively to a steam turbine to drive a shaftdriven load and the deaerator evaporator providing steam solely to heat and deaerate the feedwater.
  • the system is optimized in that the pressure levels for high and low pressure evaporators are optimized to produce the maximum practical steam turbine power from the energy in the gas turbine exhaust.
  • This invention relates to mechanism for generating steam at multiple pressures and more particularly to such a system wherein deaerated and optimally chemically treated feedwater is provided to the low pressure and high pressure evaporators so as to prevent corrosion therein and wherein fluid is passed through the evaporators at a temperature above the condensation point of the exhaust gas being passed thereover and wherein all the steam generated therein is conducted to a steam turbine which is mounted to drive a shaft driven load.
  • a low pressure deaerator evaporator or boiler is used in a downstream station of the exhaust stack to generate low pressure steam to deaerate the feedwater and the feedwater is then pumped by a boiler feedwater pump, positioned downstream of the deaerator, in a split flow path so that the boiler feedwater which is being'directed exclusively into the low pressure evaporator can be optimally chemically treated, as can the boiler feedwater which is being directed exclu sively into the high pressure evaporator.
  • allof the steam so generated is utilized in generating the shaft power to drive the load, and performs no auxiliary function except during start-up and very low load operation.
  • a primary object of the present. invention is to teach a waste heat steam generating system which can be used with a combined cycle gas turbine and steam turbine powerplant and which utilizes the energy of the steam so generated exclusively to generate shaft power for the powerplant.
  • FIG. 1 we see my multiple pressure generating steam system 10 used as part of a combined gas turbine-steam turbine cycle wherein the exhaust gases from gas turbine engine 12 are passed. through exhaust stack or duct 14 to provide the heat necessary to heat the feedwater being passed through exhaust heat recovery or stack boiler system 16 so as to generate the ,steam to drive steam turbine 18.
  • Steam turbine 18 is shaft connected to drive load 20, which could be an electric generator or other device.
  • Gas turbine engine l2 may be mechanically connected to steam turbine 18 through conventional connection 15 so that the turbines cooperate to drive load 20, but such is not necessary. While a gas turbine engine 12 is shown to provide the exhaust stackheat to the exhaust heat recovery boiler 16, it will be evident to those skilled in the art that other mechanisms could perform this function.
  • feedwater from condenser 22 is pumped by condensate pump 24 through conduit 26 into deaerator 28.
  • the initial feedwater which enters deaerator 28 is discharged from the deaerator through conduit 30 and then pumped by boiler feed pump 32 through conduit 34, which splits into conduits 36 and 38 so that the portion of thefeedwater from pump 32 which passes through conduit 36 enters deaerator evaporator or boiler 40 exclusively and in passing through the cross tubes 41 thereof, which extend across exhaust duct 14, generate low pressure saturated steam at a pressure whose saturated temperature is above the condensation (or dew point) of the exhaust gases which is extracted through line 42 and directed back into deaerator 28 so as to heat the feedwater entering the deaerator through line 26, thereby liberating all noncondensable gases and air in the feedwater for discharge to atmosphere.
  • deaerator 28 is of the fluid-tofluid type wherein the feedwater is sprayed through the steam entering deaerator 28 to form a saturated mixture at a temperature above the condensation temperature (or dew point) of the exhaust gases passing through the high pressure boiler. Accordingly, after systems start-up, deaerated feedwater is passed from the deaerator 28 to'the boiler feed pump 32 for distribution to the evaporators of exhaust heat recovery boiler 16. Deaeration is desirable so that the feedwater is of minimal corrosiveness to the metal of the boiler system through which it passes.
  • the pressure at the boiler feed pump 32 is the highest pressure in the boiler system and is sufficient to satisfy the pressure requirements of the high pressure evaporator.
  • Pump 32 provides deaerated feedwater to the entire system 16, including the deaerator just described.
  • the portion of the deaerated feedwater which passes through conduit 38 passes through low temperature economizer 44, which is of conventional design, so as to heat the feedwater before it leaves the low temperature economizer 44 through conduit 46.
  • the feedwater from conduit 46 splits into conduits 48 and 50. Approximately one-fourth to one-third of the feedwater passing through conduit 46 passes through conduit 48 and therefrom into low pressure evaporator 52 at a temperature above the condensation point of the exhaust gas passing over the cross tubes 53 of evaporator 52.
  • conduit 48 flows exclusively into low pressure evaporator 52 for evaporation therein and so that all steam is extracted therefrom through conduit 54 and directed to a low pressure station in steam turbine 18.
  • the ad vantage of having all of the feedwater passing through conduit 48 flow exclusively into the low pressure evaporator 52 is that precisely the proper chemical treatment can be madethereto by conventional treatment apparatus 57, to further reduce the harmful effect of the feedwater upon the boiler parts which it flows through.
  • Treatment mechanisms 37, 57 and 59 preferably inject the required chemicals directly into evaporator steam drums 45, 55 and 65, respectively, and are conventional.
  • conduit 50 Approximately two-thirds to three-fourths, depending on the gas temperature leaving the turbine exhaust, of the feedwater from conduit 46 then passes through conduit 50 at approximately the temperature to which it was raised in low temperature economizer 44 and is chemically treated in conduit 50, and preferably in boiler 65, by a conventional chemical treatment mechanism 59, similar to mechanism 56, and then flows as treated feedwater through the high temperature economizer 60 into the high pressure evaporator 62. It is important to note that all of the feedwater which flows through conduit 50 and the high temperature economizer 60 flows exclusively through conduit 61 into the high pressure evaporator 52 after being optimally treated chemically by chemical treatment mechanism 59.
  • High temperature economizer 60 raises the temperature of the feedwater and hence the evaporator cross tubes 63 above the condensation temperature of the stack gases passing thereover. All steam is extracted from the high pressure evaporator 62 through conduit 64 and is then passed through conventional superheater 66 and conduit 68 to a high pressure station 70 in steam turbine 18. It will therefore be seen that the superheated steam from high pressure evaporator 62 and the steam from low pressure evaporator 52 is admitted to steam turbine 18 at selected pressure stations in the steam turbine so that both work to power the steam turbine and generate shaft power exclusively therein to drive shaft driven load 20.
  • the superheated steam from conduit 68 expands and reduces in pressure in going through the high pressure portion 70 of turbine 18 and is of substantially the same pressure as is the steam entering turbine 18 from low pressure evaporator 52 via conduit 54 when the two join in mixing chamber or conduit 72 prior to passing through the low pressure portion 74 of the steam turbine 18.
  • the mixed steam After the mixed steam is expanded and reduced in pressure in passing through low pressure turbine portion 74, it passes through conduit 76 to conventional condenser 22 for recycling.
  • Economizers 44 and 60 serve to heat the feedwater passing therethrough so that the feedwater which passes therefrom into evaporators 52 and 62, respectively, is essentially at the saturation temperature of steam in steam drums for 52 and 62 thereby maximizing the amount of steam generated therein.
  • Pressure reducing valves 39 and 56 serve to regulate the pressure of the feedwater being passed through evaporators 40 and 52, respectively, as well as regulate flow to these systems.
  • Regulating valve 58 is a conventional feedwater regulating valve which regulates the flow to evaporator 62.
  • the low pressure evaporator 52 operates at about 150 psia and the deaerator evaporator 40 operates at about psia when the exhaust temperature is 850F.
  • the deaerator evaporator 40 operates at about psia when the exhaust temperature is 850F.
  • a substantial advantage to be gained by this three pressure system is the control which is available over operating temperatures of the steam and water in the heat exchanger system 16.
  • the operating temperatures of the feedwater or generated steam are sufficiently high that as the sulphur laden exhaust gases from turbine engine-12 passes through exhaust stack 14 and over the steam or water filled finned cross-over tubes of heat exchanger system 16, such as the tubes 63, 53 and 41 of the evaporator 62, 52 and 40, and the superheater 66, and economizers 60' and 44, the heated water passin'g'therethrough heats the tubes above the condensation or dew point of these sulphur particles and therefore the moisture does not deposit or condense upon the metallic surfaces of heat exchanger 16.
  • the condensed water would provide the mechanism for forming sulphuric acid which is highly corrosive so that the life of the entire system is adversely affected by deposit thereof on the metallic parts of boiler 16.
  • FIGS. 2 and 3 are a temperature energy diagram for the heat recovery boiler 16 and a temperature-entropy diagram for the steam cycle, re spectively.
  • Thecondensate is pumped to the deaerator 28 at station (I) by the condensate pump 24 at station (H).
  • the condensate mixes with saturated steam which passes from the deaerator evaporator 40 into deaerator 28 through conduit 42.
  • the steam evaporated in 'the high pressure evaporator 62 is superheated insuperheater 66 in passing from station (U) to (V).
  • the high pressure, superheated steam which we will call primary flow, enters the steam turbine 18 at the throttle inletat station (W). This flow expands to station (X) to a pressure approximately the same as the pressure in the low pressure boiler or evaporator 52.
  • the steam generated in the low pressure evaporator 52 which we will call secondary flow, passes out of the steam drum thereof at'station (R) and enters the steam turbine at the induction point (Y), where it mixes with the primary flow at station (Z).
  • My system 10 lends itself to use with other types of deaerators, for example the types shown in FIGS. 4 and 5.
  • the remainder of the system shown in FIG; 1 is applicable to the FIGS. 4 and 5 constructions and corresponding reference numerals will be used in describing the FIG. 4 and 5 constructions as were used for the FIG. 1 construction.
  • condensate from pump 24 passes throughconduit 26, including pressure regulating valve 39, into deaerator 28'.
  • Saturated steam from the deaerator evaporator 40 also passes through conduit 83 into deaerator 28' wherethe steam and feedwater mix in Iiquid-to-liquid fashion to deaer ate the feedwater.
  • the resulting mixture is saturated liquid at the deaerator pressure. All of the mixture flow passes down through connecting pipel80, the exit of whichis always submerged below the water level in the deaerator evaporator steam drum 43.
  • the feedwater required to supply the;high and .low pressure system shown in FIG. 1 passes through conduit 30 to the boiler feed pump32, from which it is pumped in the fashion shown in FIG.
  • FIG. 5 we see another deaerator embodiment which can be used with my system 10 otherwise depicted in FIG. 1.
  • the condensate from condensate pump 24 is pumped from conduit 26 into deaerator 28". There it mixes in fluidto-fluid'fashion with the saturated steam from thedeaerator evaporator 40 being passed into the deaerator 28" through conduit84.
  • the saturated mixture'from deaerator 28 passes through conduit 30 and splits so that a portion thereof recirculates back to the deaerator evaporator 40 through conduit 86, while the remainder thereof passes through conduit 88 to the boiler feed pump 32. It will be noted that in the FIG.
  • chemical treatment mechanism 90 is placed in conduit 86 or in the steam drum of deaerator evapo-- rator 40 so as to optimally treat the feedwater entering the deaerator evaporator 40, independently of the remainder of the feedwater system.
  • the feedwater, in both the FIG. 4 and FIG. 5 construction, will be treated independently at the low pressure evaporator steam drum and high pressure evaporator steam drum as shown in the FIG. 1 construction.
  • a combined gas turbine-steam turbine cycle powerplant wherein the exhaust gases of the gas turbine provide all of the heat to the steam boiler to generate steam for the steam burbine which is connected to drive a shaft driven load including:
  • steam generating means operatively associated with said exhaust stack including:
  • a low temperature economizer having tubes extending across said exhaust stack next downstream of said low pressure evaporator
  • a first flow path conduit system directing a first selected quantity of feedwater exclusively to the deaerator evaporator at a selected temperature so that the feedwater being passed through said deaerator evaporator is above the temperature of the condensation point of the exhaust gases passing over the deaerator evaporator,
  • a third flow path conduit system directing a third selected quantity of feedwater from said low temperature economizer exclusively through said high temperature economizer and said high pres- 5 sure evaporator such that the temperature of the feedwater passing through both is above the condensation point of the exhaust gases passing thereover,
  • E. means to extract steam from said high pressure evaporator and pass it through said superheater and conduct said superheated steam to a high pressure station in the steam turbine,
  • F. means to extract steam from said low pressure evaporator and direct it to a low pressure station in said steam turbine so as to cooperate with said superheated steam to power said steam turbine to drive said shaft driven load, and
  • G means to add selected quantities of water purifying chemicals to the selected quantity of feedwater introduced exclusively to the deaerator evaporator, to the selected quantity of feedwater being directed exclusively to the low pressure evaporator, and to the selected quantity of feedwater being directed exclusively to the high pressure evaporator, respectively.
  • a boiler feed pump positioned between said deaerator and said three feedwater flow path conduit systems so as to pump deaerated boiler feedwater therethrough.
  • a waste-heat stack positioned so that the waste- "heat passesfiier ethrough and having an inlet end and an outlet end,
  • V l. s team g eneratinggigans operatively associated with said waste -heat stack including:
  • a low temperature economizer having tubes extending across said waste-heat stack next downstream of said low pressure evaporator, and
  • a powerplant including means to deaerate the feedwater to be passed through ond selected quantity of feedwater exclusively through said low temperature economizer and then into said low pressure evaporator so that the temperature of the feedwater being passed through both is above the condensation point of the waste-heat gases being passed thereover, and -3.
  • a third flow path conduit system directing a third selected quantity of feedwaterfrom said low temperature economizer exclusively through said high temperature economizer and said high pressure evaporator such that the temperature of the feedwater passing through both is above the condensation point of the waste-heat gases passing thereover,
  • D. means to extract steam from said high pressure evaporator and pass it through said superheater and conduct said superheated steam to a high pressure station in the steam turbine
  • E. means to extract steam fromsaid low pressure evaporator and direct it-to a low pressure station in said steam turbine so as to cooperate with said superheated steam to power said steam turbine to drive said shaft driven load, and
  • F. means to add selected quantities of water purifying chemicals to the selected quantity of feedwater introduced exclusively to the deaerator evaporator, to the selected quantity of feedwater being directed exclusively to the low pressureevaporator, and to the selected quantity of feedwater being directed exclusively to the high pressure evaporator, respectively.
  • a multipressure steam generating powerplant including a heat recovery boiler having:
  • B a high pressure evaporator having tubes in said 'hastaiaarrs ussirsamsrsion, 3 C. a low pressure evaporator having tubes insaid heat duct at a downstreamstation, D; first feedwaterconduit means connected to provide a selected quantity of feedwater exclusively to said low pressure evaporator and including:
  • a second feedwater conduit means connected to provide a selected quantity of feedwater exclusively to the high pressure evaporator and including:
  • F. means to extract steam from both said low pressure evaporator and said high pressure evaporator.
  • a powerplant according to claim 5 wherein said feedwater deaeration means includes:
  • said feedwater deaerator includes a fluid-to-fluid deaerator positioned externally of the heat stack and a deaerator evaporator having tubes in said heat stack at, a station downstream of said low pressure 'evaporator'and conduit means connecting said deaerator and said deaerator evaporator so that the low pressure steam generated in said deaerator evaporator is directed to said deaerator so as to heat the feedwater entering the deaerator to deaerate the feedwater and so that the saturated mixture of feedwater and steam accumulated in said deaerator after said mixing will be passed in part to said deaerator evaporator, in part to said low pressure evaporator and in part to said high pressure evaporator.
  • a gas turbine-steam turbine unt'n'ed, combined cycle powerplant wherein the exhaust gases of the gas turbine provide all of the heat'to the steam boiler to generate steam for the steam turbine which is connected to drive a shaft driven 'load including:
  • a low temperature economizer having tubes extending across said exhaust stack next downstream of said low pressure evaporator
  • G. means to pass deaerated feedwater from said boiler feed pump through said steam generating means and to said steam turbine including three feedwater flow path conduit systems including:
  • a second flow pathconduit system directing a second selected quantity of deaerated feedwater exclusively to the low pressure evaporator including:
  • a third flow path conduit system directing a third selected quantity of deaerated feedwater from said boiler feed pump exclusively to said high pressure evaporator and including:
  • H. means to add selected quantities of water purifying chemicals to the selected quantity of feedwater being so introduced exclusively to the deaerator evaporator, to the selected quantity of feedwater being directed exclusively to the low pressure evaporator, and to the selected quantity of feedwater being directed exclusively to the high pressure evaporator, respectively.
  • a powerplant according to claim 9 wherein said third system splits from said second system so that about one-fourth to one-third of the deaerated feedwater enters said low pressure evaporator and about three-fourths to two-thirds of the deaerated feedwater enters said high pressure evaporator.
  • An unfired, waste-heat-steam turbine combined cycle powerplant wherein waste-heat provides all of the heat to the steam boiler to generate steam for the steam turbine which is connected to drive a shaft driven load including:
  • steam generating means operatively associated withsaid waste-heat stack including:
  • F. means to pass deaerated feedwater from said boiler feed pump through said steam generating means and to said steam turbine including three feedwater flow path conduit systems including:
  • a first flow path conduit system directing a first selected quantity of deaerated feedwater exclusively to the deaerator evaporator from said boiler feed pump including: i a. a first conduit connecting said boiler feed pump to said deaerator evaporator,
  • a second flow path conduit system directing a second selected quantity of deaerated feedwater exclusively to the low pressure evaporator including: g ⁇
  • a third flow path conduit system directing a third selected. quantity of deaerated feedwater from said boiler feed pump exclusively to said high pressure evaporator and including:
  • a fifth conduit connecting said superheater to said steam turbine so that the steam generated in said high pressure evaporator is passed through said fourth conduit to be superheated in passing through said superheater and then directed through said fifth conduit to said steam turbine so that all of the steam generated in this multipressure system is utilized to generate shaft energy in said steam turbine to drive a shaft driven load, a means to a s. 99t.q 91. i%at fitatsrr r r r ing chemicals to the selected quantity of feedwater being directed exclusively to the deaerator evaporator, to the selected quantity of feedwater being directed exclusively to the low pressure evaporator, and to the selected quantity of feedwater being directed exclusively to the high pressure evaporator, respectively.
  • multipressure steam generating powerplant in cluding a heat recovery boiler having:
  • E. means to direct a first quantity of deaerated feedwater exclusively to said low pressure evaporator
  • F. means to direct a second quantity of deaerated feedwater exclusively to said intermediate pressure evaporator
  • G. means to direct a third quantity of deaerated feedwater exclusively to said high pressure evaporator
  • i H. means to optimally chemically treat said deaerated feedwater exclusively entering each of said low, intermediate, and high pressure evaporators.
  • a multipressure steam generating powerplant including a heat recovery boiler having:
  • E. means todirect a total quantity of deaerated feedwater so that a first portionthereof flows exclusively to said low pressure evaporator, so that a second portion thereof flows exclusively to said inter .mediate pressure evaporator, and so that the remainder thereof flows exclusively to said high pressure evaporator, and
  • F. means to optimally chemically treat the deaerated feedwater being conducted exclusively into each of said low, intermediate, and high pressure evaporatOI'S.

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US00236916A 1972-03-22 1972-03-22 Multipressure steam system for unfired combined cycle powerplant Expired - Lifetime US3769795A (en)

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JP (1) JPS496302A (2)
AU (1) AU462586B2 (2)
CA (1) CA980138A (2)
DE (1) DE2311066A1 (2)
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FR2394751A1 (fr) * 1977-06-16 1979-01-12 Bbc Brown Boveri & Cie Rechauffeur a melange pour l'eau d'alimentation avec systeme regulateur
US4501233A (en) * 1982-04-24 1985-02-26 Babcock-Hitachi Kabushiki Kaisha Heat recovery steam generator
US4627386A (en) * 1983-04-08 1986-12-09 Solar Turbines, Inc. Steam generators and combined cycle power plants employing the same
US4685426A (en) * 1986-05-05 1987-08-11 The Babcock & Wilcox Company Modular exhaust gas steam generator with common boiler casing
US4858562A (en) * 1987-05-06 1989-08-22 Hitachi, Ltd. Reheat type waste heat recovery boiler and power generation plant
US4896496A (en) * 1988-07-25 1990-01-30 Stone & Webster Engineering Corp. Single pressure steam bottoming cycle for gas turbines combined cycle
EP0359735A1 (de) * 1988-09-14 1990-03-21 AUSTRIAN ENERGY & ENVIRONMENT SGP/WAAGNER-BIRO GmbH Abhitze-Dampferzeuger
EP0410111A1 (de) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Abhitzedampferzeuger für ein Gas- und Dampfturbinenkraftwerk
US5189873A (en) * 1990-09-12 1993-03-02 Hitachi, Ltd. Combined cycle power plant with water treatment
US5375410A (en) * 1993-01-25 1994-12-27 Westinghouse Electric Corp. Combined combustion and steam turbine power plant
US5442921A (en) * 1993-02-22 1995-08-22 Epri Targeted fluid delivery system
US6343570B1 (en) * 1997-08-25 2002-02-05 Siemens Aktiengesellschaft Steam generator, in particular waste-heat steam generator, and method for operating the steam generator
US6957540B1 (en) * 2004-04-28 2005-10-25 Siemens Westinghouse Power Corporation Multi-mode complex cycle power plant
WO2006048505A1 (en) * 2004-11-03 2006-05-11 Wärtsilä Finland Oy Method and system for heat recovery
US20080115922A1 (en) * 2006-11-15 2008-05-22 Jon Horek Heat recovery system and method
US20090199558A1 (en) * 2008-02-11 2009-08-13 General Electric Company Exhaust stacks and power generation systems for increasing gas turbine power output
US20110203289A1 (en) * 2007-01-04 2011-08-25 Gutierrez Juan P Power generation system incorporating multiple rankine cycles
US20120037097A1 (en) * 2007-03-22 2012-02-16 Nooter/Eriksen, Inc. High efficiency feedwater heater
US20140216365A1 (en) * 2013-02-05 2014-08-07 General Electric Company System and method for heat recovery steam generators
US20150000276A1 (en) * 2012-01-19 2015-01-01 Siemens Aktiengesellschaft Auxiliary steam generator system for a power plant
US20150211731A1 (en) * 2014-01-27 2015-07-30 Ellis Young Processed vapor make-up process and system
US9739478B2 (en) 2013-02-05 2017-08-22 General Electric Company System and method for heat recovery steam generators

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JPS53123701A (en) * 1977-04-05 1978-10-28 Mitsubishi Heavy Ind Ltd Exhaust gas heat recovering apparatus of marine prime mover
EP0147407B1 (en) * 1983-05-23 1988-06-01 Solar Turbines Incorporated Steam generator control systems
DE3408937A1 (de) * 1984-01-31 1985-08-08 BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau Kombinierte gas-/dampf-kraftwerkanlage

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EP0359735A1 (de) * 1988-09-14 1990-03-21 AUSTRIAN ENERGY & ENVIRONMENT SGP/WAAGNER-BIRO GmbH Abhitze-Dampferzeuger
EP0410111A1 (de) * 1989-07-27 1991-01-30 Siemens Aktiengesellschaft Abhitzedampferzeuger für ein Gas- und Dampfturbinenkraftwerk
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US8495859B2 (en) 2006-11-15 2013-07-30 Modine Manufacturing Company Heat recovery system and method
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US9581328B2 (en) * 2007-03-22 2017-02-28 Nooter/Eriksen, Inc. High efficiency feedwater heater
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US7707818B2 (en) 2008-02-11 2010-05-04 General Electric Company Exhaust stacks and power generation systems for increasing gas turbine power output
US20090199558A1 (en) * 2008-02-11 2009-08-13 General Electric Company Exhaust stacks and power generation systems for increasing gas turbine power output
US20150000276A1 (en) * 2012-01-19 2015-01-01 Siemens Aktiengesellschaft Auxiliary steam generator system for a power plant
US9494054B2 (en) * 2012-01-19 2016-11-15 Siemens Aktiengesellschaft Auxiliary steam generator system for a power plant
US20140216365A1 (en) * 2013-02-05 2014-08-07 General Electric Company System and method for heat recovery steam generators
US9097418B2 (en) * 2013-02-05 2015-08-04 General Electric Company System and method for heat recovery steam generators
US9739478B2 (en) 2013-02-05 2017-08-22 General Electric Company System and method for heat recovery steam generators
US20150211731A1 (en) * 2014-01-27 2015-07-30 Ellis Young Processed vapor make-up process and system
US9791146B2 (en) * 2014-01-27 2017-10-17 Ellis Young Processed vapor make-up process and system

Also Published As

Publication number Publication date
CA980138A (en) 1975-12-23
JPS496302A (2) 1974-01-21
DE2311066A1 (de) 1973-10-04
AU462586B2 (en) 1975-06-26
SE386501B (sv) 1976-08-09
AU5271373A (en) 1974-08-29
IL41670A (en) 1975-08-31
IL41670A0 (en) 1973-05-31

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