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
  • F01K27/00—Plants for converting heat or fluid energy into mechanical energy, not otherwise provided for
  • F01K27/02—Plants modified to use their waste heat, other than that of exhaust, e.g. engine-friction heat
• • 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
  • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
  • F01K3/02—Use of accumulators and specific engine types; Control thereof
  • F01K3/04—Use of accumulators and specific engine types; Control thereof the engine being of multiple-inlet-pressure type
• • 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
  • F01K23/101—Regulating means specially adapted therefor

Definitions

• the invention relates to the frequency support operation of a gas and steam turbine plant.
• this also includes the ability to release additional power in the event of high power consumption (so-called peak load operation).
• peak load operation In the future, it is expected that power plants operating at their nominal point will also participate in peak load coverage and frequency support.
• Today's solutions rely on the use of power reserves within the components or are based on technologies that can provide only a very low power reserve.
• the gas turbine can be overfired for both frequency support and peak load coverage, the compressor vanes can be opened beyond the base load position, or water can be injected into the intake air duct.
• Requirements relating only to peak load coverage can be met by steam injection into the gas turbine combustion chamber, by cooling the gas turbine intake air, for example with evaporative coolers or chillers, or by the waste heat steam generator (AHDE) with additional firing equipped to raise the steam turbine power.
• AHDE waste heat steam generator
• the live steam or the steam from the reheat can be accumulated and the turbine control valves are then opened quickly.
• EP 1 164 254 B1 describes a gas and steam turbine plant with steam diversions for peak load coverage, ie for additional power at full load.
• the object of the invention is to provide a method for the frequency-supporting operation of a gas and steam turbine plant, which provides an improved power reserve.
• the invention solves this problem by providing that in the operation of a gas and steam turbine plant with a gas turbine, a steam turbine and a Abhitzedampferzeu- ger, in the heat exchange with exhaust gas from the gas turbine steam for the steam turbine can be generated for frequency support in the power grid From a steady state operation, the absorption capacity of the steam turbine can be increased and the pressure in the heat recovery steam generator lowered to utilize storage reserves in the waste steam generator for increased steam generation, and heat energy is supplied to the waste heat steam generator so quickly that a performance curve of the gas and steam turbine plant in Consequence of increasing the absorption capacity of the steam turbine and the pressure reduction in the heat recovery steam generator is greater than or equal to a previously existing stationary operation.
• the invention is therefore based on the idea to use storage reserves in the heat recovery steam generator to generate additional steam at sudden opening of the valves.
• Pressure drop in the heat recovery steam generator is additionally generated steam and a sufficiently large and fast supply of heat energy should the usual dent in the performance curve prevent. This method can provide control power at partial and full load.
• the flexibility and efficiency of the power plant can be significantly increased, since at high power demand additional energy is available, which leads to increased revenue especially at high electricity revenues in electricity markets and makes the operation of the plant more economical (peak load capacity).
• the primary frequency support or the peak load operation it is not necessary for the primary frequency support or the peak load operation to design the high-pressure or the reheat part higher in the pressure than for the nominal operation.
• the load range of the power plant can be extended, since even the low load operation can be set more flexible.
• At least one valve in a bypass channel for bypassing a steam turbine stage or a steam turbine module is opened.
• the heat energy is supplied by an additional power of the gas turbine and thus an increased exhaust gas flow.
• the heat energy is supplied via an additional firing.
• this must be dimensioned accordingly.
• FIG. 1 shows a simplified circuit diagram of a gas and steam turbine plant with high and medium pressure overload discharge and control wheels in the steam turbine and an additional firing in the heat recovery steam generator
• FIG. 3 Steam turbine power curve with overload introduction into the medium-pressure turbine for various live steam pressure to inlet pressure conditions.
• FIG. 1 shows a gas and steam turbine plant 1, which comprises a gas turbine 2 and a steam turbine 3.
• a gas turbine 2 and a steam turbine 3.
• a rotor of the gas turbine, a rotor of a generator 5 and a rotor of the steam turbine 3 are coupled together, wherein the rotor of the steam turbine. 3 and the rotor of the generator 4 are rotationally separable from each other and coupled via a coupling 6.
• the runners of the generator 5 and of the gas turbine 2 are rigidly connected via the shaft 4. prevented.
• a flue gas outlet of the gas turbine 2 is connected via an exhaust pipe 7 with a heat recovery steam generator 8, which is provided for generating the operating steam of the steam turbine 3 from waste heat of the gas turbine.
• a compressor 9 is driven by the rotating rotor of the gas turbine 2 via the shaft 4, which sucks combustion air from the environment and a combustion chamber 10 supplies.
• the combustion air is mixed with fuel supplied by a fuel supply 11 and burned and the hot, pressurized exhaust gases are supplied to the gas turbine 12 and there relaxed under the power of work.
• the still about 500 to 600 ° C hot exhaust gases are then fed through the exhaust pipe 7 to the heat recovery steam generator 8 and flow through this until they pass through a chimney 13 into the environment.
• a high pressure superheater 14 On their way through the heat recovery steam generator 8, they pass their heat to a high pressure superheater 14, then a high pressure reheater 15, a high pressure evaporator 16, a high pressure preheater 17, then a medium pressure superheater 18, a medium pressure evaporator 19, a medium pressure preheater 20, then a low pressure superheater 21 , a low pressure evaporator 22 and finally a condensate preheater 23.
• superheated steam is supplied through a steam discharge line 24 of a high pressure stage 25 of the steam turbine 3 and there relaxed under the power of work.
• the shaft 4 and thus the generator 5 is moved to generate electrical energy.
• the partially relaxed in the high-pressure stage 25 hot steam is then fed to the high-pressure reheater 15, where it is reheated and fed via a derivative 26 a medium-pressure stage 27 of the steam turbine 3 and there relaxed under the power of mechanical work.
• the there partially relaxed steam is via an overflow 28 of a low pressure stage 29th fed to the steam turbine 3 and further relaxed there with the release of mechanical energy.
• the expanded steam is condensed in the condenser 30 of the steam turbine 3, and the resulting condensate is a condensate pump 31 directly to a low pressure stage 32 of the heat recovery steam generator 8 or via a feed 33 - and provided by the corresponding pressure - a medium-pressure stage 34 or a high-pressure stage 35th of the heat recovery steam generator 8, where the condensate evaporates.
• the steam is supplied via the corresponding outlets 24, 26, 36 of the heat recovery steam generator 8 back to the steam turbine 3 for relaxation and performance mechanical work.
• shut-off valves 37 and 38 are arranged. From the high-pressure stage 25 of the steam turbine 3 leading steam discharge line 24 branches off a bypass channel 39 with a shut-off valve 40 for bypassing the Hoch horrstu- 25 fe. Similarly, a bypass channel 41 branches off with a shut-off valve 42 for bypassing the intermediate-pressure stage 27.
• a first control wheel 43 is attached to the rotor of the steam turbine 3.
• a second control wheel 44 is attached to the rotor of the steam turbine 3.
• a control wheel comprises valves controlled via valves, which can be acted upon by segments of a turbine. Depending on how many of the valves are opened, a more or less large amount of additional steam flows through the nozzles into the turbine.
• Figure 1 shows an additional firing 45 at the entrance of the heat recovery steam generator 8, in which the gas turbine exhaust gas, which still contains much oxygen, fuel is added and the mixture is burned.
• the live steam over the temperature of the gas turbine exhaust gas can be overheated or for generating process steam when the steam generation is to be decoupled from the power generation of the gas turbine 2.
• supplemental firing 45 may be of interest to increase the output of electrical power during peak demand periods.
• the inventive method provides that the steam mass flow is increased by the steam turbine in the short term by opening an overload valve 40, 42 and a turbine bypass 39, 41 and connected to the power of the steam turbine 3 rises rapidly (seconds range).
• the overload introduction can be utilized both at the high-pressure turbine 25 for raising the live steam mass flow and at the medium-pressure turbine 27 for increasing the intermediate superheat steam mass flow and before each further turbine stage (for example low-pressure turbine 29).
• the intake capacity of the steam turbine can be increased via a control wheel 43, 44 on the high-pressure turbine 25 and / or the medium-pressure turbine 27 by opening associated valves.
• Storage reserves can be released from all pressure stages 32, 34, 35 of the heat recovery steam generator 8 (for example also medium and low pressure systems, if present).
• the drum pressure e.g. by a pressure control valve 46 in the medium-pressure steam system 34, while the Aus Grandefil can be increased. This increase in steam mass flow rate is due to an increase in the absorption capacity of the steam turbine and an associated pressure drop in the system.
• the decreasing storage effect either by a self-igniting additional firing 45 in the heat recovery steam generator 8, operated in continuous minimum load additional firing 45 or by existing power reserves in the gas turbine 2 (turning up the compressor vanes, Studentsfeue- tion, or Vampfeindüsung Water injection in the compressor 9 or combustion chamber 10) compensated or further increased.

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)
• Control Of Turbines (AREA)

Priority Applications (6)

Applications Claiming Priority (2)

Publications (2)

Family

ID=47115955

Family Applications (1)

Country Status (7)

Families Citing this family (8)

Citations (1)

Family Cites Families (12)

• 2011
  • 2011-11-14 EP EP11188956.4A patent/EP2592241A1/de not_active Withdrawn
• 2012
  • 2012-10-30 EP EP12780192.6A patent/EP2798164A2/de not_active Withdrawn
  • 2012-10-30 KR KR1020147012600A patent/KR20140088145A/ko not_active Application Discontinuation
  • 2012-10-30 RU RU2014124127/06A patent/RU2014124127A/ru not_active Application Discontinuation
  • 2012-10-30 WO PCT/EP2012/071478 patent/WO2013072183A2/de active Application Filing
  • 2012-10-30 US US14/356,158 patent/US20140345278A1/en not_active Abandoned
  • 2012-10-30 IN IN869KON2014 patent/IN2014KN00869A/en unknown
  • 2012-10-30 EP EP14004089.0A patent/EP2907980A1/de not_active Withdrawn
  • 2012-10-30 CN CN201280055971.5A patent/CN104246151B/zh not_active Expired - Fee Related

Patent Citations (1)

Also Published As

Similar Documents

Legal Events