WO2015088487A1 - Agencement d'échange thermique à haut rendement pour une centrale électrique à cycle combiné oxy-combustible - Google Patents

Agencement d'échange thermique à haut rendement pour une centrale électrique à cycle combiné oxy-combustible Download PDF

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Publication number
WO2015088487A1
WO2015088487A1 PCT/US2013/073972 US2013073972W WO2015088487A1 WO 2015088487 A1 WO2015088487 A1 WO 2015088487A1 US 2013073972 W US2013073972 W US 2013073972W WO 2015088487 A1 WO2015088487 A1 WO 2015088487A1
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WO
WIPO (PCT)
Prior art keywords
exhaust
oxy
heat
combined cycle
heat exchange
Prior art date
Application number
PCT/US2013/073972
Other languages
English (en)
Inventor
Theodore James Mallinson
Prasanth CHANDRAHASAN
Original Assignee
Siemens Energy, Inc.
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 Energy, Inc. filed Critical Siemens Energy, Inc.
Priority to PCT/US2013/073972 priority Critical patent/WO2015088487A1/fr
Publication of WO2015088487A1 publication Critical patent/WO2015088487A1/fr

Links

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
    • F01K21/047—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 having at least one combustion gas turbine
    • 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
    • F01K25/00—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for
    • F01K25/005—Plants or engines characterised by use of special working fluids, not otherwise provided for; Plants operating in closed cycles and not otherwise provided for the working fluid being steam, created by combustion of hydrogen with oxygen
    • 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
    • F01K9/00—Plants characterised by condensers arranged or modified to co-operate with the engines
    • F01K9/003—Plants characterised by condensers arranged or modified to co-operate with the engines condenser cooling circuits
    • 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
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]
    • 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

  • the invention relates to oxygen-fuel (oxy-fuel) gas turbine powered combined cycle power plants (CCPP).
  • CCPP oxygen-fuel gas turbine powered combined cycle power plants
  • the invention relates to improved capture of latent heat energy present in the gas turbine engine's exhaust stream.
  • HRSG heat recovery steam generator
  • the exhaust from the gas turbine engine that enters HRSG will be a mixture of nitrogen, carbon dioxide, unburned oxygen, and water vapor. After heat transfer occurs in the HRSG the exhaust is vented to the atmosphere.
  • This type of combined cycle power plant known as an oxy-fuel combined cycle power plant, generally has a reduced amount of, or no nitrogen in the exhaust. In some instances the emissions from an oxy-fuel plant are essentially limited to carbon dioxide and water vapor. Both constituents may be considered valuable and often either or both are captured for other uses.
  • a HRSG removes sensible heat and latent heat from the exhaust.
  • Sensible heat exchanged is that which brings about a change in temperature.
  • Latent heat exchanged is that which occurs during a constant temperature process but with a change of phase.
  • Water vapor is characterized by an anomalously high latent heat of vaporization when compared to other constituents in the exhaust.
  • the fraction of water vapor present in the exhaust of a conventional CCPP is significantly smaller than the fraction of water vapor present in the exhaust of an oxy-fuel CCPP.
  • the exhaust that leaves the HRSG in a conventional plant may still be at a temperature that permits water vapor to exist, because there is so little water vapor the lost heat energy has been deemed tolerable.
  • the exhaust that leaves the HRSG in an oxy-fuel plant can be rich in water vapor and hence the heat worth capturing. This has conventionally been accomplished by positioning an exhaust condenser at the exit of the exhaust stack which receives the exhaust from the HRSG.
  • FIG. 1 is a schematic view of a HRSG and an exemplary embodiment of a heat exchange arrangement.
  • FIG. 2 is a schematic view of an exemplary embodiment of coils of the heat exchange arrangement of FIG. 1 .
  • FIG. 3 is a schematic view of a HRSG and an alternate exemplary embodiment of a heat exchange arrangement.
  • FIG. 4 is a schematic view of a HRSG and another alternate exemplary embodiment of a heat exchange arrangement.
  • FIG. 5 is a schematic view of a HRSG and another alternate exemplary embodiment of a heat exchange arrangement.
  • FIG. 6 is a schematic view of a HRSG and another alternate exemplary embodiment of a heat exchange arrangement.
  • FIG. 7 is a table illustrating additional heat duty.
  • FIG. 8 is a table illustrating the effect of condensation on the overall heat transfer area of the exhaust condenser.
  • CCPPs combined cycle power plants
  • the latent heat of this remaining water vapor that has exited the HRSG, (which feeds the exhaust stack), represents a significant amount of the heat energy created by the CCPP and may even be greater than the amount of energy removed by the HRSG.
  • the total heat present in the exhaust exiting the HRSG is about 349 MW. Out of this about 25 MW is superheat and 324 MW is latent heat.
  • the superheat is only about 7.7% of the total heat content of the exhaust leaving the HRSG, while the latent heat is about 92.3%.
  • the 324 MW also represents a majority of the energy output of the 500 MW CCPP.
  • Such an exhaust condenser may therefore have a duty of approximately 300 MW (approximately 1 ,000 MMBtu).
  • the required exhaust condenser is thus very large, and it is difficult and expensive to lift such a large exhaust condenser to the required elevation.
  • a heat exchange arrangement could be disposed directly within the exhaust stack and used to capture the latent heat in the exhaust.
  • Most exhaust stacks enclose a volume sufficiently large to permit placing a heat exchange arrangement therein with enough capacity to condense most, if not all of the water vapor.
  • the heat exchange arrangement cannot condense all of the water vapor an exhaust condenser can still be placed at the exit of the exhaust stack to finish the condensation.
  • this exhaust condenser can be substantially smaller, making is much less difficult and less expensive to install.
  • the savings gained by eliminating or downsizing the exhaust condenser offsets the cost of the in-stack heat exchange arrangement and so a cost savings is realized. While the exemplary embodiments discussed herein include oxy-fuel turbines, the same principles can be applied to conventionally powered (air and fuel) turbines.
  • the heat exchange arrangement may not be able to extract as much latent and sensible heat from the exhaust in the exhaust stack in a conventional CCPP. Nonetheless, some heat may be extracted and thus may be appropriate in certain circumstances.
  • FIG. 1 shows a portion of a combined cycle power plant 10 including a HRSG 12 and an exhaust stack 14 typically found in a conventional CCPP (not shown).
  • a horizontal HRSG 12 is shown, but the concepts can be applied equally well to a vertical HRSG.
  • the HRSG 12 includes heat exchanging coils 16 used to transfer heat present in exhaust 18 from a gas turbine engine (not shown) to a working fluid 20 used to drive at least one primary steam turbine (not shown).
  • This working fluid 20 may be water and the heat transferred in the HRSG 12 may cause the working fluid 20 to boil and form steam that is used to drive the primary turbine.
  • the exhaust 18 upon exiting the HRSG 12 the exhaust 18 enters the exhaust stack 14 and is vented to the atmosphere without any further processing. However, in the present exhaust processing arrangement 10 the exhaust 18 is further processed in the exhaust stack 14 via a heat exchange arrangement 30.
  • a heat exchange arrangement 30 may manifest itself in any of multiple exemplary embodiments and may condense any amount of the water vapor up to and including 100% of it. In practice it is believed that a heat exchange arrangement may be configured to condense
  • the heat exchange arrangement 30 includes coil arrangement 32 disposed in the exhaust stack 14.
  • a cooling medium 34 is run through the coil arrangement 32 and draws the latent heat from the exhaust 18 in an area of enhanced heat exchange 36.
  • the cooling medium 34 may run concurrent or counter-current to a direction of flow of the exhaust 18, depending on which is deemed more suitable for the specific CCPP.
  • the cooling medium 34 may be working fluid 20 that is preheated before entering the HRSG 12. Such preheating may supplant any other external preheating arrangement and/or may enable additional heating flexibility throughout the CCPP. This will result in a higher log mean temperature difference (LMTD) value.
  • the heat exchange arrangement 30 may further include one or more collection troughs 38 configured to collect condensate 40 as desired and direct the condensate 40 through a condensate outlet 42.
  • FIG. 2 shows an exemplary embodiment of an arrangement for the coil arrangement 32 disposed in the exhaust stack 14.
  • Coils 44 of the coil arrangement 32 traverse the exhaust stack 14 from side to side and may change elevation into and out of the page from a heat exchange coil inlet 50 to a heat exchange coil outlet 52.
  • the heat exchange coil inlet 50 may be at a higher elevation (out of the page) than the heat exchange coil outlet 52 so the cooling medium 34 flows generally counter/against a direction of flow of the exhaust 18.
  • the heat exchange coil inlet 50 may be at a lower elevation (into the page) than the heat exchange coil outlet 52 so the cooling medium 34 flows concurrent generally with a direction of flow of the exhaust 18.
  • This staggered arrangement creates turbulence and this turbulence increases heat transfer efficiency.
  • FIG. 3 shows an alternate exemplary embodiment of the exhaust processing arrangement 10 that includes an exhaust condenser 60 disposed at an exhaust stack outlet 62.
  • the exhaust condenser 60 may be used to supplement the heat exchange arrangement 30 when the heat exchange arrangement 30 within the exhaust stack 14 is unable to condense all of the water vapor in the exhaust 18.
  • the heat exchange arrangement 30 and the exhaust condenser 60 together would condense up to 100% of the water vapor.
  • FIG. 4 shows an alternate exemplary embodiment of the exhaust processing arrangement 10 that includes the coil arrangement 32 in the area of enhanced heat exchange 36 that is part of a discrete, organic Rankine cycle 70.
  • the use of low-boiling Rankine fluid enables heat extraction at lower temperatures which are typical for exhaust 18 exiting the HRSG 12.
  • the organic Rankine fluid is boiled and used to drive a second turbine 72 which may, in turn, drive a second generator 74. After exiting the second turbine 72 the organic Rankine fluid is condensed in a condenser (not shown) and returned to the heat exchange coil inlet 50.
  • FIG. 5 shows an alternate exemplary embodiment of the exhaust processing arrangement 10 that includes a spraying arrangement 80 having injectors 82 configured to inject a medium 84 into the exhaust 18 in the exhaust stack 14.
  • the medium 84 absorbs the latent heat from the exhaust 18 while remaining a liquid. This occurs without a wall separating the two, and hence the heat transfer can be more efficient.
  • the condensate 40 and the medium 84 are collected by the collection trough 38 which is sized and configured to handle the combined volume of the two.
  • the condensate 40 and the medium 84 exit the exhaust stack 14 where the extracted heat may be further utilized.
  • the spraying arrangement 80 may be locally tailored to maximize heat transfer efficiency.
  • the injectors 82 in a first row 86 may be configured to inject relatively larger droplets of the medium 84.
  • the larger droplet may be able to absorb a relatively large amount of heat present in the relatively warmer exhaust 18 entering the spraying arrangement 80 without evaporating. This ensures that the captured heat remains captured and not vented to the atmosphere.
  • the injectors 82 in a second row 88 may be configured to inject medium sized droplets, and the injectors 82 in a third row 90 may be configured to inject relatively smaller droplets. This arrangement considers that the exhaust 18 cools as it travels through the spraying arrangement 80.
  • This arrangement may be altered when consideration is given to other aspects including, for example, the amount of time the droplets are in thermal communication with the exhaust 18.
  • droplets injected by the injectors 82 of the third row 90 may spend more time in the exhaust 18 and thus be prone to absorb more heat, where the opposite may be true for the droplets injected by injectors 82 of the first row 86. Consequently, any amount of localization may be employed to optimize the heat transfer characteristics of the spraying arrangement 80.
  • FIG. 6 shows an alternate exemplary embodiment of the exhaust processing arrangement 10 that includes both the coil arrangement 32 and the spraying arrangement 80. Any combination of these arrangements and any number of each arrangement of any size may be used as necessary to accommodate the specific requirements encountered and desired.
  • Oxy-fuel plant thermal efficiency 28 percent
  • the table of FIG. 7 illustrates the additional heat duty.
  • FIG. 8 illustrates the effect of condensation on the overall heat transfer area of the exhaust condenser. It can be seen that each additional 10% of heat recovered from the HRSG exhaust results in a reduction of overall heat transfer area of the exhaust condenser by 10%.

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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)

Abstract

L'invention concerne une centrale électrique à cycle combiné oxy-combustible (10) comprenant : un générateur de vapeur à récupération de chaleur (HRSG) (12) configuré pour transférer de la chaleur des gaz d'échappement (18) d'un moteur à turbine à gaz à un fluide de travail (20); une cheminée d'échappement (14) configurée pour recevoir les gaz d'échappement du générateur de vapeur à récupération de chaleur (HRSG) ; et un agencement d'échange thermique (30) configuré pour condenser de la vapeur d'eau provenant des gaz d'échappement tandis que les gaz d'échappement circulent dans la cheminée d'échappement, ce qui améliore ainsi la captation de l'énergie thermique latente présente dans le flux d'échappement.
PCT/US2013/073972 2013-12-10 2013-12-10 Agencement d'échange thermique à haut rendement pour une centrale électrique à cycle combiné oxy-combustible WO2015088487A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/US2013/073972 WO2015088487A1 (fr) 2013-12-10 2013-12-10 Agencement d'échange thermique à haut rendement pour une centrale électrique à cycle combiné oxy-combustible

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Application Number Priority Date Filing Date Title
PCT/US2013/073972 WO2015088487A1 (fr) 2013-12-10 2013-12-10 Agencement d'échange thermique à haut rendement pour une centrale électrique à cycle combiné oxy-combustible

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3184757A1 (fr) * 2015-12-21 2017-06-28 Cockerill Maintenance & Ingenierie S.A. Générateur de vapeur à récupération de chaleur de condensation
WO2017108355A1 (fr) * 2015-12-21 2017-06-29 Cockerill Maintenance & Ingenierie S.A. Générateur de vapeur à récupération de chaleur de condensation
US20180058267A1 (en) * 2015-03-31 2018-03-01 Mitsubishi Hitachi Power Systems, Ltd. Boiler, steam-generating plant provided with same, and method for operating boiler
CN115306586A (zh) * 2022-08-02 2022-11-08 北京航天试验技术研究所 一种推进剂贮箱箱压控制装置及其控制方法

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Publication number Priority date Publication date Assignee Title
WO2001090548A1 (fr) * 2000-05-12 2001-11-29 Clean Energy Systems, Inc. Systemes de generation d'energie par turbine a gaz a cycle de brayton semi-ferme
DE102010005259A1 (de) * 2009-01-26 2010-07-29 Metso Power Oy Verfahren bei einem Kraftwerk und ein Kraftwerk
EP2228515A2 (fr) * 2009-03-11 2010-09-15 Hitachi Ltd. Turbine à gaz à deux arbres
WO2011028322A1 (fr) * 2009-09-01 2011-03-10 Exxonmobil Upstream Research Company Systèmes et procédés de génération d'énergie et de récupération d'hydrocarbures à faibles émissions
WO2011093850A1 (fr) * 2010-01-26 2011-08-04 Tm Ge Automation Systems, Llc Système et procédé de récupération d'énergie
WO2014005921A1 (fr) * 2012-07-06 2014-01-09 Siemens Aktiengesellschaft Procédé de génération d'eau à partir du flux d'échappement d'un système de turbine à gaz

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Publication number Priority date Publication date Assignee Title
WO2001090548A1 (fr) * 2000-05-12 2001-11-29 Clean Energy Systems, Inc. Systemes de generation d'energie par turbine a gaz a cycle de brayton semi-ferme
DE102010005259A1 (de) * 2009-01-26 2010-07-29 Metso Power Oy Verfahren bei einem Kraftwerk und ein Kraftwerk
EP2228515A2 (fr) * 2009-03-11 2010-09-15 Hitachi Ltd. Turbine à gaz à deux arbres
WO2011028322A1 (fr) * 2009-09-01 2011-03-10 Exxonmobil Upstream Research Company Systèmes et procédés de génération d'énergie et de récupération d'hydrocarbures à faibles émissions
WO2011093850A1 (fr) * 2010-01-26 2011-08-04 Tm Ge Automation Systems, Llc Système et procédé de récupération d'énergie
WO2014005921A1 (fr) * 2012-07-06 2014-01-09 Siemens Aktiengesellschaft Procédé de génération d'eau à partir du flux d'échappement d'un système de turbine à gaz

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MAKANSI J: "GAS TURBINES GRAB WIDER SHARE OF POWER GENERATION DUTIES", POWER, MCGRAW-HILL COMPAGNY, NEW YORK, NY, US, vol. 134, no. 3, 1 March 1990 (1990-03-01), pages 40 - 42,44, XP000116492, ISSN: 0032-5929 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180058267A1 (en) * 2015-03-31 2018-03-01 Mitsubishi Hitachi Power Systems, Ltd. Boiler, steam-generating plant provided with same, and method for operating boiler
US10844753B2 (en) * 2015-03-31 2020-11-24 Mitsubishi Hitachi Power Systems, Ltd. Boiler, steam-generating plant provided with same, and method for operating boiler
EP3184757A1 (fr) * 2015-12-21 2017-06-28 Cockerill Maintenance & Ingenierie S.A. Générateur de vapeur à récupération de chaleur de condensation
WO2017108355A1 (fr) * 2015-12-21 2017-06-29 Cockerill Maintenance & Ingenierie S.A. Générateur de vapeur à récupération de chaleur de condensation
BE1025812B1 (fr) * 2015-12-21 2019-10-25 Cockerill Maintenance & Ingenierie S.A. Generateur de vapeur a recuperation de chaleur à condensation
CN115306586A (zh) * 2022-08-02 2022-11-08 北京航天试验技术研究所 一种推进剂贮箱箱压控制装置及其控制方法

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