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 with at least one high-pressure steam generator having a water-steam circuit, in the pressurized combustion chamber of which heat and combustion gases are generated by combustion of a fuel, at least one heating surface assigned to the combustion chamber, via the heat from the combustion chamber is transferred directly to the water-steam cycle, at least one steam turbine downstream of the heating surface and at least one gas turbine downstream of the combustion chamber on the exhaust gas side for work-expanding expansion of the combustion exhaust gas.
• At least partially expanded steam is withdrawn from the steam turbine with replenishment of a corresponding amount of water into the water-steam circuit and input directly into the combustion chamber at a pressure above the pressure prevailing in the combustion chamber is heated there to the highest possible temperature in the combustion chamber and then expanded together with the combustion gas in the gas turbine.
• a gas-steam power plant in which a gas turbine with an upstream combustion chamber for propellant gas supply for heat recovery is followed by a heat recovery steam boiler, which in turn has a connection to the combustion chamber on the steam side. At least one steam turbine is switched on in the connection from the heat recovery steam boiler to the combustion chamber. On the gas side, at least one further heat recovery steam generator is connected downstream of the heat recovery steam generator is connected to the combustion chamber on the steam side.
• Heat recovery steam boilers fed to the combustion chamber are each set higher than the working pressure in the
• Air, fuel and injection steam are introduced into the combustion chamber to generate a propellant gas, and the combustion gas mixed with the steam is expanded in the gas turbine in a work-performing manner. Except for inevitable losses, no heat is removed from the combustion chamber, i.e. H. the combustion chamber is not integrated in the water-steam cycle of the waste heat boiler and steam turbine. Therefore, the temperature of the propellant gas lying on the gas turbine is alone a function of the ratio of combustion air to fuel, the temperature of the supplied combustion air. the quantity and condition of the injection steam and the calorific value of the fuel supplied to the combustion chamber.
• DE-OS 33 31 153 aims to reduce pollutant emissions, it is entirely in the spirit of the gas-steam power plant known from DE-OS if the supply of injection steam has a temperature-reducing effect with a fixed combustion air ratio. However, it is disadvantageous that such a lowering of the temperature is associated with a reduction in the thermal efficiency of the overall system.
• the combustion air ratio In order to keep the gas temperature in front of the gas turbine at a desired high value from a thermodynamic point of view (efficiency) despite the steam injection, the combustion air ratio must be changed by adding fuel in the direction of a lower excess air. Because with the same air mass flow in the case of steam injection to adapt the gas temperature to one for the Gas turbine compatible temperature must be given more fuel, the propellant gas mass flow supplied to the gas turbine through the gas turbine is not only increased by the steam mass flow injected to lower the temperature, but also by the combustion exhaust gas mass flow due to the additionally required fuel mass flow. Thus, the work of the gas turbine is increased, but it is more difficult to use the energy available in the larger amount of exhaust gas from the gas turbine, so that the exhaust gas loss is increased in addition to the increased work output.
• Injected steam 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 to the overheating of the steam input directly into the combustion chamber to the exhaust gas temperature, i. 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.
• Pressure fluidized bed combustion with stationary fluidized bed is formed.
• the gas turbine in a manner known per se from DE-OS 35 36 451 has a heat exchanger for the heat exchange with the combustion air and / or a heat exchanger for the water-steam cycle and this one more Gas turbine is connected downstream, in which the combustion gas is expanded while still performing work.
• This second turbine is in turn preferred and known per se part of a turbocharger for the combustion air.
• Pressure fluidized bed firing is further preferred that 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 reheating which can take a pressure stage from the cold Zu, while the lower pressure stage can be taken from a turbine charged with the Zü steam.
• FIG. 1 shows a simplified circuit diagram to explain the gas-steam power plant according to the invention
• FIG. 2 shows an embodiment of the gas-steam power plant according to the invention, in which the combustion chamber of the high-pressure steam generator is designed as a pressure-charged fluidized bed, and
• FIG. 3 shows a Ts diagram to explain the
• 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 fed as fuel Konle (K) and for desulfurization CaCO 3 .
• 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 Da mpf 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 into the line (11) to a chimney (not shown).
• tap 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 expanded together with the combustion exhaust gas in the turbine (14), which drives the compressor (12) and possibly an additional generator (18).
• the steam is the turbine (5) z. B. at 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, the disclosure of which is hereby also made the subject of the disclosure of the present application.
• 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 (2) 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 to a preheater (24) lying parallel to the heat exchanger (15) via a cold reheater line (23).
• a preheater (24) In series with the preheater (24) is another preheater (25) which is supplied with bleed steam from the turbine (5b) via a bleed line (26).
• a control valve (27) is in series with the preheaters (24) and (25), and 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), via which motive steam for injecting the coal (K) into the combustion chamber (2) is fed to the high-pressure steam generator. Because less steam is directly introduced into the combustion chamber (2) for the injection of the fuel in the form of a coal-water mixture than seems reasonable 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 pressure in the combustion chamber built up by the compressor (12), and furthermore the pressure in the line (30) because of the injection of the fuel be higher than in the 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 in the water-steam circuit.
• the steam brought in via line (4) and having a temperature of 530 is partially expanded in the steam turbine (5a) and, after reheating again, is fully expanded to a temperature of 530 in the turbine (5b) 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 850o 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 be evaluated based on the Dampfturbi nenprocess as a steam turbine integrated into the gas turbines.

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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)

Priority Applications (2)

Applications Claiming Priority (2)

Publications (1)

Family

ID=6338414

Family Applications (1)

Country Status (4)

Cited By (2)

Families Citing this family (1)

Citations (7)

Family Cites Families (1)

• 1987
  • 1987-10-15 DE DE19873734959 patent/DE3734959A1/de active Granted
• 1988
  • 1988-10-13 EP EP88908952A patent/EP0334935B1/de not_active Expired - Lifetime
  • 1988-10-13 AT AT88908952T patent/ATE84600T1/de not_active IP Right Cessation
  • 1988-10-13 DE DE8888908952T patent/DE3877557D1/de not_active Expired - Fee Related
  • 1988-10-13 WO PCT/EP1988/000920 patent/WO1989003471A1/de active IP Right Grant

Patent Citations (7)

Non-Patent Citations (1)

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