EP2435678A1 - Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement - Google Patents

Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement

Info

Publication number
EP2435678A1
EP2435678A1 EP10724002A EP10724002A EP2435678A1 EP 2435678 A1 EP2435678 A1 EP 2435678A1 EP 10724002 A EP10724002 A EP 10724002A EP 10724002 A EP10724002 A EP 10724002A EP 2435678 A1 EP2435678 A1 EP 2435678A1
Authority
EP
European Patent Office
Prior art keywords
fluid
air
intake air
heat exchanger
ansauglufttemperiereinrichtung
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP10724002A
Other languages
German (de)
English (en)
Inventor
Erich Schmid
Daniel Hofmann
Michael SCHÖTTLER
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
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 AG filed Critical Siemens AG
Priority to EP10724002A priority Critical patent/EP2435678A1/fr
Publication of EP2435678A1 publication Critical patent/EP2435678A1/fr
Withdrawn legal-status Critical Current

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
    • 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
    • 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
    • F02C6/14—Gas-turbine plants having means for storing energy, e.g. for meeting peak loads
    • 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
    • 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
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/04—Air intakes for gas-turbine plants or jet-propulsion plants
    • F02C7/047—Heating to prevent icing
    • 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
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/08—Heating air supply before combustion, e.g. by exhaust gases
    • 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
    • F02C7/00—Features, components parts, details or accessories, not provided for in, or of interest apart form groups F02C1/00 - F02C6/00; Air intakes for jet-propulsion plants
    • F02C7/12—Cooling of plants
    • F02C7/14—Cooling of plants of fluids in the plant, e.g. lubricant or fuel
    • F02C7/141—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid
    • F02C7/143—Cooling of plants of fluids in the plant, e.g. lubricant or fuel of working fluid before or between the compressor stages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2230/00—Manufacture
    • F05D2230/50—Building or constructing in particular ways
    • F05D2230/52—Building or constructing in particular ways using existing or "off the shelf" parts, e.g. using standardized turbocharger elements

Definitions

  • the invention relates to a Ansaug Kunststofftemperier Nurs, in particular for a gas and steam turbine plant, and a method for operating such a device and in particular relates to an improved peak load operation of a combined cycle power plant.
  • the intake air can be cooled by evaporative cooling in front of the gas turbine.
  • the effectiveness of this method depends on the humidity and only leads to a limited increase in performance. Also disadvantageous are the associated water requirements or water losses.
  • the power penalty due to high ambient temperatures in the gas turbine can be compensated by a heat recovery steam generator auxiliary firing.
  • the disadvantages of this solution are the additional production costs, the reduction in efficiency and the oversizing of the water-steam cycle, the steam turbine and, if there is no single-shaft system, the steam turbine generator. Basically, performance losses can of course be compensated by the use of reserve power. Additional gas and steam turbine plant and aggregates, however, lead to high costs with a comparatively short service life.
  • the intake air of the gas turbine can be cooled by conventional refrigerators.
  • the chillers themselves use a lot of electricity. The process does not lead to a noticeable increase in performance.
  • the object of the invention is to improve the peak load operation of a gas turbine plant, in particular a gas and steam turbine plant, so that a high performance is achieved with high efficiency.
  • a reservoir for a fluid for heat transfer can be thermally connected to the circuit, the following is achieved:
  • a fluid is now made available via the reservoir, with which the temperature of the intake air can be influenced via the already existing intake air preheating system.
  • the intake air preheating system can also be used for cooling in the same way as the air is preheated.
  • the memory is thermally connectable to the circuit by a first fluid line branches off from the memory and opens into the circuit and a second fluid line branches off the circuit and opens into the memory.
  • the fluid is in this case added directly into the intake air preheating system and can influence the temperature of the intake air for a gas turbine via the heat exchanger of the intake air preheating system.
  • a heat exchanger is connected in the circuit and connected via a first and a second fluid line to the memory.
  • the fluid forms a separate circuit with storage and heat exchanger and the circuit of the intake air preheating remains unchanged.
  • the heated by the heat exchange with the intake air fluid may conveniently be cooled again by an air-fluid heat exchanger on the one hand in a storage circuit and on the other hand connected to a branching off of a compressor air line, the storage circuit, the memory, one between the first and the second fluid line connected third fluid line, and portions of the first and second fluid line from the memory to the third fluid line comprises.
  • At least one further heat exchanger for cooling the air in the branching off of the compressor air duct in the flow direction of the air is preferably connected upstream of the air-fluid heat exchanger.
  • the further heat exchanger can be connected, for example, in the water-steam cycle of a gas and steam turbine plant and used for warming feed water.
  • a pressure-reducing valve is advantageously connected between the further heat exchanger and the air-fluid heat exchanger in the air line.
  • an air expansion turbine can be connected between the further heat exchanger and the air-fluid heat exchanger in the air line.
  • the heat transfer fluid is a mixture of water and cryoprotectant (eg, glycol or ethanol).
  • cryoprotectant eg, glycol or ethanol
  • the Ansaug Kunststofftemperier beautifully is part of a gas turbine plant or a gas and steam turbine nenstrom.
  • a fluid for heat transfer from a memory is emptied and fed to the intake air preheating system for changing the temperature of an intake air.
  • compressor air is advantageously used, which itself must first be cooled. It is advantageous if compressed compressor air is cooled in heat exchange with water, for example medium pressure or low pressure feed water of a water-steam cycle of a gas and steam turbine plant.
  • a throttle relaxes the cooled compressor air.
  • the Storm station and also the Stromerlös least.
  • part of the energy generated can now be converted into cold fluid, for example, and stored, which provides additional power output during the day with high electricity revenue.
  • the gas and steam turbine plant is similar to a storage power plant, which consumes electricity at low electricity prices and can generate additional electricity at high electricity revenue, without changing the nominal power.
  • the cooling of the intake air eg from approx. +40 0 C to +10 0 C, increases the output by 15-20%.
  • the technical equipment effort is less than with a solution with conventional refrigeration machines and also the efficiency of the system (in particular with expansion turbine) is significantly higher.
  • the intake air preheating system which is usually required in any case, is also used for cooling at high outside temperatures and can therefore be used much more economically.
  • the device can significantly reduce the need for auxiliary steam for the so-called anti-icing operation of the gas turbine even in winter or generally at low ambient temperatures by hot water storage, wherein the memory is also discharged via the intake air preheating system.
  • a combination of low outside temperatures and high relative humidity values results in a greatly increased risk of icing up the intake system and the entire gas turbine.
  • the risks include icing of the filters and the consequent reduction or blocking of the air supply.
  • the former leads to reduced performance, the latter indicates standstill of the plant.
  • the addition of antifreeze prevents freezing of the water during heat exchange with cold intake air. The required for heating the mixture of water and antifreeze
  • Heat is taken, for example, from the steam systems of the water-steam circuit of a gas and steam turbine plant.
  • the stored hot water can also significantly increase plant efficiency during part-load operation.
  • the heating and cooling of buildings and room units can be done with the help of cold or hot water storage in a simple manner.
  • the memory can also be cooled and heated in parallel if necessary.
  • FIG. 1 shows a gas turbine plant and a current gas turbine intake air preheating system
  • FIG. 2 shows an intake air tempering device with direct thermal coupling by feeding the fluid from the reservoir into the intake air preheating system
  • FIG. 3 shows an intake air tempering device with indirect thermal coupling via a heat exchanger
  • FIG. 4 shows the production of cold fluid with throttle valve in the compressor air line
  • FIG. 5 shows the generation of cold fluid with a relaxation turbine in the compressor air line
  • Figure 7 shows the use of the memory of Ansaug Kunststofftemperier- device as a heat storage.
  • the gas turbine plant 1 shows schematically and by way of example a gas turbine plant 1 and a current gas turbine intake air preheating system 2 of a gas and steam turbine plant.
  • the gas turbine plant 1 is equipped with a gas turbine 3, a compressor 4 and at least one combustion chamber 5 connected between the compressor 4 and the gas turbine 3.
  • the compressor 4 By means of the compressor 4, fresh air is sucked in via the intake air line 6, compressed and fed via the fresh air line 7 to one or more burners 8 of the combustion chamber 5.
  • the supplied air is mixed with supplied via a fuel line 9 liquid or gaseous fuel and ignited the mixture.
  • the resulting combustion exhaust gases form the working medium of the gas turbine plant 1, which is supplied to the gas turbine 3, where it performs work under relaxation and drives a coupled to the gas turbine 3 shaft 10.
  • the shaft 10 is coupled with the gas turbine 3 and with the air compressor 4 and a generator 11 to drive them.
  • the intake air preheating system 2 consists of a heat exchanger 12 which is connected on the one hand to the intake air line 6 and, on the other hand, is connected to a circuit 13 of the intake air preheating system 2 in which a fluid is circulated by a circulating pump 14.
  • a steam flowing through the further heat exchanger 15 heats the circulating fluid and condenses in the process.
  • the resulting condensate is removed via the pump 17.
  • the heated fluid in turn discharges the absorbed heat in the heat exchanger 12 to the intake air in the intake air line 6.
  • FIG. 2 shows a Ansaug Kunststofftemperier thanks 18 according to a first embodiment of the invention with direct feed of a cold fluid in the intake air preheating system 2.
  • the fluid may be, for example, water, an antifreeze or a mixture of water and antifreeze.
  • the cold fluid is fed directly into the intake air preheating system 2 from a reservoir 19 via a first fluid line 20.
  • the cold fluid passes through a bypass 21 on the heat exchanger 15, which usually heats the fluid of the intake air preheating system 2, and passes to the heat exchanger 12, which is connected in the intake air line 6.
  • the cold fluid absorbs heat from the intake air, cools it and is then pumped back into the reservoir 19 via a second fluid line 22.
  • the memory 19 can be decoupled from the intake air preheating system 2 as needed.
  • FIG. 3 shows an intake air tempering device 18 according to a second embodiment of the invention with indirect cooling of the fluid circulating in the intake air preheating system 2.
  • a heat exchanger 23 is connected on the one hand in the circuit 13 of the intake air preheating system 2 and on the other hand between the first 20 and second fluid line 22.
  • valves 24, 25 in the first 20 and the second fluid line 22 are closed.
  • a third fluid line 26 connects the first fluid line 20 to the second fluid line 22 and leads via a heat exchanger 27, through which cold air flows on the secondary side.
  • a pump 28 ensures a continuous circulation and further cooling of the fluid in the circuit 66.
  • the cooled fluid with eg up to -40 0 C is stored in the memory 19. Depending on the design, this day container can hold up to 1000m3, for example.
  • FIGS. 4 and 5 show how the cold air is generated for the cooling of the fluid.
  • Hot compressed air 29 from the gas turbine compressor 4 is cooled in heat exchange with water from the water-steam cycle, at the same time increasing the production of steam in the waste heat steam generator.
  • a heat exchanger 30 for medium-pressure feedwater 31 and a heat exchanger 32 for condensate 33 are connected in the compressor air line 34 for this purpose.
  • This cold air cools the fluid via the heat exchanger 27 known from FIGS. 2 and 3 and is subsequently fed to a chimney 41 (see FIG. 6) 65.
  • the chilled air can also be used in a cooling circuit for generator cooling or in the condenser become.
  • the refrigeration could also be done with conventional chillers.
  • FIG. 6 shows a gas and steam turbine plant 38.
  • the hot exhaust gases of the gas turbine plant 1 are supplied to the waste heat steam generator 40 through the exhaust gas line 39 and flow through them until they reach the environment through a chimney 41.
  • the heat recovery steam generator 40 On their way through the heat recovery steam generator 40, they pass their heat to a high pressure superheater 42, then a high pressure reheater 43, a high pressure evaporator 44, a high pressure preheater 45, then a medium pressure superheater 46, a medium pressure evaporator 47, a medium pressure preheater 48, then a low pressure superheater 49, a low pressure evaporator 50 and finally a condensate preheater 51.
  • the shaft 10 and thus the generator 11 moves to generate electrical energy.
  • the partially relaxed in the high-pressure stage 53 hot steam is then fed to the high-pressure reheater 43, reheated there and fed via a derivative 55 and a steam supply to a medium-pressure stage 56 of the steam turbine 54 and relaxed there under the power of mechanical work.
  • the partially relaxed steam there is fed via a supply line 57 together with the low-pressure steam from the low-pressure superheater 49 to a low-pressure stage 58 of the steam turbine 54, where it is further expanded while releasing mechanical energy.
  • the expanded steam is condensed in the condenser 59, and the resulting condensate is a condensate pump 60 directly to a low pressure stage 61 of the heat recovery steam generator 40 or via a feed pump 62, and provided by this with a corresponding pressure, a medium-pressure stage 63 or a High-pressure stage 64 of the heat recovery steam generator 40 is supplied, where the condensate is evaporated.
  • a steam discharge and overheating of the steam via the corresponding derivatives of the heat recovery steam generator 40 is fed back to the steam turbine 54 for relaxation and performing mechanical work.
  • FIG. 7 shows the alternative use of the memory 19 as
  • Heat storage The fluid stored in the reservoir 19 is pumped by a pump 28 into the intake air preheating system 2.
  • the line 26 via the air-fluid heat exchanger 27 and the bypass line 21 are closed in this case.
  • the heating of the fluid takes place in the heat exchanger 15 with steam from the water-steam cycle 16 of the gas and steam turbine plant 38.
  • the heated fluid is then not passed through the heat exchanger 12, but directly via the line 67 back into the memory 19th directed.
  • the fluid For storing out the heat, i. for warming up the intake air, the fluid is pumped from the reservoir 19 into the intake air preheating system 2 and passed through the intake air heat exchanger 12 shown in Figs.

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)

Abstract

La présente invention concerne un dispositif (18) de thermorégulation de l'air d'admission comprenant, d'une part, un échangeur de chaleur (12) qui, monté dans une conduite (6) d'air d'admission, est d'autre part monté dans un circuit (13) d'un système (2) de préchauffage de l'air d'admission, un accumulateur (19) pour un fluide de transmission de chaleur pouvant être thermiquement relié au circuit (13). L'invention concerne un procédé de fonctionnement d'un dispositif (18) de thermorégulation de l'air d'admission.
EP10724002A 2009-05-28 2010-05-25 Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement Withdrawn EP2435678A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP10724002A EP2435678A1 (fr) 2009-05-28 2010-05-25 Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP09161355A EP2256316A1 (fr) 2009-05-28 2009-05-28 Dispositif d'équilibrage des températures de l'air d'aspiration et procédé de fonctionnement d'un tel dispositif
PCT/EP2010/057161 WO2010136454A1 (fr) 2009-05-28 2010-05-25 Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement
EP10724002A EP2435678A1 (fr) 2009-05-28 2010-05-25 Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement

Publications (1)

Publication Number Publication Date
EP2435678A1 true EP2435678A1 (fr) 2012-04-04

Family

ID=41413348

Family Applications (2)

Application Number Title Priority Date Filing Date
EP09161355A Withdrawn EP2256316A1 (fr) 2009-05-28 2009-05-28 Dispositif d'équilibrage des températures de l'air d'aspiration et procédé de fonctionnement d'un tel dispositif
EP10724002A Withdrawn EP2435678A1 (fr) 2009-05-28 2010-05-25 Dispositif de thermorégulation de l'air d'admission et procédé de fonctionnement

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP09161355A Withdrawn EP2256316A1 (fr) 2009-05-28 2009-05-28 Dispositif d'équilibrage des températures de l'air d'aspiration et procédé de fonctionnement d'un tel dispositif

Country Status (5)

Country Link
US (1) US20120067057A1 (fr)
EP (2) EP2256316A1 (fr)
KR (1) KR20120026569A (fr)
CN (1) CN102449288B (fr)
WO (1) WO2010136454A1 (fr)

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US8505309B2 (en) * 2011-06-14 2013-08-13 General Electric Company Systems and methods for improving the efficiency of a combined cycle power plant
DE102012202575A1 (de) * 2012-02-20 2013-08-22 Siemens Aktiengesellschaft Gaskraftwerk
CN103061886A (zh) * 2012-07-24 2013-04-24 陈大兵 一种加热燃气轮机进气的系统和方法
US9410451B2 (en) * 2012-12-04 2016-08-09 General Electric Company Gas turbine engine with integrated bottoming cycle system
WO2014130817A1 (fr) * 2013-02-21 2014-08-28 United Technologies Corporation Élimination de glace non homogène d'un système d'alimentation en combustible
US10914200B2 (en) 2013-10-31 2021-02-09 General Electric Technology Gmbh Combined cycle power plant with improved efficiency
EP3023614A1 (fr) * 2014-11-20 2016-05-25 Siemens Aktiengesellschaft Appareil et procédé de refroidissement ou de chauffage de l'entrée d'air d'une turbine à gaz
MX2019007623A (es) * 2016-12-22 2019-09-05 Siemens Ag Planta generadora con sistema de aire de admision de turbina de gas.
DE102017223705A1 (de) * 2017-12-22 2019-06-27 E.On Energy Projects Gmbh Kraftwerk
DE102019210737A1 (de) 2019-07-19 2021-01-21 Siemens Aktiengesellschaft Gasturbine mit thermischem Energiespeicher, Verfahren zum Betreiben und Verfahren zur Modifikation

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US5203161A (en) * 1990-10-30 1993-04-20 Lehto John M Method and arrangement for cooling air to gas turbine inlet
JPH08151933A (ja) * 1994-09-28 1996-06-11 Toshiba Corp ガスタービン吸気冷却装置
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Also Published As

Publication number Publication date
EP2256316A1 (fr) 2010-12-01
US20120067057A1 (en) 2012-03-22
CN102449288B (zh) 2014-12-31
WO2010136454A1 (fr) 2010-12-02
CN102449288A (zh) 2012-05-09
KR20120026569A (ko) 2012-03-19

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