WO2011006882A2 - Cogeneration plant and cogeneration method - Google Patents

Cogeneration plant and cogeneration method Download PDF

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Publication number
WO2011006882A2
WO2011006882A2 PCT/EP2010/060022 EP2010060022W WO2011006882A2 WO 2011006882 A2 WO2011006882 A2 WO 2011006882A2 EP 2010060022 W EP2010060022 W EP 2010060022W WO 2011006882 A2 WO2011006882 A2 WO 2011006882A2
Authority
WO
WIPO (PCT)
Prior art keywords
combustion gas
steam
turbine
condenser
gas
Prior art date
Application number
PCT/EP2010/060022
Other languages
French (fr)
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WO2011006882A3 (en
Inventor
Mats SJÖDIN
Original Assignee
Siemens Aktiengesellschaft
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 Siemens Aktiengesellschaft filed Critical Siemens Aktiengesellschaft
Priority to PL10732946T priority Critical patent/PL2454454T3/en
Priority to EP10732946.8A priority patent/EP2454454B1/en
Priority to ES10732946.8T priority patent/ES2559506T3/en
Priority to MA34525A priority patent/MA33424B1/en
Priority to CN201080031273.2A priority patent/CN102472120B/en
Priority to US13/383,283 priority patent/US9657604B2/en
Publication of WO2011006882A2 publication Critical patent/WO2011006882A2/en
Publication of WO2011006882A3 publication Critical patent/WO2011006882A3/en
Priority to TNP2011000671A priority patent/TN2011000671A1/en

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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
    • 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
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • F01K17/02—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic
    • F01K17/025—Using steam or condensate extracted or exhausted from steam engine plant for heating purposes, e.g. industrial, domestic in combination with at least one gas turbine, e.g. a combustion gas turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/34—Gas-turbine plants characterised by the use of combustion products as the working fluid with recycling of part of the working fluid, i.e. semi-closed cycles with combustion products in the closed part of the cycle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas- turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • 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
    • F22B1/1807—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 using the exhaust gases of combustion engines
    • F22B1/1815—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 using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
    • F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
    • F28D21/0001—Recuperative heat exchangers
    • F28D21/0003—Recuperative heat exchangers the heat being recuperated from exhaust gases
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/14—Combined heat and power generation [CHP]
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/32—Direct CO2 mitigation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/34—Indirect CO2mitigation, i.e. by acting on non CO2directly related matters of the process, e.g. pre-heating or heat recovery

Definitions

  • Cogeneration plant and cogeneration method relates to a plant and a method of cogeneration, by burning a fuel in a gas turbine cycle for generation of a combustion gas utilized for heating water into steam in a steam cycle, wherein said gas turbine cycle includes
  • a combustor of said gas turbine burning a mixture of fuel, oxygen and a recirculated first flow of combustion gas, generating combustion gas to be expanded
  • a heat recovery steam generator arranged downstream the gas turbine, receiving combustion gas to heat liquid water and steam, resulting in steam and/or superheated steam,
  • a compressor receiving said first combustion gas flow, which is compressed to enter the combustor and mix with said flow of oxygen and fuel to be burned in said gas turbine,
  • said steam cycle includes:
  • a steam turbine by means of which said steam is expanded
  • a first condenser arranged downstream the steam turbine, by means of which expanded steam is at least partially condensed to liquid water
  • these cycles consist of a so called closed Brayton Cycle operated at a high temperature combined with a low temperature Rankine Cycle.
  • the Brayton Cycle consists of compressors, a combustion chamber and a high temperature gas turbine.
  • a Rankine Cycle consists of a steam turbine, a condenser and a steam generator.
  • the steam generator might be a heat recovery steam generator.
  • the turbine can be a one casing turbine or a combination of high-, intermediate- or low-pressure turbines.
  • the fuel is natural gas or other hydro-carbon based fuel gas together with a nearly stochiometric mass flow of oxygen, which is supplied to a combustion chamber respectively burner, preferably operated at a pressure of 20 bar - 60 bar depending on the chosen design parameters for the Brayton cycle, mainly turbine inlet temperature, turbine cooling concept and low pressure compressor inlet temperature.
  • the high temperature turbine is therefore operated at a
  • the turbine cooling system utilizes the working medium from the compressor which is mainly a mixture of carbon dioxide and water as coolant.
  • the relatively cool working medium from the compressor is also utilized as cooling medium for the burners respectively the combustion chamber and all other parts which are exposed to the high temperature from the combustion.
  • the hot exhaust gas After expansion in the Brayton cycle gas turbine the hot exhaust gas is cooled in a downstream heat recovery steam generator vaporising water and superheating steam for a Rankine cycle high
  • the cooled exhaust gas exiting the heat recovery steam generator is entering a
  • cooler/condenser-module operating with a cooling medium preferably separated from the Rankine cycle.
  • cooler/condenser could be connected to an external cooling source such as sea water, ambient air, ambient air via an intermediate water system or a district heating grid.
  • the main purpose of this cooler/condenser-module is to reduce the water content in the combustion gas to reduce the compressor work in the compression of the re-circulated stream.
  • the dehydrated combustion gas stream is divided into two part flows, of which a first stream is re- heated before it is compressed and fed into the combustion chamber respectively burner and the second stream is a bleed stream compensating for the part of the injected fuel and oxygen that has not been separated in the cooler/condenser.
  • the first stream that is to be re-compressed in the main cycle is also passing a re-heat heat exchanger before it is entering the compressor.
  • the main purpose with this re-heat is to reduce the relative humidity in the flue gas stream to avoid erosion of the first compressor stages by water droplets.
  • the cooler/condenser and the re-heat could be designed to generate favourable cycle conditions for the Brayton cycle in order to optimize the cycle efficiency, plant net present value or be designed to fit a temperature in the high temperature part of the compressor that is favourable from a material point of view.
  • the second working medium stream from the division point is a bleed stream, balancing the rest of the feed streams of fuel and oxygen that have not been separated in the
  • cooler/condenser module containing mainly steam and carbon dioxide, supplied to a second condenser, in which the de- humidification of the combustion gas stream is continued in a second stage where more water is separated from the
  • condensation is fed into a water clean-up system from where it could be regarded as a by-product.
  • the condensed water from the cooler/condenser is also drained to the same water clean-up system. This cycle is powered by the heat recovery steam generator heated by the exhaust gas of the high
  • gas turbine, steam turbine and compressor are used synonymously for one or more respective machines, which might be arranged in serial or parallel order and are used to expand or compress essentially one respective process fluid flow .
  • the method of cogeneration disclosed might be performed with a power generation cycle, hereinafter referred to as a low pressure twin cycle.
  • the low pressure twin cycle is a re- circulated oxy fuel cycle with a heat recovery steam
  • the oxy fuel cycle utilizes an oxy fuel turbine unit - which is basically a gas turbine designed to operate with oxy fuel - including a compressor, a combustor and a turbine unit.
  • oxy fuel turbine unit - which is basically a gas turbine designed to operate with oxy fuel - including a compressor, a combustor and a turbine unit.
  • a H 2 O- C ⁇ 2-mixture is generated in the combustor by close to
  • cooler/condenser-module preferably uses cooling or district heating water as cooling media before the cooled gas is reheated and recycled through the compressor.
  • the compressor comprises several units, for example a low
  • the combustor which comprises a mixing chamber and the combustor.
  • the combustor can be provided with several swirlers and burners for a highly efficient and stable combustion. Downstream the heat recovery steam generator said combustion gas is cooled and the moisture content of said combustion gas is partially condensed and the liquid phase is separated from the
  • combustion gas flow before the gas flow is divided into a first combustion gas flow and a second combustion gas flow.
  • Said first combustion gas flow is submitted to the described re-heat heat exchanger to reduce the relative humidity in the flue gas stream to avoid erosion of the first compressor stages before it is entering the compressor, but also to make it possible to reduce the moisture content of the combustion gas in a larger extent without reducing the temperature of the combustion gas flow into the combustion.
  • Said first combustion gas flow is then submitted to the described compression to enter downstream the combustor of the gas turbine.
  • Said second combustion gas flow is further cooled down to condense more of the moisture content of the
  • combustion gas flow to liquid water in order to separate the vaporised water from the carbon dioxide, which is afterwards compressed and extracted from the cycle preferably in order to store this compressed gas finally.
  • Figure 1 shows a schematic overview of a cycle according to the invention.
  • Figure 1 shows a low pressure twin cycle LPTC, which combines a gas turbine GT and a steam turbine STT in one thermodynamic cycle essentially by a heat recovery steam generator HRSG.
  • the gas turbine GT comprises a combustor COMB, a first gas turbine GTl and a second gas turbine GT2, wherein the first gas turbine GTl drives a compressor unit COMP and the second gas turbine GT2 drives a first generator Gl by means of a second transmission gear GR2.
  • the compressor unit COMP comprises a low pressure compressor COMPl and a high pressure compressor COMP2, which are both coupled to each other by means of a transmission gear GRl.
  • the transmission gear GRl has a gear ratio smaller 1 to give the low pressure
  • the combustor COMB is supplied with oxygen 02 and fuel F, which is mixed to a close to stochiometric mixture in a not further shown mixing chamber and burned in a burner BUR of the combustor COMB and expanded downstream the combustor COMB into the first gas turbine GTl and the second gas turbine GT2 as a combustion gas CG.
  • the oxygen 02 and the fuel F is mixed upstream the burner of the combustor COMB with a first flow of combustion gas CGl, which was compressed by the compressor COMP upstream the combustor COMB.
  • the combustion gas CG Downstream the expansion in the gas turbine GT the combustion gas CG is submitted to the heat recovery steam generator HRSG to be cooled down by way of heating up liquid water LQ to steam ST in order to gain super-heated steam ST.
  • the heat recovery steam generator HRSG comprises several heat
  • cooler/condenser-module CCON operating with a cooling medium CM separated from the Rankine cycle.
  • This cooler/condenser could be connected to an external cooling source as sea water, ambient air via a water system or a district heating grid.
  • the cooler/condenser CCON the humid fraction of the combustion gas is partly condensed into liquid water, which is separated from the working medium of the cycle CG.
  • the condensed water from the cooler/condenser is drained to a water clean-up system.
  • the main reason for this condensation is to reduce the H2O fraction in the dehydrated combustion gas CGDH re-circulated to the compressors to reduce the amount of compression work in the cycle.
  • Downstream the heat exchange in the cooler/condenser module CCON the combustion gas CG is divided at a division point DIV into a first flow of combustion gas CBl and a second flow of combustion gas CB2, wherein the first flow of combustion gas CBl is re-heated in a heater CHEAT before it enters the compressor COMP.
  • the second flow of combustion gas CB2 is submitted to a second condenser CON2 in order to cool down this mixture of water and carbon dioxide.
  • a part of the humid fraction of the combustion gas CB2 is condensed into water H2O, which is separated from the rest of the gas mixture.
  • COCl - C0C3 and intercoolers COOl - C003 the carbon dioxide CO2 is
  • the drawing shows by way of example three compressors and intercooling while the number of stages can in practice vary to more or less stages.
  • the water H20 condensed and separated in a second condenser CON2 and in a number of intercoolers is united at a junction point COM and submitted to a fourth pump PU4 and delivered to a higher pressure level.
  • the superheated steam ST leaving the heat recovery steam generator HRSG enters downstream a high pressure steam turbine STTl of the steam turbine STT to be expanded.
  • the high pressure steam turbine STTl is coupled to the intermediate pressure steam turbine STT2 by means of a third gear GR3, which enables different speeds of the two steam turbines.
  • a second generator G2 is coupled to the
  • the liquid water LQ Downstream the pump PUl the liquid water LQ exchanges heat energy in a first heat exchanger EXl before entering a first separator SEPl, which degasifies the liquid water LQ.
  • the degasified liquid water LQ After entering the cold site of the first heat exchanger EXl the degasified liquid water LQ is delivered by a second pump PU2 to a higher pressure level to enter the cold site of the heat recovery steam generator HRSG.
  • the liquid water LQ is stepwise increased in temperature in the heat recovery steam generator HRSG passing through several heat exchangers HEX, vaporized and superheated by heat exchange with the
  • the super heated steam ST is submitted downstream the heat recovery steam generator HRSG into the high pressure turbine STTl of the steam turbine ST to be expanded.
  • a cooling steam STCO is extracted at an extraction point by means of an extraction module EXT from the high pressure steam turbine STTl to cool parts of a hot gas path HGP of the first gas turbine GTl. While 35% of the cooling steam STCO is injected into the hot gas path HGP for the purpose of film cooling, 65% of the cooling steam STCO leaves the cooling system CS of the gas turbine GT with a higher temperature.
  • the remaining 65% of the cooling steam STCO are reunited with the main flow of the steam ST by means of a feeding module IN at the entrance of the low pressure steam turbine STT2, which also receives the steam ST exiting the high pressure steam turbine STTl.
  • a portion of the cooling steam STCO can be injected into the hot gas path HGP of the gas turbine GT.
  • the portion STGTCO is at least partially used for film cooling of rotating parts of the gas turbine GT.
  • Another embodiment provides the cooling system CS as a closed system with regard to the hot gas path HGP of the gas turbine GT and the cooling steam STCO is reunited with the steam ST in full amount. Good results were achieved, when the portion STGTCO to be injected into the hot gas path HGP was between 20% to 40% of said cooling steam STCO flow.
  • cooling steam STCO is only used to cool stationary parts of the gas turbine GT.
  • Another preferred embodiment provides cooling for the rotating parts wherein rotating parts are cooled with said compressed combustion gas CG which is bypassed over the combustor to be injected into the hot gas path HGP.
  • the combustion gas CG leaving the cooler/condenser-module CCON has a temperature of 55°C-75°C preferably 65°C.
  • the separate cooling medium CM of the cooler/condenser-module CCON can be heated up in the cooler/condenser-module CCON depending on the heat exchange up to approx. 95°C, which temperature level can then be used to heat the heat exchanger CHEAT to increase the first combustion gas flow CBl in temperature from 65°C up to 70 0 C which leads to a lower relative humidity.

Abstract

The invention relates to a co-generation plant and method, comprising : a gas turbine (GT), a heat recovery steam generator (HRSG), a steam turbine (STT), a cooler/condenser (CCON), a division module (DMOD) at a division point (DIV), by means of which downstream said heat recovery steam generator (HRSG) said combustion gas (CG) is cooled and dehumidified in the cooler/condenser (CCON) and then divided into a first combustion gas flow (CB1) and a second combustion gas flow (CB2), a second condenser (CON2) receiving said second combustion gas flow (CB2) to separate contained carbon dioxide (CO2) from contained water by condensation of the water, a heater (CHEAT), a compressor (COMP), receiving said first combustion gas flow (CB1), which is heated, compressed and partly extracted to by-pass the combustor (COMB) for cooling of the gas turbine (GT) before it enter the combustor (COMB) and mix with said flow of oxygen (02) and fuel (F) to be burned in said gas turbine (GT).

Description

Description
Cogeneration plant and cogeneration method The invention relates to a plant and a method of cogeneration, by burning a fuel in a gas turbine cycle for generation of a combustion gas utilized for heating water into steam in a steam cycle, wherein said gas turbine cycle includes
a gas turbine, to expand a combustion gas,
a combustor of said gas turbine, burning a mixture of fuel, oxygen and a recirculated first flow of combustion gas, generating combustion gas to be expanded,
a heat recovery steam generator, arranged downstream the gas turbine, receiving combustion gas to heat liquid water and steam, resulting in steam and/or superheated steam,
a division module at a division point, by means of which downstream said heat recovery steam generator said combustion gas is divided into said recirculated first combustion gas flow and a second combustion gas flow,
a compressor, receiving said first combustion gas flow, which is compressed to enter the combustor and mix with said flow of oxygen and fuel to be burned in said gas turbine,
said steam cycle includes:
a steam turbine, by means of which said steam is expanded, a first condenser, arranged downstream the steam turbine, by means of which expanded steam is at least partially condensed to liquid water,
a first pump, wherein said first pump delivers said liquid water with increased pressure to said heat recovery steam generator to be heated up by heat exchange with said
combustion gas.
Due to the increasing awareness to climate relevant emissions a lot of effort is undertaken to minimize the emission of carbon dioxide, which is thought to be one of the most relevant reasons for the increase of the world's temperature respectively the greenhouse effect. Latest developments led to cogeneration cycles having zero emission and a higher efficiency. Within this cycle fossil fuels are burned with pure oxygen, which enables the separation of the carbon dioxide, generated during the oxidation, in a cost effective way by condensation of the H20-fraction of the combustion gas. The increased cycle efficiencies compensate at least partly the efforts for the supply of pure oxygen undertaken in an upstream air separation module. This cycle becomes a zero emission cycle if the separated carbon dioxide is stored at an adequate location.
Basically these cycles consist of a so called closed Brayton Cycle operated at a high temperature combined with a low temperature Rankine Cycle. Typically the Brayton Cycle consists of compressors, a combustion chamber and a high temperature gas turbine. Often a Rankine Cycle consists of a steam turbine, a condenser and a steam generator. The steam generator might be a heat recovery steam generator. The turbine can be a one casing turbine or a combination of high-, intermediate- or low-pressure turbines. Preferably the fuel is natural gas or other hydro-carbon based fuel gas together with a nearly stochiometric mass flow of oxygen, which is supplied to a combustion chamber respectively burner, preferably operated at a pressure of 20 bar - 60 bar depending on the chosen design parameters for the Brayton cycle, mainly turbine inlet temperature, turbine cooling concept and low pressure compressor inlet temperature. The high temperature turbine is therefore operated at a
temperature of up to 16000C and the turbine cooling system utilizes the working medium from the compressor which is mainly a mixture of carbon dioxide and water as coolant. The relatively cool working medium from the compressor is also utilized as cooling medium for the burners respectively the combustion chamber and all other parts which are exposed to the high temperature from the combustion. After expansion in the Brayton cycle gas turbine the hot exhaust gas is cooled in a downstream heat recovery steam generator vaporising water and superheating steam for a Rankine cycle high
pressure steam turbine.
It is one object of the invention to increase the efficiency of the Brayton cycle and to avoid erosion in the compressor.
In accordance with the invention there is provided a
cogeneration plant and method of the incipiently mentioned type with the further features of claim 1 respectively claim 11. The respectively dependent claims refer to preferred embodiments of the invention.
Referring to the invention, the cooled exhaust gas exiting the heat recovery steam generator is entering a
cooler/condenser-module operating with a cooling medium preferably separated from the Rankine cycle. This
cooler/condenser could be connected to an external cooling source such as sea water, ambient air, ambient air via an intermediate water system or a district heating grid. The main purpose of this cooler/condenser-module is to reduce the water content in the combustion gas to reduce the compressor work in the compression of the re-circulated stream. After the cooler/condenser the dehydrated combustion gas stream is divided into two part flows, of which a first stream is re- heated before it is compressed and fed into the combustion chamber respectively burner and the second stream is a bleed stream compensating for the part of the injected fuel and oxygen that has not been separated in the cooler/condenser. The first stream that is to be re-compressed in the main cycle is also passing a re-heat heat exchanger before it is entering the compressor. The main purpose with this re-heat is to reduce the relative humidity in the flue gas stream to avoid erosion of the first compressor stages by water droplets. Together the cooler/condenser and the re-heat could be designed to generate favourable cycle conditions for the Brayton cycle in order to optimize the cycle efficiency, plant net present value or be designed to fit a temperature in the high temperature part of the compressor that is favourable from a material point of view. The amount of reduction of the water content in the flue gas generated from the condensation in the cooler/condenser-module and the temperature of the working medium into the compressor
generated by the heater, together with the chosen compressor pressure ratio, makes it possible to reduce the compressor work and to design the cycle for an optimum compressor outlet temperature either for maximum cycle efficiency or for maximum plant net present value. The possibility to design the system to generate a certain temperature of the working medium before the compressor can also be utilized to keep the medium temperature in the high temperature parts of the compressor below the design temperature for discs, vanes and blades i.e. design the cycle for maximum pressure ratio. The second working medium stream from the division point is a bleed stream, balancing the rest of the feed streams of fuel and oxygen that have not been separated in the
cooler/condenser module, containing mainly steam and carbon dioxide, supplied to a second condenser, in which the de- humidification of the combustion gas stream is continued in a second stage where more water is separated from the
combustion gas. The separated water of the second
condensation is fed into a water clean-up system from where it could be regarded as a by-product. The condensed water from the cooler/condenser is also drained to the same water clean-up system. This cycle is powered by the heat recovery steam generator heated by the exhaust gas of the high
temperature turbine (gas turbine cycle) on the primary side vaporizing and superheating the water respectively steam on the secondary side.
The terms gas turbine, steam turbine and compressor are used synonymously for one or more respective machines, which might be arranged in serial or parallel order and are used to expand or compress essentially one respective process fluid flow . The method of cogeneration disclosed might be performed with a power generation cycle, hereinafter referred to as a low pressure twin cycle. The low pressure twin cycle is a re- circulated oxy fuel cycle with a heat recovery steam
generator generating steam for a steam cycle. The oxy fuel cycle utilizes an oxy fuel turbine unit - which is basically a gas turbine designed to operate with oxy fuel - including a compressor, a combustor and a turbine unit. Preferably a H2O- Cθ2-mixture is generated in the combustor by close to
stochiometric combustion of hydrocarbons in pure oxygen. This mixture is then expanded in a gas turbine before entering the heat recovery steam generator unit. Downstream the heat recovery steam generator exhaust said mixture is cooled and partly dehydrated in a cooler/condenser-module. Said
cooler/condenser-module preferably uses cooling or district heating water as cooling media before the cooled gas is reheated and recycled through the compressor. Preferably the compressor comprises several units, for example a low
pressure and a high pressure unit.
After the compression said mixture enters the combustor, which comprises a mixing chamber and the combustor. The combustor can be provided with several swirlers and burners for a highly efficient and stable combustion. Downstream the heat recovery steam generator said combustion gas is cooled and the moisture content of said combustion gas is partially condensed and the liquid phase is separated from the
combustion gas flow before the gas flow is divided into a first combustion gas flow and a second combustion gas flow. Said first combustion gas flow is submitted to the described re-heat heat exchanger to reduce the relative humidity in the flue gas stream to avoid erosion of the first compressor stages before it is entering the compressor, but also to make it possible to reduce the moisture content of the combustion gas in a larger extent without reducing the temperature of the combustion gas flow into the combustion. Said first combustion gas flow is then submitted to the described compression to enter downstream the combustor of the gas turbine. Said second combustion gas flow is further cooled down to condense more of the moisture content of the
combustion gas flow to liquid water in order to separate the vaporised water from the carbon dioxide, which is afterwards compressed and extracted from the cycle preferably in order to store this compressed gas finally.
The invention will now be described, purely by way of
example, with reference to the attached drawings, of which:
Figure 1 shows a schematic overview of a cycle according to the invention.
Figure 1 shows a low pressure twin cycle LPTC, which combines a gas turbine GT and a steam turbine STT in one thermodynamic cycle essentially by a heat recovery steam generator HRSG. The gas turbine GT comprises a combustor COMB, a first gas turbine GTl and a second gas turbine GT2, wherein the first gas turbine GTl drives a compressor unit COMP and the second gas turbine GT2 drives a first generator Gl by means of a second transmission gear GR2. The compressor unit COMP comprises a low pressure compressor COMPl and a high pressure compressor COMP2, which are both coupled to each other by means of a transmission gear GRl. The transmission gear GRl has a gear ratio smaller 1 to give the low pressure
compressor COMPl a lower speed.
The combustor COMB is supplied with oxygen 02 and fuel F, which is mixed to a close to stochiometric mixture in a not further shown mixing chamber and burned in a burner BUR of the combustor COMB and expanded downstream the combustor COMB into the first gas turbine GTl and the second gas turbine GT2 as a combustion gas CG. The oxygen 02 and the fuel F is mixed upstream the burner of the combustor COMB with a first flow of combustion gas CGl, which was compressed by the compressor COMP upstream the combustor COMB. Downstream the expansion in the gas turbine GT the combustion gas CG is submitted to the heat recovery steam generator HRSG to be cooled down by way of heating up liquid water LQ to steam ST in order to gain super-heated steam ST. The heat recovery steam generator HRSG comprises several heat
exchangers HEX, which transfer energy from the combustion gas CG to the liquid water LQ respectively the steam ST.
Downstream the heat exchange in the heat recovery steam generator HRSG the combustion gas CG is entering a
cooler/condenser-module CCON operating with a cooling medium CM separated from the Rankine cycle. This cooler/condenser could be connected to an external cooling source as sea water, ambient air via a water system or a district heating grid. In the cooler/condenser CCON the humid fraction of the combustion gas is partly condensed into liquid water, which is separated from the working medium of the cycle CG. The condensed water from the cooler/condenser is drained to a water clean-up system. The main reason for this condensation is to reduce the H2O fraction in the dehydrated combustion gas CGDH re-circulated to the compressors to reduce the amount of compression work in the cycle.
Downstream the heat exchange in the cooler/condenser module CCON the combustion gas CG is divided at a division point DIV into a first flow of combustion gas CBl and a second flow of combustion gas CB2, wherein the first flow of combustion gas CBl is re-heated in a heater CHEAT before it enters the compressor COMP.
The second flow of combustion gas CB2 is submitted to a second condenser CON2 in order to cool down this mixture of water and carbon dioxide. In the second condenser CON2 a part of the humid fraction of the combustion gas CB2 is condensed into water H2O, which is separated from the rest of the gas mixture. By means of a number of compressors COCl - C0C3 and intercoolers COOl - C003 the carbon dioxide CO2 is
compressed, the moisture content reduced and the carbon dioxide is cooled to liquid phase for transport and storage. The drawing shows by way of example three compressors and intercooling while the number of stages can in practice vary to more or less stages.
The water H20 condensed and separated in a second condenser CON2 and in a number of intercoolers is united at a junction point COM and submitted to a fourth pump PU4 and delivered to a higher pressure level.
The superheated steam ST leaving the heat recovery steam generator HRSG enters downstream a high pressure steam turbine STTl of the steam turbine STT to be expanded.
The high pressure steam turbine STTl is coupled to the intermediate pressure steam turbine STT2 by means of a third gear GR3, which enables different speeds of the two steam turbines. A second generator G2 is coupled to the
intermediate pressure steam turbine STT2 to generate
electricity. Downstream the steam turbine STT the steam ST enters a first condenser CONl to be condensed into liquid water LQ.
Downstream the pump PUl the liquid water LQ exchanges heat energy in a first heat exchanger EXl before entering a first separator SEPl, which degasifies the liquid water LQ. After entering the cold site of the first heat exchanger EXl the degasified liquid water LQ is delivered by a second pump PU2 to a higher pressure level to enter the cold site of the heat recovery steam generator HRSG. The liquid water LQ is stepwise increased in temperature in the heat recovery steam generator HRSG passing through several heat exchangers HEX, vaporized and superheated by heat exchange with the
combustion gas CG from the exhaust of the gas turbine GT. The super heated steam ST is submitted downstream the heat recovery steam generator HRSG into the high pressure turbine STTl of the steam turbine ST to be expanded. Within this expansion process of the steam turbine ST a cooling steam STCO is extracted at an extraction point by means of an extraction module EXT from the high pressure steam turbine STTl to cool parts of a hot gas path HGP of the first gas turbine GTl. While 35% of the cooling steam STCO is injected into the hot gas path HGP for the purpose of film cooling, 65% of the cooling steam STCO leaves the cooling system CS of the gas turbine GT with a higher temperature. The remaining 65% of the cooling steam STCO are reunited with the main flow of the steam ST by means of a feeding module IN at the entrance of the low pressure steam turbine STT2, which also receives the steam ST exiting the high pressure steam turbine STTl. A portion of the cooling steam STCO can be injected into the hot gas path HGP of the gas turbine GT. Preferably the portion STGTCO is at least partially used for film cooling of rotating parts of the gas turbine GT.
Another embodiment provides the cooling system CS as a closed system with regard to the hot gas path HGP of the gas turbine GT and the cooling steam STCO is reunited with the steam ST in full amount. Good results were achieved, when the portion STGTCO to be injected into the hot gas path HGP was between 20% to 40% of said cooling steam STCO flow. Such an
embodiment can preferably implemented, when the cooling steam STCO is only used to cool stationary parts of the gas turbine GT. Another preferred embodiment provides cooling for the rotating parts wherein rotating parts are cooled with said compressed combustion gas CG which is bypassed over the combustor to be injected into the hot gas path HGP.
Good efficiency can be obtained, when the combustion gas CG leaving the cooler/condenser-module CCON has a temperature of 55°C-75°C preferably 65°C. The separate cooling medium CM of the cooler/condenser-module CCON can be heated up in the cooler/condenser-module CCON depending on the heat exchange up to approx. 95°C, which temperature level can then be used to heat the heat exchanger CHEAT to increase the first combustion gas flow CBl in temperature from 65°C up to 700C which leads to a lower relative humidity.

Claims

Patent claims 1. Cogeneration plant burning a fuel in a gas turbine cycle for generation of a combustion gas (CG) utilized for heating water into steam in a steam cycle, wherein:
said gas turbine cycle includes:
- a gas turbine (GT) , to expand a combustion gas (CB) , - a combustor (COMB) of said gas turbine (GT) , burning a mixture of fuel (F), oxygen (02) and a recirculated first flow of combustion gas (CG) , generating combustion gas (CG) to be expanded,
- a heat recovery steam generator (HRSG) , arranged downstream the gas turbine (GT) , receiving combustion gas (CG) to heat liquid water (LQ) and steam (ST), resulting in steam (ST) and/or superheated steam (ST) ,
- a division module (DMOD) at a division point (DIV) , by means of which downstream said heat recovery steam generator (HRSG) said combustion gas (CG) is divided into said recirculated first combustion gas flow (CBl) and a second combustion gas flow (CB2),
- a compressor (COMP) , receiving said first combustion gas flow (CBl), which is compressed to enter the
combustor (COMB) and mix with said flow of oxygen (02) and fuel (F) to be burned in said gas turbine (GT) , said steam cycle includes:
- a steam turbine (STT), by means of which said
steam (ST) is expanded,
- a first condenser (CONl), arranged downstream the steam turbine (STT) , by means of which expanded steam is at least partially condensed to liquid water (LQ) ,
- a first pump (PUl), wherein said first pump (PUl) delivers said liquid water (LQ) with increased pressure to said heat recovery steam generator (HRSG) to be heated up by heat exchange with said combustion gas (CG) ,
characterized in that - a cooler/condenser (CCON) receiving combustion
gas (CG) is provided downstream the heat recovery steam generator (HRSG) , which is cooling the combustion gas flow (CG) and
- a heater (CHEAT) for heating and de-liquefying
combustion gas (CBl) is provided downstream said
division module (DMOD) and upstream said
compressor (COMP) for heating and de-liquefying said part of said combustion gas (CBl) before supplying it to the compressor (COMP) .
2. Cogeneration plant according to claim 1, wherein said cooler/condenser module (CCON) partly condensates the vapor fraction of said combustion gas (CG) into liquid phase (H20) .
3. Cogeneration plant according to claim 1 or 2, wherein said cooler/condenser (CCON) is cooled by a cooling medium
separated from the steam cycle.
4. Cogeneration plant according to claim 3, wherein said cooling medium is one from the group of: sea water, ambient air, ambient air via an intermediate water system, water from a district heating grid.
5. Cogeneration plant according to one of the preceding claims, wherein a second condenser (CON2) is provided
downstream the division module (DMOD) receiving said second combustion gas flow (CB2) to further cool said second
combustion gas flow (CB2) .
6. Cogeneration plant according to claim 5, wherein a
compressor and intercooler system (COCl-COCn, COOl-COOm) is provided downstream said second condenser (CON2) receiving said second combustion gas flow (CB2) to reduce the moisture content by separating water from said second combustion gas flow (CB2), wherein the remaining carbon dioxide is
compressed and cooled to liquid phase.
7. Cogeneration plant according to one of the preceding claims, wherein said compressor (COMP) compresses said combustion gas (CG) up to a pressure (P_OUT_CO) in said combustor (COMB) of between 25 bar - 55 bar.
8. Cogeneration plant according to one of the preceding claims, wherein said heat recovery steam generator (HRSG) cools the combustion gas (CG) down to a
temperature (T_OUT_HRSG) of between 55°C - 85°C, preferably between 65°C - 75°C.
9. Cogeneration plant according to one of the preceding claims, wherein an extraction module (EXT) extracts a flow of cooling steam (STCO) at an extraction point within the expansion of said steam (ST) in the steam turbine (SST) to be supplied to a cooling system (CS) of said gas turbine (GT) as a cooling fluid and, which cooling steam (STCO) is at least partially reunited with the main steam (ST) flow during or after the expansion of the steam (ST) in the steam turbine (STT) downstream the extraction point by means of a feeding module (IN) .
10. Cogeneration plant according to claim 1,
wherein a portion (STGTCO) of the cooling steam (STCO) is partially injected into a hot gas path (HGP) of the gas turbine (GT) for cooling purpose.
11. A method of burning a fuel (F) in a gas turbine cycle of a cogeneration plant for the generation of a combustion gas (CG) utilized for heating water into steam in a steam cycle, the method including the steps of:
in the gas turbine cycle:
- generating said combustion gas (CG) by burning a mixture of said fuel (F), oxygen (02) and re-circulated combustion gas (CBl) in a combustor (COMB),
- expanding said combustion gas (CG) in a gas
turbine (GT) , - heating water into steam (ST) in said steam cycle in a heat recovery steam generator (HRSG) utilizing said combustion gas (CG) as the heating medium,
- compressing a part (CBl) of said combustion gas (CG) re-circulated from said heat recovery steam
generator (HRSG) ,
- supplying a major fraction of said re-circulated combustion gas (CBl) to said combustor (COMB)
and in the steam cycle:
- generating said steam (ST) in said heat recovery steam generator (HRSG) ,
- expanding said steam (ST) in a steam turbine (STT) ,
- condensing said expanded steam into water,
- re-circulating said water to the heat recovery steam generator (HRSG) ,
the method characterized by the steps:
- cooling and/or condensing said combustion gas (CG) downstream said heat recovery steam generator (HRSG) in a condenser (CCON) ,
- supplying at least part of said cooled and/or condensed combustion gas (CG) constituting said re-circulated combusting gas (CBl) to a heater (CHEAT),
- heating and de-liquefying said re-circulated combustion gas (CBl) before said compression.
12. A method according to claim 11, further comprising the steps of:
- condensing in said condenser (CCON) , at least partly, the humid fraction of the combustion gas (CG) into liquid phase (H20),
- separating said liquid phase from the combustion gas (CG) .
13. A method according to any of claims 11 and 12, wherein - said condenser (CCON) is designed to minimize the humid fraction of the combustion gas (CG) , and
- said heater (CHEAT) is designed to increase the
temperature of the re-circulated combustion gas (CBl), such that the maximum temperature T_OUT_CO after said compression is reached so that a predetermined maximum pressure P_OUT_CO is reached for maximum gas turbine cycle efficiency.
PCT/EP2010/060022 2009-07-13 2010-07-13 Cogeneration plant and cogeneration method WO2011006882A2 (en)

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ES10732946.8T ES2559506T3 (en) 2009-07-13 2010-07-13 Cogeneration plant and cogeneration method
MA34525A MA33424B1 (en) 2009-07-13 2010-07-13 COGENERATION PLANT AND COGENERATION METHOD
CN201080031273.2A CN102472120B (en) 2009-07-13 2010-07-13 Cogeneration plant and cogeneration method
US13/383,283 US9657604B2 (en) 2009-07-13 2010-07-13 Cogeneration plant with a division module recirculating with a first combustion gas flow and separating carbon dioxide with a second combustion gas flow
TNP2011000671A TN2011000671A1 (en) 2009-07-13 2011-12-27 Cogeneration plant and method

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US20120137698A1 (en) 2012-06-07
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US9657604B2 (en) 2017-05-23
EP2454454A2 (en) 2012-05-23
MA33424B1 (en) 2012-07-03
TN2011000671A1 (en) 2013-05-24
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EP2454454B1 (en) 2015-10-28
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