EP2617952A2 - Dispositif et procédé destinés à la surchauffe intermédiaire de la vapeur de turbine - Google Patents

Dispositif et procédé destinés à la surchauffe intermédiaire de la vapeur de turbine Download PDF

Info

Publication number
EP2617952A2
EP2617952A2 EP12008412.4A EP12008412A EP2617952A2 EP 2617952 A2 EP2617952 A2 EP 2617952A2 EP 12008412 A EP12008412 A EP 12008412A EP 2617952 A2 EP2617952 A2 EP 2617952A2
Authority
EP
European Patent Office
Prior art keywords
condensate
steam
subcooler
reheater
superheater
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Withdrawn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
EP12008412.4A
Other languages
German (de)
English (en)
Inventor
Guido Bonati
Gerd Stuckenschneider
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.)
Balcke Duerr GmbH
Original Assignee
Balcke Duerr GmbH
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 Balcke Duerr GmbH filed Critical Balcke Duerr GmbH
Publication of EP2617952A2 publication Critical patent/EP2617952A2/fr
Withdrawn legal-status Critical Current

Links

Images

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
    • F01K3/00—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein
    • F01K3/18—Plants characterised by the use of steam or heat accumulators, or intermediate steam heaters, therein having heaters
    • 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
    • F01K19/00—Regenerating or otherwise treating steam exhausted from steam engine plant
    • F01K19/02—Regenerating by compression
    • F01K19/04—Regenerating by compression in combination with cooling or heating
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B40/00—Subcoolers, desuperheaters or superheaters
    • F25B40/02—Subcoolers

Definitions

  • the invention relates to a device for the reheating of turbine steam, with a reheater and with a condensate collection tank, in which condensate is passed from the reheater.
  • the invention further relates to a method for reheating a turbine steam in a steam turbine process.
  • Such devices and methods are used in a multi-stage steam turbine process of a steam power plant. They are often combined with a water separator and serve to dry the wet steam exiting the high pressure turbine and reheat the steam, depending on the process, prior to its entry into the medium pressure or low pressure turbines, referred to as reheat.
  • reheat medium pressure or low pressure turbines
  • Combined water separators and reheaters are known from the prior art with a common pressure-resistant container in horizontal or vertical construction, in which two strictly separate circuits of heat-absorbing water or water vapor on the one hand and a heat-emitting medium, such as flue gas, helium, water or water vapor or Thermal oil or molten salt are arranged at not directly evaporating solar systems on the other.
  • Generic devices are in DE 23 14 732 A .
  • US 4,607,689 A US 4,015,562 A and US 3,574,303 A disclosed.
  • the invention is based on the object to provide a device and a method of the type mentioned, which has an improved efficiency and leads to improved efficiency.
  • a condensate subcooler is present in a common housing with the reheater that the condensate subcooler with the condensate collecting tank is connected to use the condensate collecting tank for preheating the turbine steam, that the subcooler is disposed below the reheater, and that the condensate collecting tank is connected to the subcooler to supply condensate from the condensate collecting tank as a heating medium for preheating the turbine steam.
  • the subcooler works like a first superheater stage. On a condensate pump can be omitted.
  • the object is achieved in that condensate is discharged along the flow path of the heating steam in a superheater from the superheater into a condensate tank, wherein the discharge can take place at spaced locations along the flow path at which the heating steam has different pressures.
  • Condensate streams with different pressure levels can be guided by siphons into a common condensate tank.
  • the condensate collected in the container may serve as a heating medium for the subcooler to preheat the turbine steam upstream of the steam heated superheater.
  • the reheater is provided on the heating steam side with a first outlet for condensate and downstream of the heating steam with a second outlet for condensate and rinsing steam, so that the heating steam is conducted in four ways through the reheater bundle.
  • a particularly advantageous embodiment of the invention is that the first and second outlet are connected to the condensate collecting tank, preferably according to the principle of the U-tube manometer. Then, even with multiple Walkerdampfheim the total amount of condensate can be used for subcooling.
  • a water separator is arranged upstream of the subcooler.
  • the superheater is located as far above and the subcooler as far down in the pressure-resistant container.
  • the process is particularly simple in that the derived condensate is supplied in free gradient to the condensate subcooler.
  • a condensate pump be waived.
  • a condensate pump is provided to supply condensate to the condensate subcooler.
  • the condensate derived at the various points is preferably fed to the collecting container on the basis of the principle of the U-tube manometer, from which the condensate drains off as the heating medium.
  • Fig. 1 and 2 are located in a common pressure-resistant cylindrical housing 10 lying type a subcooler 11, a water separator 12, and a reheater 13 for turbine steam from the process cycle of a high-pressure steam turbine plant.
  • the subcooler 11 is located upstream of the superheater 13 and downstream of the water separator 12.
  • the interior of the housing 10 is in the longitudinal direction according to Fig. 1 divided into a working space and a distribution space, wherein both are limited at one of the end sides of the housing 10 by a end wall 5.
  • the distribution room takes according to Fig. 1 a frontal area 7 and according to Fig. 2 a extending over the remaining length of the container 10 a region 6, which forms the inflow region of the water separator 12.
  • the region 6 of the distributor space runs along a side longitudinal wall of the housing 10 parallel to the working space. In the illustrated example, it essentially occupies a lateral sector of the cylindrical housing 10.
  • the working space 8 extends substantially over the length of the housing 10 between the end wall 5 and the end wall 4. It has flow-conducting guide surfaces and partitions, with which the turbine steam successively through the water 12, the subcooler 11 and the superheater 13 is performed.
  • the water separator 12 is located with respect to the longitudinal center plane M L of the housing 10 in a lateral region of the housing 10 along the inside of the distributor chamber 6. Instead of the illustrated Wasserabscheiders 12, two symmetrically arranged Wasserabscheider myselfn are possible.
  • the subcooler 11 is thus below the reheater 13 and laterally offset below the water separator 12.
  • the reheater 13 is arranged in the illustrated example in the upper region of the housing 10 with the same lateral offset to the water separator 12 as the subcooler 11. However, an equal lateral offset is not mandatory.
  • wet turbine steam typically with a water content of about 2 to 16%, is introduced into the container 10, which outlet is from a high-pressure turbine (not shown).
  • the turbine steam exits as superheated steam via an outlet 15 at the top of the housing after being dried in the water separator 12 and then heated in the subcooler 11 and superheater 13.
  • the superheater 13 is supplied with a heat-emitting high or low pressure pressure steam via a heating steam inlet 16 for heating.
  • resulting condensate flows are pressure-dependent either directly via the condensate line 33 or condensate loops (eg 34) a separate condensate collection tank 22 outside the housing 10 (FIG. Fig. 2 . Fig. 3 ).
  • the condensate collecting tank 22 is located in front of the housing 10 or in front of the cutting plane and is therefore not reproduced.
  • the superheater 13 comprises a bundle 23 of horizontally extending U-tubes, which extend over the entire length of the working space, and whose ends are connected to a pipe plate 24. Behind the pipe disk 24 there is an inlet chamber 25, into which the heating steam inlet 16 opens, and a separate outlet chamber 26 with the outlet 17.
  • the water separator 12 consists of separator modules 27 with mechanical droplet separators whose surfaces also detect the smallest drops, so that they can be brought together and collected at the bottom.
  • the Abscheidermodule 27 are over the entire length arranged the working space. They form the connection between the distributor space 6 and the working space. Since the water separator 12 is arranged laterally offset from the superheater 11, an outflow region of the dried turbine steam lies below the superheater 11.
  • the turbine steam is guided horizontally through the water separator 12 according to arrow P1.
  • the water removed in the water separator 12 from the turbine steam passes downwards and is discharged via a water outlet 20 in the bottom of the container 10 to the outside.
  • the subcooler 11 consists of a substantially horizontally extending tube bundle 28. It has a subcooler inlet 18 and a subcooler outlet 19, via which condensate is conducted from the condensate collecting tank 22 as heating medium into the tube bundle 28 or removed therefrom as supercooled condensate.
  • the tube bundle 28 extends according to Fig. 1 over the entire length of the working space 8.
  • the subcooler 11 is arranged below the outflow region, which adjoins the water separator 12 laterally and downstream.
  • the outlet space is separated by a partition wall from the rest of the working space 8, which extends in the example shown from the upper edge of the water separator funnel-shaped extending to the opposite edge of the subcooler 11, so that the flow of the emerging from the water separator 12 dried turbine steam according to arrow P2 streamlined in can enter the subcooler 11.
  • the subcooler 11 is open at the bottom, where there is a deflection space 31 which is open after the side facing away from the water separator 12, so that the already superheated turbine steam exiting from the subcooler 11 passes laterally past the subcooler in the remaining working space 8 according to arrow P3 along the partition up to the superheater 13 can move.
  • the turbine steam enters from below into the superheater 13, passes through it from bottom to top, in this case continues to overheat and emerges from the housing 10 according to arrow P4. From there it is fed to a low-pressure turbine (not shown).
  • the condensate collecting tank 22 is formed in the illustrated example as a cylindrical hollow body in a horizontal position. According to Fig. 2 and Fig. 3 the condensate collecting tank 22 is disposed at a height location between the super heater 13 and the subcooler 11. Outlet 17 is connected via a condensate loop with the condensate collection tank 22, which compensates for the differential pressure between the second and fourth way.
  • the outlet 37 of the fourth path of the superheater 13 directly connected to the condensate collection tank 22 is higher than the condensate level of the condensate collection tank 22 and the outlet 35 of the condensate collection tank 22 is above or at least equal to the heating medium inlet 18.
  • the siphon 34 By using the siphon 34, it is possible to guide the condensate flows flowing in from the superheater 13, despite their different pressure levels, into the common condensate collecting tank 22 without a spontaneous evaporation taking place in the condensate collecting tank 22 or cross flows to the superheater 13.
  • the pressure prevailing in the condensate collecting tank 22 corresponds approximately to the pressure at the outlet of the fourth path.
  • the temperature of the condensate collected in the condensate collecting tank 22 results from the saturated steam temperature corresponding to the pressure.
  • the subcooling of the condensate takes place only in the subcooler 11.
  • Fig. 3 illustrates the passage of the heating steam through the superheater 13 and the functional connections of the superheater 13 with the condensate collection tank 22.
  • the condensate drainage takes place at two points with the pressures p pass 2 and p pass 4 .
  • the heating steam flowing into the tube bundle 33 according to the arrow P6 successively passes through the pass 1, pass 2, pass 3 and pass 4 paths, where it releases energy to the turbine steam coming from the subcooler 11 and heats it up.
  • Pass 1 and Pass 2 condenses a portion of the heating steam while heating the turbine steam, whereby a pressure loss in Pass 1 and Pass 2 paths is created.
  • the resulting condensate is discharged through the outlet 17 and passes through the siphon 34 into the condensate collection tank 22.
  • the heating steam in the pass 3 and pass 4 further heats the turbine steam, where it continues to condense, and a pressure Pass 4 is created at the exit of Pass 4.
  • This condensate from the pass Pass 3 and Pass 4 passes with the flushing steam through the condensate line 33 into the condensate collection tank 22.
  • the pressure prevailing in the condensate collection tank 22 pressure corresponds to the pressure p pass 4 , the higher pressure p pass 2 at the end of the second path through the Condensate loop 34 is balanced.
  • the pressure difference ⁇ p between path 2 and path 4 corresponds to the difference between the height of the condensate column in the input-side pipe siphon 34 and the height of the condensate level in the condensate-collecting tank 22.
  • the driving force for the flow through the sub-cooler is the geodetic height in the condensate-collecting tank. A relaxation to a lower pressure level behind the subcooler promotes the flow, but it is not absolutely necessary.
  • the condensate leaves the subcooler 11 as supercooled condensate via the Schumediumauslass 19 and is discharged from the housing 10 to the outside.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
EP12008412.4A 2012-01-20 2012-12-18 Dispositif et procédé destinés à la surchauffe intermédiaire de la vapeur de turbine Withdrawn EP2617952A2 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012001091.5A DE102012001091B4 (de) 2012-01-20 2012-01-20 Vorrichtung und Verfahren zum Zwischenüberhitzen von Turbinendampf

Publications (1)

Publication Number Publication Date
EP2617952A2 true EP2617952A2 (fr) 2013-07-24

Family

ID=47561031

Family Applications (1)

Application Number Title Priority Date Filing Date
EP12008412.4A Withdrawn EP2617952A2 (fr) 2012-01-20 2012-12-18 Dispositif et procédé destinés à la surchauffe intermédiaire de la vapeur de turbine

Country Status (7)

Country Link
US (1) US8997492B2 (fr)
EP (1) EP2617952A2 (fr)
KR (1) KR20130085988A (fr)
CN (1) CN103216816A (fr)
DE (1) DE102012001091B4 (fr)
MA (1) MA35003B1 (fr)
ZA (1) ZA201300346B (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3511536A1 (fr) * 2018-01-10 2019-07-17 General Electric Technology GmbH Système d'échange de chaleur comportant un refroidisseur secondaire intégré

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8797966B2 (en) 2011-09-23 2014-08-05 Ofinno Technologies, Llc Channel state information transmission
US8848673B2 (en) 2011-12-19 2014-09-30 Ofinno Technologies, Llc Beam information exchange between base stations
EP2881691A1 (fr) 2013-12-09 2015-06-10 Balcke-Dürr GmbH Échangeur de chaleur avec une plaque tubulaire et un manchon inséré
CN114110560B (zh) * 2021-10-20 2023-07-21 西安精密机械研究所 一种变结构螺旋盘管锅炉反应器

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3574303A (en) 1968-09-30 1971-04-13 Westinghouse Electric Corp Moisture separator reheater for pressurized vapor
DE2314732A1 (de) 1972-05-01 1973-11-15 Westinghouse Electric Corp Waermeaustauscher
US4015562A (en) 1975-07-25 1977-04-05 Foster Wheeler Energy Corporation Moisture separator and reheater
DE3445609A1 (de) 1984-12-14 1986-06-26 L. & C. Steinmüller GmbH, 5270 Gummersbach Vorrichtung zum trocknen von nassdampf und anschliessendem ueberhitzen des getrockneten dampfes
US4607689A (en) 1982-12-27 1986-08-26 Tokyo Shibaura Denki Kabushiki Kaisha Reheating device of steam power plant

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3744459A (en) * 1971-10-12 1973-07-10 Gen Electric Condensate drain subcooler for moisture separator and reheater
CH569862A5 (fr) * 1973-10-02 1975-11-28 Sulzer Ag
NZ248729A (en) * 1992-10-02 1996-03-26 Ormat Ind Ltd High pressure geothermal power plant with secondary low pressure turbogenerator
US5622605A (en) * 1993-11-05 1997-04-22 Simpson; Gary D. Process for desalinating water while producing power
DE19962403A1 (de) * 1999-12-23 2001-06-28 Alstom Power Schweiz Ag Baden Verfahren zum Umrüsten eines Sattdampf erzeugenden Systems mit mindestens einer Dampfturbogruppe sowie nach dem Verfahren umgerüstetes Kraftwerk

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3574303A (en) 1968-09-30 1971-04-13 Westinghouse Electric Corp Moisture separator reheater for pressurized vapor
DE2314732A1 (de) 1972-05-01 1973-11-15 Westinghouse Electric Corp Waermeaustauscher
US4015562A (en) 1975-07-25 1977-04-05 Foster Wheeler Energy Corporation Moisture separator and reheater
US4607689A (en) 1982-12-27 1986-08-26 Tokyo Shibaura Denki Kabushiki Kaisha Reheating device of steam power plant
DE3445609A1 (de) 1984-12-14 1986-06-26 L. & C. Steinmüller GmbH, 5270 Gummersbach Vorrichtung zum trocknen von nassdampf und anschliessendem ueberhitzen des getrockneten dampfes

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3511536A1 (fr) * 2018-01-10 2019-07-17 General Electric Technology GmbH Système d'échange de chaleur comportant un refroidisseur secondaire intégré
WO2019137923A1 (fr) * 2018-01-10 2019-07-18 General Electric Technology Gmbh Système d'échange de chaleur doté d'un sous-refroidisseur intégré

Also Published As

Publication number Publication date
CN103216816A (zh) 2013-07-24
DE102012001091B4 (de) 2014-10-30
US20140026576A1 (en) 2014-01-30
KR20130085988A (ko) 2013-07-30
MA35003B1 (fr) 2014-04-03
ZA201300346B (en) 2013-09-25
DE102012001091A1 (de) 2013-07-25
US8997492B2 (en) 2015-04-07

Similar Documents

Publication Publication Date Title
EP1848925B1 (fr) Générateur de vapeur de type horizontal
EP1710498A1 (fr) Générateur de vapeur
DE102012001091B4 (de) Vorrichtung und Verfahren zum Zwischenüberhitzen von Turbinendampf
DE102009012322B4 (de) Durchlaufverdampfer
EP2603672A2 (fr) Générateur de vapeur à récupération de chaleur
WO2010029033A2 (fr) Générateur de vapeur à récupération de chaleur
EP1806533A1 (fr) Cycle à vapeur d'une centrale électrique
EP3017152B1 (fr) Centrale à cycle combiné gaz-vapeur munie d'un générateur de vapeur à récupération de chaleur et un pre-chauffage du carburant
EP2721211B1 (fr) Procédé de récupération de chaleur pour une partie sèche d'une machine de fabrication d'une bande de matériau et machine de fabrication d'une bande de matériau
WO2015003898A1 (fr) Système de préchauffage et procédé utilisant un tel système de préchauffage
WO2010102864A2 (fr) Évaporateur continu
EP2409078B1 (fr) Procédé de conception d'un évaporateur continu
DE69717165T2 (de) Verfahren zum betrieb eines zwanglaufdampferzeugers und dampferzeuger zur ausführung des verfahrens
WO2012175461A1 (fr) Procédé et système pour la récupération de chaleur dans une section de séchage d'une machine servant à fabriquer une bande de matière
WO2016188671A1 (fr) Circuit de vapeur d'eau d'une installation de turbine à gaz et à vapeur
EP3224541B1 (fr) Générateur de vapeur à récupération de chaleur
DE10052414A1 (de) Verfahren zum Betreiben einer Energieumwandlungseinrichtung sowie Vorrichtung zur Durchführung eines solchen Verfahrens
DE102011077796A1 (de) Verfahren und System zur Wärmerückgewinnung für eine Trockenpartie einer Maschine zur Herstellung einer Materialbahn
EP1512906A1 (fr) Générateur de vapeur de construction horizontale à passage unique et méthode pour faire fonctionner ledit générateur de vapeur à passage unique
DE1965078B2 (de) Verfahren zum gleitdruckbetrieb eines zwanglaufdampferzeu gers
DE102018002669A1 (de) Entspannungsverdampferanlage
WO2015000701A1 (fr) Installation de séparation de co2 et procédé permettant de faire fonctionner ladite installation
DE102010041962B3 (de) Fossil befeuerter Dampferzeuger
DE1965078C (de) Verfahren zum Gleitdruckbetrieb eines Zwanglauf da mpferzeugers
EP2554805B1 (fr) Dispositif à utilisation de vapeur

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20150701