EP0334935B1 - Gas-dampf-kraftanlage - Google Patents

Gas-dampf-kraftanlage Download PDF

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Publication number
EP0334935B1
EP0334935B1 EP88908952A EP88908952A EP0334935B1 EP 0334935 B1 EP0334935 B1 EP 0334935B1 EP 88908952 A EP88908952 A EP 88908952A EP 88908952 A EP88908952 A EP 88908952A EP 0334935 B1 EP0334935 B1 EP 0334935B1
Authority
EP
European Patent Office
Prior art keywords
steam
gas
combustion chamber
turbine
power plant
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP88908952A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0334935A1 (de
Inventor
Raimund Croonenbrock
Reinhold Ulrich Pitt
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Hitachi Zosen Inova Steinmueller GmbH
Original Assignee
L&C Steinmueller GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by L&C Steinmueller GmbH filed Critical L&C Steinmueller GmbH
Priority to AT88908952T priority Critical patent/ATE84600T1/de
Publication of EP0334935A1 publication Critical patent/EP0334935A1/de
Application granted granted Critical
Publication of EP0334935B1 publication Critical patent/EP0334935B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F01K23/061—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 combustion in a fluidised bed
    • F01K23/062—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 combustion in a fluidised bed the combustion bed being pressurised

Definitions

  • the invention relates to a gas-steam power plant of the type mentioned in the preamble of claim 1.
  • Such a gas-steam power plant is known from FR-E-92 028 and FR-A-1 496 420, in which the majority of the steam generated in the plant, together with the fuel gases, is discharged to the environment; only a small part of the steam released in the turbine is mixed with the water to preheat the feed water.
  • the steam of the steam turbine which is designed without a condensing device, is added to the combustion chamber at a point where, after mixing, the combustion gas and steam have a common temperature of approx. 600 ° C, while the temperature of the combustion gas in front of the mixing point is 1300 ° C.
  • the steam partially expanded in the gas turbine is therefore not heated to the highest possible temperature in the combustion chamber.
  • GB-A-2 087 252 discloses a pressure fluidized bed with a stationary fluidized bed in a gas-steam power plant, in which steam or water is introduced into the fluidized bed to regulate the temperature of the fluidized bed.
  • the steam turbine of the gas-steam power plant is provided with a condensation device and the condensed water is evaporated again.
  • gas-steam power plants with high-pressure steam generators can be equipped with a pressure-charged fluidized bed furnace, with a compressed coal dust furnace, compressed oil or compressed gas furnace.
  • the aim is always to improve the efficiency of gas-steam power plants.
  • This object is achieved in that the steam removed from a condensation steam turbine is input into the combustion chamber at a near-stoichiometric combustion air ratio in the range from 1 to 1.5 of the fuel and is heated there to the highest possible temperature in the combustion chamber.
  • the steam generated in the plant is returned to the combustion chamber as so-called bleed steam, but is heated there to the highest possible temperature in the combustion chamber in order to serve as a working medium for the gas turbine.
  • the steam is heated to a temperature which is substantially above the currently highest possible temperature in the water-steam cycle, which can be 530 ° C, for example.
  • steam is injected into a combustion chamber to which at least one heating surface is assigned, it can be achieved by appropriate design of the size of the heating surface or heating surfaces that the amount of heat transferred to the high-pressure steam is reduced by just as much as the overheating of the directly into the Combustion steam input to the exhaust gas temperature, d. H. the gas turbine fuel gas temperature is to be used.
  • the heating surface can be adapted in a particularly simple manner by adjusting the height of the fluidized bed.
  • the combustion takes place unchanged at the same Near stoichiometric combustion air ratio.
  • the propellant gas mass flow is therefore only increased by the injection steam mass flow, but not by an additional combustion gas flow.
  • the exhaust gas loss after utilizing the energy available in the exhaust gas of the gas turbine is therefore smaller than in the known process.
  • the heating surface can preferably be designed as a wall and / or as a heating surface which is arranged in the combustion chamber.
  • the firebox is designed as a pressure fluidized bed combustion with a stationary fluidized bed.
  • the gas turbine in a manner known per se from DE-OS 35 36 451 has a heat exchanger for heat exchange with the combustion air and / or a heat exchanger for the water-steam cycle and this one Another gas turbine is connected downstream, in which the combustion gas is expanded while performing work.
  • This second turbine is, in turn, preferred and known per se, part of a turbocharger for the combustion air.
  • the steam introduced into the combustion chamber serves at least partially as motive steam for injecting the fuel into the pressure fluidized bed.
  • the steam to be supplied and removed from the turbine is fed to the combustion chamber in at least two pressure stages, z. B. at a turbine system with an intermediate superheater line pressure stage required for intermediate superheating can be taken from the intermediate superheater line, while the lower pressure stage can be taken from a turbine charged with the ZÜ steam.
  • FIG. 1 schematically shows a high pressure steam generator (1), the combustion chamber of which is designed as a pressure-charged fluidized bed (2).
  • the fluidized bed is supplied as coal (K) and for desulfurization CaCO3.
  • a heating surface (3) is assigned to the firebox (2) (it is clear that several heating surfaces in the form of wall heating surfaces and heating surfaces arranged inside the firebox can be provided).
  • the high-pressure steam leaving the heating surface (3) is fed via a line (4) to a steam turbine (5), in which it is expanded to perform work.
  • the steam turbine (5) drives a generator (6).
  • the steam emerging from the steam turbine (5) is condensed in a condenser (7) and by means of pumps (8) and (9) and a feed water tank (10) located between these pumps via a line (11) to the high-pressure steam generator (1) forwarded.
  • Compressed combustion air (L) is fed to the pressure fluidized bed (2) by means of a compressor (12).
  • the combustion exhaust gases from the combustion chamber (2) are fed via a filter (13) to a gas turbine (14) which expands the combustion exhaust gas and from there via a heat exchanger (15) switched on in the line (11) to a chimney (not shown).
  • bleed steam from the turbine (5) is introduced directly into the combustion chamber (2) of the high-pressure steam generator (1).
  • the steam is heated to the highest possible temperature in the firing chamber and, together with the combustion exhaust gas, relaxes in the turbine (14) which drives the compressor (12) and, if appropriate, an additional generator (18).
  • the steam is the turbine (5) z. B. with a temperature of the order of 530 ° C and a pressure of 37 bar.
  • the bleed steam introduced into the combustion chamber via the line (16) can be heated to a temperature of 850 ° C. in the case of a pressure fluidized bed and can be expanded in the gas turbine (14), which improves the efficiency.
  • FIG. 1 For the gas-steam power plant according to FIG. 2 are shown in FIG. 1 used reference numerals, as far as possible. With regard to the circuit of the gas turbine process shown there, reference is expressly made to DE-OS 35 36 451 and DE-Z "Energiespektrum", Jan. 1987, pp. 21-22, the disclosure of which is hereby also made the subject of the disclosure of the present application becomes.
  • a high-pressure turbine (5a) and a low-pressure turbine (5b) are provided in the gas-steam power plant according to FIG. 2.
  • Steam emerging from the high-pressure turbine (5a) is fed via line (20) to a heating surface (21) in the high-pressure steam generator (1), in order to be subjected to reheating there.
  • the reheated steam is fed to the low-pressure turbine via a line (22).
  • steam of a first pressure stage is fed via a cold reheater line (23) to a preheater (24) lying parallel to the heat exchanger (15).
  • a further preheater (25) is located in series with the preheater (24) and is supplied with tapped steam from the turbine (5b) via a bleed line (26).
  • a control valve (27) is in series with the preheaters (24) and (25).
  • the feed water reservoir (10) is heated via a further tap line (28) of the turbine (5b).
  • a line (30) having a throttle valve (29) branches off from the line (23) and is used to supply the high pressure steam generator with motive steam for injecting the coal (K) into the combustion chamber (2). Since for the injection of the fuel in the form of a coal-water mixture, less steam is introduced directly into the combustion chamber (2) than makes sense for the possible increase in efficiency, the combustion chamber is still connected to the system via a tap line (31) Steam turbine (5b) connected, a control valve (32) also being set in line (31).
  • the pressure in the lines (31) and (30) downstream of the rain valves (32) and (29) must be greater than the combustion chamber pressure built up by the compressor (12) in the combustion chamber, and further the pressure in the line (30) is due to injection of fuel must be higher than in line (31).
  • the gas emerging from the gas turbine (14) is fed to the heat exchanger (15) via a combustion air / combustion gas heat exchanger (33) and is subsequently expanded in a further gas turbine (34) which, together with a compressor upstream of the compressor (12) (35) builds a turbocharger.
  • a gas cooler (36) which is preferably also integrated into the water-steam circuit.
  • the steam introduced via line (4) and having a temperature of 530 ° in the steam turbine (5a) is partially expanded and after another reheating to a temperature of 530 ° in the turbine (5b) fully expanded and at a temperature of 30 ° C condensed.
  • the steam removed from the turbine (5a) via line (23, 30) is fed into the combustion chamber (2) in the case of the pressure fluidized bed according to FIG. 2 heated to the highest possible temperature of 850 ° C and together with the combustion gases in the gas turbine relaxed working.
  • This is shown in the (Ts) diagram of the steam turbine process by the dash-dotted line.
  • the gas turbine (14) or the gas turbines (14) and (34) can thus also be evaluated with respect to the steam turbine process as a steam turbine integrated in the gas turbines.

Landscapes

  • 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)
EP88908952A 1987-10-15 1988-10-13 Gas-dampf-kraftanlage Expired - Lifetime EP0334935B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT88908952T ATE84600T1 (de) 1987-10-15 1988-10-13 Gas-dampf-kraftanlage.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3734959 1987-10-15
DE19873734959 DE3734959A1 (de) 1987-10-15 1987-10-15 Gas-dampf-kraftanlage

Publications (2)

Publication Number Publication Date
EP0334935A1 EP0334935A1 (de) 1989-10-04
EP0334935B1 true EP0334935B1 (de) 1993-01-13

Family

ID=6338414

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88908952A Expired - Lifetime EP0334935B1 (de) 1987-10-15 1988-10-13 Gas-dampf-kraftanlage

Country Status (4)

Country Link
EP (1) EP0334935B1 (enrdf_load_stackoverflow)
AT (1) ATE84600T1 (enrdf_load_stackoverflow)
DE (2) DE3734959A1 (enrdf_load_stackoverflow)
WO (1) WO1989003471A1 (enrdf_load_stackoverflow)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2624891B2 (ja) * 1990-11-30 1997-06-25 株式会社日立製作所 加圧流動層ボイラ発電プラント
DE4117192C2 (de) * 1991-05-25 1994-06-23 Saarbergwerke Ag Verfahren zur Erzeugung von Energie in einer kombinierten Gas-Dampfkraftanlage und Anlage zur Durchführung des Verfahrens
FR2968706A1 (fr) 2010-12-10 2012-06-15 Alstom Technology Ltd Circuit d'alimentation en vapeur d'une turbine

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB935658A (en) * 1959-12-30 1963-09-04 Union Carbide Corp Process for generating steam using a fluidized bed, combustion apparatus
CH456250A (de) * 1966-05-06 1968-05-15 Sulzer Ag Verfahren zum gemischten Gas- und Dampfbetrieb einer Gasturbinenanlage sowie Anlage zur Ausübung des Verfahrens
FR1496420A (fr) * 1966-10-11 1967-09-29 Sulzer Ag Procédé pour l'alimentation mixte en gaz et en vapeur d'une installation de turbine à gaz et instalation pour la mise en oeuvre de ce procédé
FR92028E (fr) * 1966-12-28 1968-09-13 Sulzer Ag Procédé pour l'alimentation mixte en gaz et en vapeur d'une installation de turbine à gaz et installation pour la mise en oeuvre de ce procédé
DE2138664C3 (de) * 1971-07-23 1974-01-24 Gebrueder Sulzer Ag, Winterthur (Schweiz) Gas-Dampfturbinenanlage
CH555471A (de) * 1972-09-07 1974-10-31 Sulzer Ag Gas-dampfturbinenanlage.
SE434883B (sv) * 1980-10-15 1984-08-20 Stal Laval Turbin Ab Sett att driva en kombinerad gas-angturbinanleggning samt kombinerad gas-angturbinanleggning for utnyttjande av settet
DE3536451A1 (de) * 1985-10-12 1987-04-16 Steinmueller Gmbh L & C Druckaufgeladen betreibbare feuerung fuer einen dampferzeuger

Also Published As

Publication number Publication date
EP0334935A1 (de) 1989-10-04
ATE84600T1 (de) 1993-01-15
DE3734959C2 (enrdf_load_stackoverflow) 1990-05-31
DE3734959A1 (de) 1989-07-13
DE3877557D1 (de) 1993-02-25
WO1989003471A1 (en) 1989-04-20

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