US3443550A - Two-section heat recovery steam generator - Google Patents

Two-section heat recovery steam generator Download PDF

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Publication number
US3443550A
US3443550A US636529A US3443550DA US3443550A US 3443550 A US3443550 A US 3443550A US 636529 A US636529 A US 636529A US 3443550D A US3443550D A US 3443550DA US 3443550 A US3443550 A US 3443550A
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United States
Prior art keywords
steam generator
evaporator
heat recovery
burner
steam
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Expired - Lifetime
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US636529A
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English (en)
Inventor
Howard F May
John M Kovacik
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General Electric Co
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General Electric Co
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Publication of US3443550A publication Critical patent/US3443550A/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1861—Waste heat boilers with supplementary firing

Definitions

  • the present invention is related to steam generators.
  • the invention is related to steam generators of the heat recovery type in which exhaust heat from an engine such as a gas turbine is used to generate steam.
  • Exhaust heat recovery steam generators are known to the art, and many schemes for the same have been proposed.
  • economy of operation implies improved efiiciency of the steam generator and economy of construction implies improved steam generation capacity for a given capital or hardware expenditure.
  • the heat recovery steam generator of the present invention is primarily directed at the latter economy, that is a relatively economic structure, as compared to the prior art, for a given steam generation capacity.
  • the gas which supplies heat to generate steam is generally passed once through the steam generator after exhausting from its first use and single firing. Exhausting at a temperature on the order of 300 F., the gas still contains more thermal energy than the ambient air. This gas also contains unused or excess air which would otherwise be available to combine with fuel for combustion.
  • Another object is to provide such a steam generator having an improved steam generation capacity for a given amount of heat exchange surface operating at a given maximum temperature.
  • Another object is to provide such a steam generator, operating between the same temperatures but providing a greater heat exchange from the exhaust gases to the water.
  • the present invention is practiced in one form by a heat recovery steam generator having an economizer, evaporator and super heater disposed in the path of gas turbine exhaust gases.
  • a burner is located upstream of the economizer, evaporator and superheater to add heat to the gases.
  • FIG. 1 is a schematic diagram of a fired exhaust heat recovery steam generator, known to the prior art
  • FIG. 2 is a schematic diagram of an unfired exhaust heat recovery generator, also known to the prior art
  • FIG. 3 is a more detailed schematic diagram of a fired exhaust heat recovery steam generator as in FIG. 1, and
  • FIG. 4 is a schematic diagram of a fired exhaust heat recovery steam generator according to thepresent invention.
  • FIG. 1 showing a fired exhaust heat recovery steam generator generally indicated at 2, an economizer 4, evaporator 6, superheater 8, and burner 10 are shown disposed within a conduit or stack 12 which is in turn disposed in the path of exhaust gases from a heat engine such as a gas turbine.
  • a drum 14 is located external to the steam generator stack 12 and is disposed to receive feedwater from the economizer 4 and in turn to discharge feedwater into the evaporator 6 by means of a pump 16.
  • the evaporator 6 receives water from drum 14 and returns water and steam thereto through a circuit.
  • the drum 14 also feeds steam to the tubes of superheater 8 from which steam is fed to its point of use.
  • the conduit 12 receives exhaust gases from a turbine and diffuser (not shown) and through a turning elbow 40 which directs the gases to turn from a generally horizontal flow direction to a generally vertical one.
  • a turbine and diffuser not shown
  • Such turning of the gas fiow results in pressure and flow disturbances or turbulence in the conduit immediately downstream of the turning elbow 40.
  • turning vanes 42 and screens 44 are included in the gas path to guide the gas flow to the burner 10 and to provide for a more uniformly flowing exhaust gas.
  • an economizer 4, evaporator 6, and superheater 8 are again shown disposed within a stack or conduit 12 in the path of gases exhausting from a gas turbine.
  • An external drum 14 and pump 16 are also included and serve the same purpose as in the fired steam generator mentioned above.
  • the unfired steam generator of FIG. 2 does not include a burner but simply uses the heat of the exhaust gas without further firing.
  • the capacity which is provided by the unfired steam generator arrangement of FIG. 2 is limited and can be increased either by raising the gas temperature or by increasing the quantity of hot gas.
  • the fired steam generator adds fuel to the unused or excess air of the exhaust gas and thereby adds to the quantity of heat in the gas for steam generation.
  • a fired heat recovery steam generator similar to that in FIG. 1 is shown, with the evaporator section 6 in greater detail.
  • a drum outlet line 18 leads from the drum 14 to the pump 16 which in turn discharges through pump discharge line '19 into an evaporator inlet header 20.
  • Evaporator inlet header 20 communicates with a plurality of 3 evaporator tubes 6 which are disposed in parallel and which in turn communicate with evaporator return header 22.
  • Return header 22 leads through return line 24 back into the drum 14.
  • evaporator tubes 6, headers and 22, lines 18, 19 and 24, and drum 14 constitute a circuit A.
  • gas turbine exhaust approaching the burner at approximately 900 F. is heated by means of the burner to approximately 1300 F. and is then passed over the superheater, the evaporator, and the economizer tubes, finally exhausting at a temperature of approximately 300 F., to generate a given amount of steam in the steam generator.
  • This provides a heat exchange corresponding to (1300-300) or 1000".
  • a heat recovery element or pre-evaporator 26 is disposed within the stack 12 upstream of the burner 10 and downstream of turning elbow 40.
  • Pre-evaporator 26 communicates with a pre-evaporator inlet header 28 and a pre-evaporator outlet header 30.
  • the pre-evaporator inlet header 28 is connected by an inlet line 32 to pump outlet line 19 on the discharge side of pump 16.
  • Preevaporator outlet header is connected by return line 34 to return line 24 immediately upstream of the drum 14. That is, evaporator tubes 26, headers 28 and 30, lines 18, 32 and 34, and drum r14 constitute a circuit B. Lines 32 and 34, headers 28 and 30, and evaporator tubes 26 of circuit B are connected in parallel with lines 19 and 24, headers 2'0 and 22 and evaporator tubes 6 of circuit A.
  • pre-evaporator 26 in FIG. 4 is essentially a number of the evaporator tubes 6 of FIG. 3 moved into a different position before the burner 10.
  • FIGURE 4 while presently preferred, is not the limit of our inventive concept.
  • the pre-evaporator 26 and its flow circuit B need not necessarily be connected with flow circuit A. If desired, a separate circuit B could be made to include a separate drum 14, pump 16, etc. In fact, there could be, upstream of burner 10, not only a pre-evaporator 26, but an economizer and a superheater. The net effect of such an arrangement would be to have an unfired exhaust heat recovery steam generator and a fired exhaust heat recovery steam generator in series (with respect to gas flow). This would provide a substantially increased steam generation capacity, but at a correspondingly increased hardware cost.
  • gas turbine exhaust in FIG. 4 at 900 upsteam of the pre-evaporator is cooled by the pre-evaporator to 600 R, which is its temperature approaching the burner 10.
  • the burner raises the temperature to 1300 which after passing over the superheater, evaporator tubes, and economizer reduces to 300 exhaust.
  • This provides a heat exchange corresponding to (900-600) and (1300-300) or 1300.
  • a single steam generator as in FIG. 1 or FIG. 2, provides a given steam output capacity for a given amount of steam generator hardware.
  • the optimized arrangement of this invention provides a substantially increased steam generation capacity without a corresponding increase in structure or capital cost.
  • An additional feature of the present invention is one of flexibility. All boilers should be fired at their maximum temperature, thus keeping at a minimum their required heat transfer surface. As applied to the present steam generator, any additional capacity of steam flow desired in addition to the basic capacity of the fired steam generator and over a range of from zero to about 40% thereof, can be met by controlling the size of the pre-evaporator. This gives the manufacturer more flexibility in that the same fired steam generator can be installed with various size pre-evaporators to provide different capacities for different requirements. The maximum firing temperature desired, as, for example, 1300", can thus be maintained over an output range of 40% since the basic fired steam generator is operating at full capacity, keeping the steam generator at its minimum possible size.
  • burner operation is improved because of improved gas flow.
  • the gas flow distribution to the burner is improved by the introduction of pressure drop in the gas turbine exhaust by the presence of the pre-evaporator.
  • the pre-evaporator thus serves as an incidental aid to the combustion process in the burner and obviates the screens 44 of FIG. *1.
  • a heat recovery steam generator including an economizer, an evaporator, and a superheater disposed in the path of hot gaseous products of combustion, and
  • a heat recovery element disposed in said path directly upstream of and adjacent said burner to absorb heat from said gaseous products, said heat recovery element defining a fluid flow path connected in parallel with at least part of the flow path through said economizer, evaporator and superheater.
  • a heat recovery steam generator as defined in claim 1 further including a drum located external to said path, said evaporator disposed in, and forming a part of, a circuit to receive fluid from and to return fluid to said drum,
  • said heat recovery element comprising a pre-evaporator disposed in and forming a part of a parallel circuit to receive fluid from and to return fluid to said drum.
  • a heat recovery steam generator as defined in claim 2 in which said evaporator includes a discharge header and a return header and a plurality of parallel evaporator tubes extending therebetween, and
  • said pre-evaporator similarly includes a discharge header and a return header and a plurality of parallel pre-evaporator tubes extending .therebetween.
  • a combined heat recovery steam generator including a fired steam generator and an unfired steam generator, said fired steam generator having a burner and disposed downstream of said unfired steam generator with respect to the flow relative thereto of hot gaseous combustion products, said unfired steam generator having heat recovery elements directly adjacent and in line with said burner to bathe the flow of gas thereto,
  • a heat recovery steam generator having a stack connected to a source of combustion-supporting waste heat gas and containing a plurality of substantially horizontal heat exchange tubes connected with pumping means to recircula'te fluid to and from an external steam drum, the improvement comprising:
  • a burner assembly disposed in the stack between the first and second groups and directly adjacent the second whereby the second group precools the gases before firing and distributes the fiow to the burner assembly.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Combustion & Propulsion (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Chemical & Material Sciences (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Air Supply (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
US636529A 1967-05-05 1967-05-05 Two-section heat recovery steam generator Expired - Lifetime US3443550A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US63652967A 1967-05-05 1967-05-05

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US3443550A true US3443550A (en) 1969-05-13

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US636529A Expired - Lifetime US3443550A (en) 1967-05-05 1967-05-05 Two-section heat recovery steam generator

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US (1) US3443550A (enrdf_load_stackoverflow)
JP (1) JPS4936881B1 (enrdf_load_stackoverflow)
BE (1) BE714632A (enrdf_load_stackoverflow)
CH (1) CH485172A (enrdf_load_stackoverflow)
DE (1) DE1751293A1 (enrdf_load_stackoverflow)
DK (1) DK123116B (enrdf_load_stackoverflow)
FR (1) FR1561015A (enrdf_load_stackoverflow)
GB (1) GB1200516A (enrdf_load_stackoverflow)
NL (1) NL6806195A (enrdf_load_stackoverflow)

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3561405A (en) * 1969-02-04 1971-02-09 Gen Electric Secondary fuel system for a supplementary fired heat recovery steam generator
US3581715A (en) * 1969-11-21 1971-06-01 Combustion Eng Method and apparatus for providing coke-oven gas as supplementary fuel for a steam generator organization
US3841270A (en) * 1972-11-01 1974-10-15 Westinghouse Electric Corp Flow restrictor for an evaporator
US3934553A (en) * 1975-01-06 1976-01-27 General Electric Company Combined wall burner and flameholder for HRSG
US3958922A (en) * 1974-09-20 1976-05-25 John Zink Company Duct burner assembly
US4145995A (en) * 1976-07-14 1979-03-27 Hitachi, Ltd. Method of operating a power plant and apparatus therefor
ES2133213A1 (es) * 1995-08-02 1999-09-01 Decos Impianti S P A Instalacion para el tratamiento de humos descargados de hornos para la produccion de fritas ceramicas.
US6092490A (en) * 1998-04-03 2000-07-25 Combustion Engineering, Inc. Heat recovery steam generator
WO2002053984A2 (en) 2000-12-29 2002-07-11 Nuovi Sistemi Termotecnici S.R.L. Condensation boiler
WO2002068801A1 (de) 2001-02-27 2002-09-06 Alstom (Switzerland) Ltd Verfahren zur nachrüstung eines dampfsystems
US6453852B1 (en) * 2000-05-22 2002-09-24 Corn Company, Inc. Temperature stratified superheater and duct burner
US20060249098A1 (en) * 2005-04-25 2006-11-09 Kvaerner Power Oy. Arrangement in recovery boiler
CN102734810A (zh) * 2011-04-12 2012-10-17 无锡市晨光耐火材料有限公司 一种co余热吸收锅炉
US20140090356A1 (en) * 2011-05-31 2014-04-03 Kabushiki Kaisha Toshiba Heat recovery steam generator and power plant

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5437090U (enrdf_load_stackoverflow) * 1977-08-19 1979-03-10
JPS5442489U (enrdf_load_stackoverflow) * 1977-08-31 1979-03-22
JPS6155501A (ja) * 1984-08-24 1986-03-20 株式会社日立製作所 排熱回収ボイラ
DE3842325C2 (de) * 1988-12-16 1999-10-07 Standard Kessel Ges Lentjes Fa Mehrzug-Abhitzekessel mit Zusatzfeuerung
US5762031A (en) * 1997-04-28 1998-06-09 Gurevich; Arkadiy M. Vertical drum-type boiler with enhanced circulation
DE102006009406A1 (de) * 2006-02-26 2007-09-06 Hutter, Friedrich, Dipl.-Ing. (FH) Verfahren zur Stabilisierung des Wasserumlaufs in einem Wasserrohr-Dampferzeuger mit Abkühleinrichtung für Gasturbinen-Prozeßgas bei einem kombinierten Gasturbinen-Dampfprozeß

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2547589A (en) * 1947-07-02 1951-04-03 Comb Eng Superheater Inc Apparatus for extracting heat from gases under pressure
AT186665B (de) * 1954-06-04 1956-09-10 Mak Maschinenbau Kiel Ag Heizanlage für die Fahrzeugräume von mit Brennkraftmaschinen angetriebenen Schienenfahrzeugen
US2926493A (en) * 1955-03-07 1960-03-01 Babcock & Wilcox Co Gas turbine with waste heat steam generator
US3314231A (en) * 1965-12-29 1967-04-18 Combustion Eng Steaming feedwater system utilizing gas turbine exhaust

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2547589A (en) * 1947-07-02 1951-04-03 Comb Eng Superheater Inc Apparatus for extracting heat from gases under pressure
AT186665B (de) * 1954-06-04 1956-09-10 Mak Maschinenbau Kiel Ag Heizanlage für die Fahrzeugräume von mit Brennkraftmaschinen angetriebenen Schienenfahrzeugen
US2926493A (en) * 1955-03-07 1960-03-01 Babcock & Wilcox Co Gas turbine with waste heat steam generator
US3314231A (en) * 1965-12-29 1967-04-18 Combustion Eng Steaming feedwater system utilizing gas turbine exhaust

Cited By (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3561405A (en) * 1969-02-04 1971-02-09 Gen Electric Secondary fuel system for a supplementary fired heat recovery steam generator
US3581715A (en) * 1969-11-21 1971-06-01 Combustion Eng Method and apparatus for providing coke-oven gas as supplementary fuel for a steam generator organization
US3841270A (en) * 1972-11-01 1974-10-15 Westinghouse Electric Corp Flow restrictor for an evaporator
US3958922A (en) * 1974-09-20 1976-05-25 John Zink Company Duct burner assembly
US3934553A (en) * 1975-01-06 1976-01-27 General Electric Company Combined wall burner and flameholder for HRSG
US4145995A (en) * 1976-07-14 1979-03-27 Hitachi, Ltd. Method of operating a power plant and apparatus therefor
ES2133213A1 (es) * 1995-08-02 1999-09-01 Decos Impianti S P A Instalacion para el tratamiento de humos descargados de hornos para la produccion de fritas ceramicas.
US6092490A (en) * 1998-04-03 2000-07-25 Combustion Engineering, Inc. Heat recovery steam generator
US6453852B1 (en) * 2000-05-22 2002-09-24 Corn Company, Inc. Temperature stratified superheater and duct burner
WO2002053984A2 (en) 2000-12-29 2002-07-11 Nuovi Sistemi Termotecnici S.R.L. Condensation boiler
WO2002068801A1 (de) 2001-02-27 2002-09-06 Alstom (Switzerland) Ltd Verfahren zur nachrüstung eines dampfsystems
US20060249098A1 (en) * 2005-04-25 2006-11-09 Kvaerner Power Oy. Arrangement in recovery boiler
US7434543B2 (en) * 2005-04-25 2008-10-14 Kvaerner Power Oy Arrangement in recovery boiler
CN102734810A (zh) * 2011-04-12 2012-10-17 无锡市晨光耐火材料有限公司 一种co余热吸收锅炉
US20140090356A1 (en) * 2011-05-31 2014-04-03 Kabushiki Kaisha Toshiba Heat recovery steam generator and power plant
US9416686B2 (en) * 2011-05-31 2016-08-16 Kabushiki Kaisha Toshiba Heat recovery steam generator and power plant

Also Published As

Publication number Publication date
JPS4936881B1 (enrdf_load_stackoverflow) 1974-10-04
DE1751293A1 (de) 1971-04-08
NL6806195A (enrdf_load_stackoverflow) 1968-11-06
BE714632A (enrdf_load_stackoverflow) 1968-09-30
GB1200516A (en) 1970-07-29
DK123116B (da) 1972-05-15
FR1561015A (enrdf_load_stackoverflow) 1969-03-21
CH485172A (de) 1970-01-31

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