US3756029A - Gas/steam turbine plant and a method of operating same - Google Patents

Gas/steam turbine plant and a method of operating same Download PDF

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Publication number
US3756029A
US3756029A US00168688A US3756029DA US3756029A US 3756029 A US3756029 A US 3756029A US 00168688 A US00168688 A US 00168688A US 3756029D A US3756029D A US 3756029DA US 3756029 A US3756029 A US 3756029A
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Prior art keywords
steam
turbine
gas
combustion chamber
steam turbine
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US00168688A
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English (en)
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E Aguet
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Sulzer AG
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Sulzer AG
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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
    • F01K21/00—Steam engine plants not otherwise provided for
    • F01K21/04—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas
    • F01K21/042—Steam engine plants not otherwise provided for using mixtures of steam and gas; Plants generating or heating steam by bringing water or steam into direct contact with hot gas pure steam being expanded in a motor somewhere in the plant
    • 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

Definitions

  • This invention relates to a gas/steam turbine plant and to a method of operating the same.
  • Plants of this type allow the building of a gas/steam turbine plant which is particularly suitable for producing peak current while combining high efficiency, ap-' proaching that of conventional steam power stations, with a much lower initial cost.
  • the present invention relates to a further development of the known plant and is intended to further increase the output and thermal efficiency of such a plant without enlarging the combustion chamber or the heating surfaces contained in this chamber.
  • the invention is intended to be suitable where clean fuels (that is, fuels with a lower content of impurities such as, for example, sulphur or vanadium) are used.
  • the method by which this end is achieved is characterized in that a second portion of the expanded steam is reheated in heating elements and then, performing work, is expanded in a second steam turbine to a condenser pressure below atmospheric pressure.
  • the plant is characterized by a second steam turbine which is connected in series with the first steam turbine and which is connected by its inlet to the outlet of the first steam turbine by way of a reheater heating surface and by its outlet to a condenser.
  • the plant includes a throttling means in one of the steam components in order to control the distribution of the steam volume between the combustion chamber and the second steam turbine.
  • the plant has a throttling member, e.g., a regulating valve in the line connecting the inlet of the second steam turbine to the outlet of the first steam turbine.
  • a throttling member e.g., a regulating valve in the line connecting the inlet of the second steam turbine to the outlet of the first steam turbine.
  • the operation of this throttling member is made to depend on the temperature of the gas/steam mixture at the inlet of the gas turbine so that throttling is increased when the temperature rises and vice-versa. This provides low-loss control economically by simple means.
  • a delivery line of an air compressor which leads to a burner in the combustion chamber is provided with a branch line which contains a throttling member and leads into a space between the heating elements and an outer pressure shell of the combustion chamber.
  • FIG. 1 diagrammatically illustrates an arrangement of a gas/steam turbine plant embodying the invention
  • FIG. 2 illustrates a cross-sectional view through the throttling member in the air compressor delivery line along line A-A in FIG. 1.
  • the gas/steam turbine plant includes an air compressor 1 which delivers compressed air 2 to a distributor 3, from which some of the air is fed along a line 6 to a burner 7, e.g., having an adjustable air outlet cross-section, at the bottom of a cumbustion chamber 8.
  • the combustion chamber 8 has side walls 9, consisting of tubes which are welded together in a fluid-tight manner, and an insulating floor 10.
  • the upper part of the combustion chamber 8 contains a superheater 11 in the path of the flue gases from the burner 7.
  • the combustion chamber 8 is enclosed in a pressure vessel, such as a pressure shell 12.
  • a sheet metal jacket 13 which is open at the top is positioned between the combustion chamber walls 9 and floor 10 and the inner surface of the vessel 12 to partially enclose the combustion chamber 8.
  • a flue gas line 20 is connected to the bottom of the jacket 13 and leads to the inlet of a gas/steam turbine 21, which shares a common shaft 23 with the compressor 1 and an electric generator 22.
  • the outlet of the gas/steam turbine 21 is connected by a line 30 to a heat exchanger 31 containing a reheater 32 and a feed water heater 33.
  • the heat exchanger 31 is connected by a line 34 to a stack (not shown) so that the cooled waste gas and the mixed-in steam can be exhausted.
  • the line 20 is also enclosed by an air line 40 which connects the distributor 3 to the interior of the pressure vessel 12.
  • a throttle valve 41 is provided inside the distributor 3 and is adjustable by means of a lever for purposes as described below.
  • the tubes in the combustion chamber walls 9 form an economiser and evaporator heating surfaces or elements, as is known, to which feed water is fed from a feed water tank by a feed pump 51.
  • the tubes forming these walls lead into a header 53 which is connected to the tubes in the superheater 11.
  • a live steam line 54 containing a live steam valve 55 connects the superheater 11 to a first steam turbine 56, which is a high pressure turbine.
  • the turbine 56 has two outlets.
  • the first outlet is connected by a line 60 to the distributor 3, which it enters downstream of the throttle valve 41.
  • the second steam outlet is connected to a line 61 with a regulating valve 62 leading to the reheater 32.
  • a line 65 extends to a second steam turbine 66 from the reheater 32 to direct the superheated steam thereto.
  • This steam turbine 66 which is a low pressure turbine has an outlet which feeds the steam to a condenser 67.
  • the condenser 67 connects over a condensate pump 68 which pumps the condensate through a bleeder steam economiser 69 to the feed water heater 33, which is heated by the waste gases from the gas/steam turbine 21.
  • the bleeder steam economiser 69 is heated with superheated steam drawn from the low pressure turbine 66 along a bleeder line 70.
  • a line connects the heater 33 into a deaerator 76 on top of the feed water tank so as to conduct the condensate flow thereto.
  • a pump 79 feeds make-up water to the deaerator 76 along a make-up water line 78, by way of a desalting plant 80.
  • the flue gas line is provided with a temperature sensor 82, the signal from which is fed along a signal line 83 to a controller 84.
  • This controller also, by way of a line 85, receives a desired-value signal which may, for example, depend on the type of fuel used.
  • the controller 84 serves to operate the regulating valve 62.
  • FIGS. 1 and 2 The plant illustrated in FIGS. 1 and 2 operates as follows:
  • the shaft 23 runs at a constant speed, so that the compressor 1 delivers a substantially constant volume of air regardless of the load on the plant.
  • Some of the air is fed along the line 6 to the burner 7, approximately in proportion to the load, whereas the remainder flows through the throttle valve 42 and line 40 into the pressure vessel 12 exteriorly of the heating elements, to gether with that portion of the steam expanded in the first turbine 56 which is fed along the line 60.
  • the volume rate of flow of this steam drops as the load decreases.
  • the steam/air mixture formed in the distributor 3 cools the surface of the pressure vessel 12 and then, at the upper end of this vessel 12, mixes with the combustion gases leaving the combustion chamber 8.
  • the mixture then flows down through the space left between the combustion chamber wall9 and the jacket 13 and flows through the pipe 20 to the gas/steam turbine 21.
  • the mixture then performs work in the turbine 21 before passing on into the heat exchanger 31 and tinally through the line 34 in the stack.
  • the temperature of the flue gases at the upper end of the combustion chamber 8 depends on the type of fuel. Fuels which burn with a roaring flame, for example, light oil and gas, radiate less heat so that less heat is transferred to the combustion chamber walls 9, less steam is produced and the discharge temperature of the flue gases is higher than if heavy oil is used. However, the plant is able to adapt to these conditions so as to burn light oil and gas as well as heavy oils which contain sulphur and vanadium.
  • the temperature at the inlet of the gas/steam turbine 21 may be relatively high, for example, 850 C.
  • the desired value 85 for the controller 84 is set at 850 C, with the result that the valve 62 allows a large quantity of steam to flow down, reducing the back pressure in the distributor 3.
  • the compressor 1, in accordance with its characteristic curve, supplies somewhat more air permitting more fuel to be burned in the combustion chamber 8. The output of the plant is therefore increased.
  • the proportion of air from the compressor 1 which is fed to the pressure vessel 12 progressively increases.
  • the lever 90 is adjusted by means of the plant load transmitter (not shown).
  • the volume of steam arriving through the line 60 decreases due to the temperature-maintaining effect of the controller 84.
  • the controller 84 is designed to reduce the flow cross-section at the valve 62 when the temperature-measuring device 82 detects a temperature rise at the inlet of the turbine 21, and vice-versa.
  • the proportion of steam used for cooling purposes changes so that the temperature at the inlet of the gas/steam turbine 21 is kept constant.
  • the re mainder of the steam is processed in the second steam turbine 66, i.e., the low pressure turbine.
  • the steam production in the combustion chamber walls 9 increases and the discharge temperature of the flue gases leaving the combustion chamber 8 drops.
  • the temperature at the gas turbine inlet must be lower than in the preceding case, for example, 600 to 650 C.
  • the volume of steam fed along the line 60 to the pressure vessel 12 is increased. This is done by suitably reducing the desiredvalue signal fed along the signal line to the controller 84 when heavy oil is used.
  • the steam turbine 66 and/or 56 may be completely separate from the gas turbine set and have their own electric generator.
  • a gas/steam turbine plant embodying the invention has the advantage of permitting, in return for a relatively small rise in initial cost, greater efficiency, particularly at partial load. Also, if clean fuel is used, the plant can have an output increase of up to 20% while still being equally suitable for poorer fuel.
  • the apparatus required in addition to the known installation includes the low pressure turbine 66 with the reheater 32, the condenser 67 and the condensate pump 68.
  • the desalting plant 80 can be smaller since some of the steam formed in the combustion chamber walls is recovered by the condenser 67.
  • a gas/steam turbine plant comprising a combustion chamber
  • a gas turbine connected to said combustion chamber to receive combustion gases therefrom and exhaust waste gas
  • heating elements within said combustion chamber for evaporating and superheating feed water to steam
  • a first steam turbine connected to said heating elements to receive steam therefrom and to expand the received steam
  • a second steam turbine connected to said first steam turbine to receive and expand a portion of the expanded steam therein while performing work
  • a temperature sensing means for sensing the temperature of the combustion gases delivered to said gas turbine said sensing means being connected to said regulating valve for adjusting said regulating valve to decrease the flow of steam therethrough in response to an increase in sensed temperature and vice versa.
  • a gas/steam plant as set forth in claim 1 further comprising a pressure shell enclosing said combustion chamber, a compressor, a burner in said combustion chamber, a delivery line between said compressor and burner for delivering compressed air into said burner, a branch line between said delivery line and said shell for delivering air between said shell and said combustion chamber, and a throttling member in said branch line for controlling the flow of air therethrough and wherein said second means is a line between said first steam turbine and said branch line for delivering steam into said branch line for entry into said shell.
  • a gas/steam turbine plant comprising a pressure vessel
  • a compressor connected with said combustion chamber for delivering air thereto and selectively connected to said pressure vessel for delivering air therein;
  • a gas turbine connected with said combustion chamber to receive combustion gases therefrom;
  • a first steam turbine connected to said heating elements to receive steam therefrom and to expand the received steam
  • a second steam turbine connected to said first steam turbine to receive and expand a portion of the expanded steam therein while performing work
  • second means between said steam turbines for controlling the portion of the expanded steam delivered to said second steam turbine in response to the temperature of thecombustion gases received in said gas turbine whereby the portion of expanded steam delivered to said second steam turbine decreases in response to an increase in said temperature while the portion of expanded steam delivered to said pressure vessel increans and vice versa.
  • a gas/steam turbine plant as set forth in claim 4 which further comprises a reheater between said steam turbines for receiving the expanded steam and a heat exchanger enclosing said reheater and connected to said gas turbine for receiving waste gas therefrom to heat the steam in said reheater.
  • a gas steam turbine plant comprising a pressure vessel having an inner surface
  • a jacket having an open end positioned between said combustion chamber and said pressure vessel inner surface to partially enclose said combustion chamber
  • a compressor connected with said combustion chamber for delivering air thereto and selectively connected to said pressure vessel for delivering air therein between said jacket and said pressure vessel inner surface to cool said surface;
  • a gas turbine connected with said combustion chamber to receive combustion gases therefrom;
  • heating elements within said combustion chamber for evaporating and superheating feed water to steam
  • a gas/steam turbine plant as set forth in claim 7 further comprising a branch line between said compressor and said pressure vessel for delivering air to said pressure vessel and a throttle valve in said branch line for controlling the amount of air delivered to said pressure vessel.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
US00168688A 1970-08-12 1971-08-03 Gas/steam turbine plant and a method of operating same Expired - Lifetime US3756029A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CH1208970A CH527360A (de) 1970-08-12 1970-08-12 Verfahren zum Betrieb einer Gas-Dampfturbinenanlage sowie Gas-Dampfturbinenanlage zur Ausübung des Verfahrens

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US3756029A true US3756029A (en) 1973-09-04

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US00168688A Expired - Lifetime US3756029A (en) 1970-08-12 1971-08-03 Gas/steam turbine plant and a method of operating same

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US (1) US3756029A (de)
JP (1) JPS4938224B1 (de)
BE (1) BE771186A (de)
CA (1) CA939157A (de)
CH (1) CH527360A (de)
DE (1) DE2065160A1 (de)
ES (1) ES393676A1 (de)
FR (1) FR2101936A5 (de)
GB (1) GB1300016A (de)
NL (1) NL147835B (de)
SE (1) SE369945B (de)

Cited By (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3832845A (en) * 1972-09-07 1974-09-03 Sulzer Ag Combined gas and steam powerplant with supplementary steam mixing
US3854283A (en) * 1973-10-25 1974-12-17 R Stirling Internal combustion steam generating system
US3913315A (en) * 1971-05-17 1975-10-21 Foster Wheeler Energy Corp Sulfur recovery from fluidized bed which heats gas in a closed circuit gas turbine
US4031404A (en) * 1974-08-08 1977-06-21 Westinghouse Electric Corporation Combined cycle electric power plant and a heat recovery steam generator having improved temperature control of the steam generated
US4409928A (en) * 1981-11-02 1983-10-18 The United States Of America As Represented By The Secretary Of The Navy Standardized compact modular boiler
US5042247A (en) * 1989-01-26 1991-08-27 General Electric Company Overspeed protection method for a gas turbine/steam turbine combined cycle
US5058373A (en) * 1989-01-26 1991-10-22 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US5069030A (en) * 1989-01-26 1991-12-03 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US5099643A (en) * 1989-01-26 1992-03-31 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
WO1992011446A1 (en) * 1990-12-18 1992-07-09 Mezhdunarodny Zapadno-Sibirsky Tsentr Ekologicheskikh I Medikobiologicheskikh Issledovany Thermal plant
US5199256A (en) * 1989-01-26 1993-04-06 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US20080047272A1 (en) * 2006-08-28 2008-02-28 Harry Schoell Heat regenerative mini-turbine generator
US20100139276A1 (en) * 2005-11-07 2010-06-10 Veritask Energy Systems, Inc. Method of Efficiency and Emissions Performance Improvement for the Simple Steam Cycle
US20140373539A1 (en) * 2011-09-15 2014-12-25 Guido U. Parisi Multifunction domestic station, device for powering the same with hydrogen and method of operating the same
EP2010820A4 (de) * 2006-03-30 2016-03-02 Steamex Group Sverige Ab Verfahren und vorrichtung zur herstellung eines dampf enthaltenden gasförmigen mediums
US10006626B2 (en) 2007-09-28 2018-06-26 Steamex Group Sverige Ab Method and device for producing a gaseous medium comprising steam
CN113638780A (zh) * 2021-07-08 2021-11-12 江西联达冶金有限公司 高温钢渣余热回收装置

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0826780B2 (ja) * 1993-02-26 1996-03-21 石川島播磨重工業株式会社 部分再生式二流体ガスタービン
US20100326083A1 (en) * 2009-06-26 2010-12-30 Robert Bland Spray system, power augmentation system for engine containing spray system and method of humidifying air

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3195306A (en) * 1962-12-17 1965-07-20 Combustion Eng Gas-steam power plant
US3325992A (en) * 1966-04-26 1967-06-20 Gen Electric Combined steam turbine gas turbine cycle
US3331202A (en) * 1965-02-15 1967-07-18 Sulzer Ag Steam power plant
US3335565A (en) * 1966-05-06 1967-08-15 Sulzer Ag Gas turbine and method of operating same
US3353360A (en) * 1966-02-18 1967-11-21 Foster Wheeler Corp Power plant with steam injection
US3359723A (en) * 1965-10-29 1967-12-26 Exxon Research Engineering Co Method of combusting a residual fuel utilizing a two-stage air injection technique and an intermediate steam injection step
US3561216A (en) * 1969-03-19 1971-02-09 Gen Electric Thermal stress controlled loading of steam turbine-generators

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3195306A (en) * 1962-12-17 1965-07-20 Combustion Eng Gas-steam power plant
US3331202A (en) * 1965-02-15 1967-07-18 Sulzer Ag Steam power plant
US3359723A (en) * 1965-10-29 1967-12-26 Exxon Research Engineering Co Method of combusting a residual fuel utilizing a two-stage air injection technique and an intermediate steam injection step
US3353360A (en) * 1966-02-18 1967-11-21 Foster Wheeler Corp Power plant with steam injection
US3325992A (en) * 1966-04-26 1967-06-20 Gen Electric Combined steam turbine gas turbine cycle
US3335565A (en) * 1966-05-06 1967-08-15 Sulzer Ag Gas turbine and method of operating same
US3561216A (en) * 1969-03-19 1971-02-09 Gen Electric Thermal stress controlled loading of steam turbine-generators

Cited By (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913315A (en) * 1971-05-17 1975-10-21 Foster Wheeler Energy Corp Sulfur recovery from fluidized bed which heats gas in a closed circuit gas turbine
US3832845A (en) * 1972-09-07 1974-09-03 Sulzer Ag Combined gas and steam powerplant with supplementary steam mixing
US3854283A (en) * 1973-10-25 1974-12-17 R Stirling Internal combustion steam generating system
US4031404A (en) * 1974-08-08 1977-06-21 Westinghouse Electric Corporation Combined cycle electric power plant and a heat recovery steam generator having improved temperature control of the steam generated
US4409928A (en) * 1981-11-02 1983-10-18 The United States Of America As Represented By The Secretary Of The Navy Standardized compact modular boiler
US5099643A (en) * 1989-01-26 1992-03-31 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US5058373A (en) * 1989-01-26 1991-10-22 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US5069030A (en) * 1989-01-26 1991-12-03 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
US5042247A (en) * 1989-01-26 1991-08-27 General Electric Company Overspeed protection method for a gas turbine/steam turbine combined cycle
US5199256A (en) * 1989-01-26 1993-04-06 General Electric Company Overspeed protection for a gas turbine/steam turbine combined cycle
WO1992011446A1 (en) * 1990-12-18 1992-07-09 Mezhdunarodny Zapadno-Sibirsky Tsentr Ekologicheskikh I Medikobiologicheskikh Issledovany Thermal plant
US20100139276A1 (en) * 2005-11-07 2010-06-10 Veritask Energy Systems, Inc. Method of Efficiency and Emissions Performance Improvement for the Simple Steam Cycle
US8453452B2 (en) * 2005-11-07 2013-06-04 Veritask Energy Systems, Inc. Method of efficiency and emissions performance improvement for the simple steam cycle
EP2010820A4 (de) * 2006-03-30 2016-03-02 Steamex Group Sverige Ab Verfahren und vorrichtung zur herstellung eines dampf enthaltenden gasförmigen mediums
US20080047272A1 (en) * 2006-08-28 2008-02-28 Harry Schoell Heat regenerative mini-turbine generator
US10006626B2 (en) 2007-09-28 2018-06-26 Steamex Group Sverige Ab Method and device for producing a gaseous medium comprising steam
US10775038B2 (en) 2007-09-28 2020-09-15 Steamex Group Sverige Ab Method and device for producing a gaseous medium comprising steam
US20140373539A1 (en) * 2011-09-15 2014-12-25 Guido U. Parisi Multifunction domestic station, device for powering the same with hydrogen and method of operating the same
CN113638780A (zh) * 2021-07-08 2021-11-12 江西联达冶金有限公司 高温钢渣余热回收装置

Also Published As

Publication number Publication date
NL7012872A (de) 1972-02-15
DE2041183A1 (de) 1972-02-17
CH527360A (de) 1972-08-31
BE771186A (fr) 1971-12-16
SE369945B (de) 1974-09-23
DE2041183B2 (de) 1972-12-07
DE2065160A1 (de) 1972-08-24
JPS4938224B1 (de) 1974-10-16
CA939157A (en) 1974-01-01
GB1300016A (en) 1972-12-20
ES393676A1 (es) 1973-08-16
FR2101936A5 (de) 1972-03-31
NL147835B (nl) 1975-11-17

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