EP0915233B1 - Centrale hybride d'énergie - Google Patents

Centrale hybride d'énergie Download PDF

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Publication number
EP0915233B1
EP0915233B1 EP97810827A EP97810827A EP0915233B1 EP 0915233 B1 EP0915233 B1 EP 0915233B1 EP 97810827 A EP97810827 A EP 97810827A EP 97810827 A EP97810827 A EP 97810827A EP 0915233 B1 EP0915233 B1 EP 0915233B1
Authority
EP
European Patent Office
Prior art keywords
steam
steam generator
feedwater
heat
power plant
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.)
Expired - Lifetime
Application number
EP97810827A
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German (de)
English (en)
Other versions
EP0915233A1 (fr
Inventor
Mircea Fetescu
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.)
General Electric Switzerland GmbH
Original Assignee
Alstom Schweiz 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 Alstom Schweiz AG filed Critical Alstom Schweiz AG
Priority to DE59709579T priority Critical patent/DE59709579D1/de
Priority to EP97810827A priority patent/EP0915233B1/fr
Priority to IL12680098A priority patent/IL126800A/en
Publication of EP0915233A1 publication Critical patent/EP0915233A1/fr
Application granted granted Critical
Publication of EP0915233B1 publication Critical patent/EP0915233B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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

Definitions

  • the present invention relates to the field of Power plant technology. It relates to a hybrid power plant, comprehensively a steam turbine driving a first generator, which optionally with steam from a fuel-operated Steam generator and / or with steam from a waste heat steam generator can be operated, as well as a second generator driving gas turbine, at the outlet of the heat recovery steam generator is arranged and from the hot combustion gases the gas turbine is flowed through, as well as a feed water tank, in which that from the steam turbine’s exhaust steam returned condensate formed in a condenser, and from which feed water for steam generation to the Steam generator or the waste heat steam generator is released, the condensate before being returned to the feed water tank and the feed water before delivery to the steam generator be preheated.
  • Such a hybrid power plant is e.g. from DE-A1-195 42 917 known.
  • the hybrid power plant 10 includes the conventional steam circuit with a steam turbine 24 several stages 25, .., 27 and one via the turbine shaft 29 coupled generator 28, a steam generator 11, a Feed water tank 35 and a condenser 34.
  • the feed water is from the feed water tank 35 by means of a Feed water pump 36 via the feed water supply line 38
  • Steam generator 11 supplied, usually with coal, oil or gas is fired via a fuel supply 13 in a burner 12 arrives and is burned there, the smoke gases are discharged through a flue gas outlet become.
  • the feed water is in the steam generator 11 as it passes through several at different temperature levels Heat exchanger 15, .., 17 heated and converted into steam, the as live steam via a live steam line 20 of a high pressure stage 25 of the steam turbine 24 is fed and there under Performing work in a first step is relaxed becomes.
  • the steam passes from the outlet of the high pressure stage 25 either via the bypass line 23 with the valve 22 open directly to the entrance of a subsequent medium pressure stage 26, or is first with valves 19 and 21 open sent through a further heat exchanger 18 and reheated there. After a further relaxation in the medium pressure stage The steam becomes 26 in a subsequent low pressure stage 27 finally relaxed to its ultimate pressure and converted to condensate in a condenser 34.
  • the Condensate is discharged from a condensate pump 37 via a condensate line 41 transported back into the feed water tank 35.
  • the feed water For preheating the feed water is behind the feed water pump 36 in the feed water supply line 38 at least one regenerative heat exchanger provided as high-pressure preheater 39, which is traversed by steam, which via a sampling steam line 31 from the high pressure stage 25 of the steam turbine 25 is removed.
  • the condensate pump 37 in the condensate line at least two regenerative heat exchangers as Low pressure preheater 42, 43 provided by steam are flowed through, from the medium pressure stage 26 or Low pressure stage 27 via extraction steam lines 32 or 33 is removed.
  • the conventional steam cycle a gas turbine 50 with a to the turbine shaft 56 coupled generator 55 and a heat recovery steam generator 44 added by the hot ones Combustion gases of the gas turbine 50 is flowed through.
  • the heat recovery steam generator 44 becomes feed water, which between the Feed water pump 36 and preheater 39 by means of a feed water supply 40 branched off and the heat recovery steam generator 44 is supplied, heated in several heat exchangers 45, .., 47 and converted into steam, which in addition as live steam or alternatively to live steam from the steam generator 11 via the live steam line 30 to the high pressure stage 25 of the Steam turbine 24 arrives.
  • a further heat exchanger 48 On the low temperature side of the Heat recovery steam generator 44 is a further heat exchanger 48 arranged, in which condensate is preheated, which between the preheaters 42 and 43 by means of a condensate line 41a is branched off.
  • the gas turbine 50 itself includes a turbine 51 and one Compressors 54, which sit on the common shaft 56.
  • the compressor 54 draws in and compresses combustion air for a subsequent burner 52 where the combustion of the via the fuel supply 53 introduced fuel.
  • the hot combustion gases perform in the turbine Work and arrive after passing through the heat recovery steam generator 44 to the outside in an exhaust pipe 49.
  • the task is at a hybrid power plant of the type mentioned kind of solved that for preheating the condensate and the feed water only the hot exhaust gases the gas turbine can be used.
  • the steam turbine can be mounted on the floor because on the usually arranged under the steam turbine Preheater no consideration needs to be taken.
  • the not withdrawn steam can be in the steam turbine with high efficiency be used for power generation.
  • a preferred embodiment of the hybrid power plant according to the Invention is characterized in that in the Heat recovery steam generator is a heat exchanger for preheating the entire feed water and a heat exchanger for preheating of the entire condensate are provided that the Condensate and the feed water for preheating by the corresponding Heat exchanger is routed that the heat exchanger for preheating the condensate on the low temperature side the heat recovery steam generator is arranged, and that the Heat exchanger for preheating the feed water in the heat recovery steam generator further heat exchangers towards the high temperature side for the generation of steam from the preheated feed water are connected downstream.
  • This can cause the heat in the heat recovery steam generator on one compared to steam extraction low energy levels can be recovered.
  • the (big) Preheaters in the heat recovery steam generator work with a low Temperature difference, which - compared to the conventional steam-powered regenerative preheaters - to a lower one Cause loss of exergy.
  • FIG. 2 shows a preferred exemplary embodiment for a hybrid power plant shown schematically.
  • An essential difference of the system diagram shown in FIG. 2 for the system diagram from Fig. 1 is that in Fig. 2 with Extraction steam from the steam turbine 24 operated regenerative Preheaters 39, 42 and 43 are completely omitted, and that the preheating of both the feed water and the Condensate carried out directly in the heat recovery steam generator 44 ' becomes.
  • the waste heat steam generator 44 ' is designed to that it preheats all of the feed water and all of it Condensate can take over. To do this, the associated Low temperature heat exchanger 47 'and 48' in the heat recovery steam generator 44 'compared to the heat exchangers 47 and 48 Fig. 1 is enlarged.
  • the feed water supply line 40 guides the entire feed water from the feed water pump 36 to the entrance of the heat exchanger 47 '. From the exit of the heat exchanger 47 'the preheated feed water is optionally passed directly into the subsequent ones, which are at a higher temperature Heat exchanger 45, 46 and is there in live steam converted, or it passes through the feed water supply 38 to the steam generator 11.
  • the condensate is discharged through the condensate line 41a fully on the entrance of the heat exchanger 48 'guided, preheated in the heat exchanger 48' and then introduced into the feed water tank 35.
  • the total waste heat the gas turbine 50 is used to fully preheat of the entire feed water and condensate and to generate live steam that meets the live steam conditions corresponds to the steam generator 11 and in addition to Steam generator 11 forms a second fresh steam source.
  • operating mode 1 only the conventional steam cycle is used.
  • the gas turbine 50 is not in operation.
  • Corresponding also finds no preheating of the feed water and of the condensate in the heat recovery steam generator 44 '.
  • This operating mode is comparable to operating a CSPP, at which closed the regenerative preheater and steam extraction are. The efficiency is correspondingly lower.
  • This mode is not the normal mode and will be only used if the gas turbine (s) are on schedule or forcibly fail.
  • Preheating the condensate can improve the situation made in the degasser of the feed water tank 35 become.
  • the preheating of the feed water can be done in a special Preheaters are carried out in the steam generator 11, the instead of the heat exchanger 18 for reheating some of the flue gases are supplied.
  • the disadvantage is that associated increased complexity of the steam generator 11.
  • the system In operating mode 2, the system is in the intended hybrid Driving style, with live steam for the steam turbine 24 both by the steam generator 11 and by the heat recovery steam generator 44 'is provided.
  • the system is a pure combination system (CCPP) driven, i.e. the live steam is used exclusively generated in the heat recovery steam generator 44 '. This can cause moisture come in the outlet of the steam turbine 24. This can be done avoid the steam between the medium pressure stage 26 and the low pressure stage 27 of the steam turbine 24 by a heat exchanger or by injection of hot steam is additionally heated in the steam line, or that Steam removed at the entrance to low pressure stage 27 and before the last section of the low pressure stage 27 is added.
  • CCPP pure combination system

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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)

Claims (5)

  1. Centrale d'énergie hybride (10), comprenant une turbine à vapeur (24) entraínant un premier générateur (28), laquelle peut être entraínée au choix par de la vapeur provenant d'un générateur de vapeur (11) fonctionnant avec du combustible, et/ou par de la vapeur provenant d'un générateur de vapeur à chaleur perdue (44'), ainsi qu'une turbine à gaz (50) entraínant un deuxième générateur (55), à la sortie de laquelle est disposé le générateur de vapeur à chaleur perdue (44') qui est parcouru par les gaz de combustion chauds de la turbine à gaz (50), ainsi qu'un réservoir d'eau d'alimentation (35), dans lequel est renvoyé le condensat formé dans un condenseur (34) et provenant de la vapeur évacuée par la turbine à vapeur (24), et duquel l'eau d'alimentation est diffusée pour la production de vapeur au niveau du générateur de vapeur (11) ou au niveau du générateur de vapeur à chaleur perdue (44'), le condensat étant préchauffé avant son retour dans le réservoir d'eau d'alimentation (35), ainsi que l'eau d'alimentation avant sa diffusion au niveau du générateur de vapeur (11), caractérisée en ce que pour le préchauffage du condensat et de l'eau d'alimentation, on utilise exclusivement les gaz d'échappement chauds de la turbine à gaz (50).
  2. Centrale d'énergie hybride selon la revendication 1, caractérisée en ce qu'on prévoit dans le générateur de vapeur à chaleur perdue (44') un échangeur de chaleur (47') pour le préchauffage de toute l'eau d'alimentation, et un échangeur de chaleur (48') pour le préchauffage de tout le condensat, et en ce que le condensat et l'eau d'alimentation sont guidés pour le préchauffage à travers l'échangeur de chaleur correspondant (48', respectivement 47').
  3. Centrale d'énergie hybride selon la revendication 2, caractérisée en ce que l'échangeur de chaleur (48') pour le préchauffage du condensat est disposé du côté basse température du générateur de vapeur à chaleur perdue (44').
  4. Centrale d'énergie hybride selon l'une quelconque des revendications 2 et 3, caractérisée en ce que d'autres échangeurs de chaleur (45, 46) pour la génération de vapeur à partir de l'eau d'alimentation préchauffée sont placés, vers le côté haute température, en aval de l'échangeur de chaleur (47') pour le préchauffage de l'eau d'alimentation dans le générateur de vapeur à chaleur perdue (44').
  5. Centrale d'énergie hybride selon la revendication 4, caractérisée en ce qu'une pompe d'eau d'alimentation (36) est disposée à la sortie du réservoir d'eau d'alimentation (35), en ce que la sortie de la pompe d'eau d'alimentation (36) est connectée à l'entrée de l'échangeur de chaleur (47') pour le préchauffage de l'eau d'alimentation, et en ce que la sortie de l'échangeur de chaleur (47') est raccordée à la conduite d'eau d'alimentation (38) du générateur de vapeur (11).
EP97810827A 1997-11-05 1997-11-05 Centrale hybride d'énergie Expired - Lifetime EP0915233B1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
DE59709579T DE59709579D1 (de) 1997-11-05 1997-11-05 Hybridkraftwerk
EP97810827A EP0915233B1 (fr) 1997-11-05 1997-11-05 Centrale hybride d'énergie
IL12680098A IL126800A (en) 1997-11-05 1998-10-29 Hybrid power plant

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP97810827A EP0915233B1 (fr) 1997-11-05 1997-11-05 Centrale hybride d'énergie

Publications (2)

Publication Number Publication Date
EP0915233A1 EP0915233A1 (fr) 1999-05-12
EP0915233B1 true EP0915233B1 (fr) 2003-03-19

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EP97810827A Expired - Lifetime EP0915233B1 (fr) 1997-11-05 1997-11-05 Centrale hybride d'énergie

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EP (1) EP0915233B1 (fr)
DE (1) DE59709579D1 (fr)
IL (1) IL126800A (fr)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109854316B (zh) * 2019-02-02 2023-09-08 华电电力科学研究院有限公司 一种基于能源梯级利用的联合循环供热与电力调峰耦合系统及其运行方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH645433A5 (de) * 1980-04-11 1984-09-28 Sulzer Ag Kombinierte gasturbinen-dampfkraftanlage.
JPS6017210A (ja) * 1983-07-08 1985-01-29 Hitachi Ltd 複合サイクル発電プラント
JP2750784B2 (ja) * 1991-02-06 1998-05-13 三井造船株式会社 廃熱回収方法
JPH051568A (ja) * 1991-04-18 1993-01-08 Mitsui Eng & Shipbuild Co Ltd ガスタービン・コージエネレーシヨン設備の熱回収システム
JPH06241005A (ja) * 1993-02-17 1994-08-30 Ishikawajima Harima Heavy Ind Co Ltd 複合発電設備
DE19542917A1 (de) 1994-12-21 1996-06-27 Abb Management Ag Kombianlage mit konventionellem Wasser/Dampf-Kreislauf

Also Published As

Publication number Publication date
EP0915233A1 (fr) 1999-05-12
DE59709579D1 (de) 2003-04-24
IL126800A (en) 2002-03-10
IL126800A0 (en) 1999-08-17

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