EP2324285B1 - Générateur de vapeur à récupération de chaleur - Google Patents

Générateur de vapeur à récupération de chaleur Download PDF

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Publication number
EP2324285B1
EP2324285B1 EP09782665.5A EP09782665A EP2324285B1 EP 2324285 B1 EP2324285 B1 EP 2324285B1 EP 09782665 A EP09782665 A EP 09782665A EP 2324285 B1 EP2324285 B1 EP 2324285B1
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EP
European Patent Office
Prior art keywords
tubes
steam generator
waste heat
water separation
flow
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.)
Active
Application number
EP09782665.5A
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German (de)
English (en)
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EP2324285A2 (fr
Inventor
Jan BRÜCKNER
Joachim Franke
Holger Schmidt
Frank Thomas
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
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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.)
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Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to PL09782665T priority Critical patent/PL2324285T3/pl
Priority to EP09782665.5A priority patent/EP2324285B1/fr
Publication of EP2324285A2 publication Critical patent/EP2324285A2/fr
Application granted granted Critical
Publication of EP2324285B1 publication Critical patent/EP2324285B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B15/00—Water-tube boilers of horizontal type, i.e. the water-tube sets being arranged horizontally
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B21/00—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B37/00—Component parts or details of steam boilers
    • F22B37/02—Component parts or details of steam boilers applicable to more than one kind or type of steam boiler
    • F22B37/26—Steam-separating arrangements

Definitions

  • the invention relates to a heat recovery steam generator with a number of evaporator tubes connected in parallel on the flow medium side, through which a number of superheater tubes are connected via a water separation system, wherein the water separation system comprises a number of water separation elements, each of which downstream of a number of evaporator tubes and / or a number of superheater tubes upstream, wherein each of the Wasserabscheideieri comprises a connected to the respective upstream evaporator tubes Einströmrohr mosaic, seen in its longitudinal direction merges into a Wasserableitrohr voting, wherein in the transition region a number of Abströmrohr structurien branches, which are connected to an inlet header of the respective downstream superheater tubes.
  • a heat recovery steam generator is a heat exchanger that recovers heat from a hot gas stream.
  • Heat recovery steam generators are used, for example, in gas and steam turbine power plants, in which the hot exhaust gases of one or more gas turbines are conducted into a heat recovery steam generator. The steam generated therein is then used to drive a steam turbine. This combination produces electrical energy much more efficiently than gas or steam turbine alone.
  • Heat recovery steam generators can be categorized by a variety of criteria: based on the flow direction of the gas flow, heat recovery steam generators can be classified, for example, into vertical and horizontal types. Furthermore, there are steam generator with a plurality of pressure stages with different thermal states of the water-steam mixture contained in each case.
  • Steam generators can generally be designed as natural circulation, forced circulation or continuous steam generators.
  • a continuous steam generator the heating of evaporator tubes leads to a complete evaporation of the flow medium in the evaporator tubes in one pass.
  • the flow medium - usually water - is supplied to the evaporator tubes downstream superheater tubes after its evaporation and overheated there.
  • the position of the evaporation end point, d. H. the point of transition from a flow with residual moisture to pure steam flow, is variable and mode-dependent.
  • the evaporation end point is, for example, in an end region of the evaporator tubes, so that the overheating of the evaporated flow medium already begins in the evaporator tubes.
  • a continuous steam generator In contrast to a natural or forced circulation steam generator, a continuous steam generator is not subject to any pressure limitation, so that it can reach steam pressures far above the critical pressure of water (p crit ⁇ 221 bar) - at which water and steam can not occur simultaneously at any temperature and therefore no phase separation is possible - can be designed.
  • such a continuous steam generator is normally operated with a minimum flow of flow medium in the evaporator tubes during low-load operation or during start-up.
  • the operationally provided minimum flow of flow medium in the evaporator tubes is thus not fully evaporated during startup or during low load operation in the evaporator tubes, so that in such a mode at the end of the evaporator tubes still unevaporated flow medium, d. H. a water-steam mixture are present.
  • the evaporator tubes downstream of the continuous steam generator superheater tubes usually not for a relatively large flow unvaporized flow medium are designed continuous flow steam generators are usually designed so that even when starting and during low load operation excessive water ingress into the superheater pipes is safely avoided.
  • the evaporator tubes are usually connected to the superheater tubes connected downstream via a Wasserabscheidesystem.
  • the water separator causes a separation of the emerging during the start or in low load operation of the evaporator tubes water-steam mixture in water and in steam.
  • the steam is fed to the superheater tubes connected downstream of the water separation system, whereas the separated water can be returned to the evaporator tubes, for example via a circulation pump, or removed via a decompressor.
  • the Wasserabscheidesystem can include a variety of Wasserabscheidemaschinen that are integrated directly into the tubes.
  • each of the parallel-connected evaporator tubes may be assigned a Wasserabscheideelement.
  • the Wasserabscheideetic can continue to be designed as a so-called T-piece Wasserabscheide 1952.
  • each T-piece water separation element in each case comprises an inflow pipe piece connected to the upstream evaporator pipe, which, as seen in its longitudinal direction, merges into a water drainage pipe piece, wherein an outflow pipe piece connected to the downstream superheater pipe branches off in the transition region.
  • the T-piece Wasserabscheideelement is designed for a Trägheitsseparation of the flowing from the upstream evaporator tube in the Einströmrohr Swiss water-steam mixture. Because of its comparatively higher inertia, namely, the water content of the flow medium flowing in the inflow pipe piece flows preferably further in the axial extension of the inflow pipe piece at the transition point and thus passes into the water diverter pipe piece and from there usually continues into a connected collecting container. The vapor content of the inflow pipe section flowing water-steam mixture, however, can better follow a forced deflection due to its relatively lower inertia and thus flows through the Abströmrohr conducted to the downstream superheater pipe section.
  • a designed for continuous operation heat recovery steam generator of this type is for example from the EP 1 701 090 A1 and the EP 1 701 091 A1 known.
  • the transfer of flow medium to the superheater tubes is not only limited to steam, but now a water-steam mixture can be continued to the superheater tubes by the Wasserabscheideieri be fed.
  • the evaporation end point can be pushed into the superheater tubes as needed.
  • the live steam temperature can be controlled in comparatively large limits by influencing the feedwater quantity.
  • This object is achieved according to the invention by arranging a distributor element on the steam side between the respective water separation element and the inlet header of the subsequent heating surface.
  • the invention is based on the consideration that the decentralized separation of water, which takes place separately in each of the parallel-connected evaporator tubes in the construction described above, a comparatively large number of T-piece Wasserabscheideijnn can lead to design problems in large-scale application. Due to the space problems that may be associated with the need to accommodate such a large number of water separation elements, such a construction may also entail significant additional costs and restrictions on the heat recovery steam generator's geometric parameters due to the high design effort involved.
  • a distributor element is arranged on the steam side between the respective Wasserabscheideelement and the inlet header.
  • the distributor element is designed as a star distributor, d. H. it comprises a baffle plate, an inlet tube arranged perpendicular to the baffle plate, and a number of outlet tubes arranged in a star shape around the baffle plate in the plane thereof.
  • the inflowing water impinges on the baffle plate and is distributed in a symmetrical manner perpendicular to the inflow direction and directed into the outlet tubes.
  • the baffle plate in a particularly advantageous embodiment is circular and the exit tubes arranged concentrically to the center of the baffle plate at equal intervals to the respective adjacent outlet tubes. In this way, a particularly homogeneous distribution is ensured on the different outlet pipes.
  • Such turbulent flows can occur in particular in the form of so-called slugs, which are caused by the different flow velocities of vaporized and unevaporated flow medium in the tubes.
  • the result is a wave-like movement that causes a pulsating mass flow, which can lead to mechanical and thermal loads on the Wasserabscheideimplantation and also the downstream superheater tubes.
  • measures should be taken against the further propagation of the turbulence from the evaporator tubes into the T-piece water separator elements and the downstream superheater tubes. This should be done before the water-steam mixture in the T-piece Wasserabscheideetic.
  • a flow turbulence damper is provided in the inflow pipe sections of a number of water separation elements in an advantageous embodiment.
  • the turbulences in the pipe system arise because two different phases of the flow medium flow through the pipe system parallel to one another. At the interface of the two phases, vortices occur at widely differing flow velocities, resulting in a rapid local displacement of the interface between the two phases in the form of a wave-like motion.
  • the flow turbulence dampers in an advantageous embodiment each comprise a number of bulkheads, each of which closes a part of the pipe cross section. The slugs break at the bulkheads, some of the water is held back and distributed to the area following the slug, mainly dominated by steam.
  • the waves are smoothed and pulsation-free operation is achieved by smoothing the wave motions.
  • the direction of oscillation of the wave movements entering the flow turbulence absorbers should be known and predictable.
  • possible swirling movements of the inflowing water-vapor mixture should be suppressed, as these could hinder the operation of the flow turbulence damper.
  • the flow turbulence dampers on the tube inner wall advantageously comprise a number of guide profiles aligned in the main flow direction of the flow medium. Through the guide profiles a possible swirling motion of the water vapor mixture is stopped and the water vapor mixture is introduced in such a geometric position in the flow turbulence damper that they can fulfill their task appropriately.
  • the flow turbulence dampers can be introduced directly during the production of the tubes.
  • the flow turbulence dampers are advantageously made of a material having the same material as the tube or similar composition. This also prevents too high a mechanical stress on the pipes, which would arise with different materials for pipes and flow turbulence dampers and / or the guide profiles by the different thermal expansion properties.
  • the advantages achieved by the invention are in particular that a uniform distribution of the flow medium is achieved on the superheater tubes by the vapor-side arrangement of an additional distribution element between the respective Wasserabscheideelement and the inlet header of the superheater heating even at a much lower number of Wasserabscheideimplantationn.
  • These measures make it possible to reduce the number of water separation elements in the first place. This means a much lower production cost and a comparatively lower complexity of the pipe system of the heat recovery steam generator and it is a particularly high operational flexibility even in start-up or low load operation achievable.
  • FIG. 1 shows the schematic representation of a heat recovery steam generator 1 with horizontal flue gas path.
  • the flow medium M is fed into the pipe system by an upstream feed pump not shown in detail. Initially, it flows into a number of evaporator inlet collectors 2, which ensure the distribution of the flow medium M to four evaporator heating surfaces with evaporator tubes 4, in which then an evaporation of the flow medium takes place.
  • further evaporator heating surfaces may be connected upstream or the heating surfaces may be arranged in different geometrical configurations in the heating gas channel.
  • a number of evaporator tubes 4 opens into a via a first evaporator outlet header 6 and a second outlet header 8 in a common transition pipe section 10, which is the T-piece Wasserabscheideelement 12 downstream.
  • the T-piece Wasserabscheideelement comprises a Einströmrohr laminate 14, which is seen in its longitudinal direction merges into a Wasserableitrohr laminate 16, wherein in the transition region, a Abströmrohr lenders 18 branches off.
  • the Wasserableitrohr lenders 16 opens into a Abschlämmtechnisch 20, which is arranged downstream of a collecting tank 22 arranged outside the flue gas duct.
  • an outlet valve 24 is connected, via which the separated water can either be discarded or re-fed to the evaporation cycle.
  • the outlet valve 24 can be closed and thus an overfeed of the T-piece Wasserabscheideieri 12 be brought about.
  • still unevaporated water W enters the superheater tubes 26, so that they can still be used for further evaporation, d. h.,
  • the evaporation end point can be moved into the superheater tubes, which allows a relatively higher flexibility in the operation of the heat recovery steam generator 1.
  • T-piece water separation elements 12 In order to allow a particularly simple construction of the heat recovery steam generator 1, a comparatively smaller number of T-piece water separation elements 12 should be used. In order to compensate for the resulting inhomogeneities in terms of distribution to the superheater tubes and thus to allow such a configuration in the first place, the T-piece Wasserabscheideimplantationn distribution elements 34 are interposed in the manner of star distributors. These provide for a pre-distribution of the flow medium M in the event of over-feeding of the T-piece Wasserabscheideimplantation 12 on the superheater inlet collector 28th
  • the operation of the distribution elements 34 in the form of star distributors is in the plan of the heat recovery steam generator 1 according to FIG. 2 seen. Also recognizable are the first and second evaporator outlet collectors 6, 8, furthermore the T-piece water separation elements 12, the drainage line 20 and the collecting container 22.
  • the flow medium M impinges on a circular baffle plate and bounces from there into star-shaped, concentrically-symmetrically arranged outlet tubes 36 Arrangement of the output shown in the embodiment eight output tubes 36 is assigned to each output tube 36 about the same amount of flow medium M. These open at equal intervals in the superheater inlet header 28, so that there is already a pre-distribution of the flow medium M to the entire width of the superheater inlet header 28.
  • FIG. 3 clearly showing the heat recovery steam generator 1 from the direction of the flue gas inlet. Visible are the second evaporator outlet header 8, further the T-piece Wasserabscheide institute 12, the Abschlämmtechnisch 20, the sump 22 with the outlet valve 24, further the distributor elements 34 with the discharge pipes 36, which open into the superheater inlet header 28.
  • FIG. 3 shows clearly the advantages of the pre-distribution:
  • the flow medium M is already distributed over the eight outlet pipes in each case homogeneously over the entire width of each superheater inlet collector 28.
  • the flow medium M in the superheater inlet collectors 28 could not be evenly distributed, as these due to the width of the superheater heating not for such a homogeneous distribution of, for example, a single supply are suitable.
  • FIG. 4 shows an alternative embodiment, namely a heat recovery steam generator 1 with vertical flue gas direction in a side view.
  • the components and their function are substantially identical to that in the 1 to 3 shown steam generator, only the evaporator tubes 4 and the superheater tubes 26 are arranged horizontally.
  • the evaporator tubes 4 are repeatedly guided in turns through the Schugaskanal.
  • each of these elements is relatively larger dimensions.
  • flow turbulence dampers 38 are provided in an area upstream of the T-piece water separation elements 12. These may for example be mounted in an outlet region of the evaporator tubes 4, in the illustrated embodiment, they are introduced in the inflow pipe section 14 of the T-piece Wasserabscheideelements 12, which separately in FIG. 5 is shown.
  • the flow turbulence dampers 38 may include a number of bulkheads or guide profiles that may be fabricated from the same material as the inflow tubing 14. With regard to their geometric parameters, they can furthermore be adapted to the local flow conditions provided during operation.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Drying Of Solid Materials (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Separating Particles In Gases By Inertia (AREA)

Claims (8)

  1. Générateur de vapeur (1) à récupération de la chaleur perdue ayant un certain nombre de tubes (4) d'évaporateur, qui sont montés en parallèle du côté du fluide en écoulement, en aval desquels est monté, par l'intermédiaire d'un système de séparation d'eau, un certain nombre de tubes (8) de surchauffeur, le système de séparation d'eau comprenant un certain nombre d'éléments (12) de séparation d'eau, dont chacun est monté respectivement en aval d'un certain nombre de tubes (4) d'évaporateur et/ou est monté en amont d'un certain nombre de tubes (26) de surchauffeur, chacun des éléments (12) de séparation d'eau comprenant une pièce (14) tubulaire d'entrée communiquant avec les tubes (4) d'évaporateur montés respectivement en amont et se transformant, considéré dans sa direction longitudinale, en une pièce (16) tubulaire d'évacuation de l'eau, un certain nombre de pièces (18) tubulaires d'évacuation bifurquant dans la partie de transformation,
    caractérisé en ce que les pièces (18) tubulaires d'évacuation communiquent avec un collecteur (28) d'entrée des tubes (26) de surchauffeur montés respectivement en aval, un élément (34) répartiteur étant disposé du côté de la vapeur entre l'élément (12) de séparation d'eau et le collecteur (28) d'entrée.
  2. Générateur (1) de vapeur à récupération de la chaleur perdue suivant la revendication 1, dans lequel l'élément (34) répartiteur respectif comprend une plaque de rebondissement, un tube d'entrée disposé perpendiculairement à la plaque de rebondissement et un certain nombre de tubes (36) de sortie disposés en étoile autour de la plaque de rebondissement dans son plan.
  3. Générateur (1) de vapeur à récupération de la chaleur perdue suivant la revendication 2, dans lequel la plaque de rebondissement est circulaire et les tubes (36) de sortie sont disposés concentriquement au milieu de la plaque de rebondissement à de mêmes distances des tubes (36) de sortie voisins respectivement.
  4. Générateur (1) de vapeur à récupération de la chaleur perdue suivant l'une des revendications 1 à 3, dans lequel l'élément (34) répartiteur respectif comprend entre cinq et 20 tubes (36) de sortie.
  5. Générateur (1) de vapeur à récupération de la chaleur perdue suivant l'une des revendications 1 à 4, dans lequel il est prévu, dans les pièces (14) tubulaires d'entrée d'un certain nombre d'éléments (12) de séparation de l'eau, respectivement un amortisseur (38) de la turbulence de l'écoulement.
  6. Générateur (1) de vapeur à récupération de la chaleur perdue suivant la revendication 5, dans lequel l'amortisseur (38) de la turbulence de l'écoulement comprend respectivement un certain nombre de cloisons, qui ferment respectivement une partie de la section transversale du tube.
  7. Générateur (1) de vapeur à récupération de la chaleur perdue suivant la revendication 5 ou 6, dans lequel l'amortisseur (38) de la turbulence de l'écoulement a, sur une paroi intérieure de tube, un certain nombre de profilés de guidage dirigés dans la direction d'écoulement principal du fluide en écoulement.
  8. Générateur (1) de vapeur à récupération de la chaleur perdue suivant l'une des revendications 5 à 7, dans lequel les amortisseurs (38) de la turbulence de l'écoulement sont en un matériau ayant la même composition que le matériau du tube ou une composition similaire.
EP09782665.5A 2008-09-09 2009-09-07 Générateur de vapeur à récupération de chaleur Active EP2324285B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL09782665T PL2324285T3 (pl) 2008-09-09 2009-09-07 Kocioł odzyskowy
EP09782665.5A EP2324285B1 (fr) 2008-09-09 2009-09-07 Générateur de vapeur à récupération de chaleur

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP08015864A EP2204611A1 (fr) 2008-09-09 2008-09-09 Générateur de vapeur à récupération de chaleur
EP09782665.5A EP2324285B1 (fr) 2008-09-09 2009-09-07 Générateur de vapeur à récupération de chaleur
PCT/EP2009/061521 WO2010029033A2 (fr) 2008-09-09 2009-09-07 Générateur de vapeur à récupération de chaleur

Publications (2)

Publication Number Publication Date
EP2324285A2 EP2324285A2 (fr) 2011-05-25
EP2324285B1 true EP2324285B1 (fr) 2016-11-02

Family

ID=42005552

Family Applications (2)

Application Number Title Priority Date Filing Date
EP08015864A Withdrawn EP2204611A1 (fr) 2008-09-09 2008-09-09 Générateur de vapeur à récupération de chaleur
EP09782665.5A Active EP2324285B1 (fr) 2008-09-09 2009-09-07 Générateur de vapeur à récupération de chaleur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP08015864A Withdrawn EP2204611A1 (fr) 2008-09-09 2008-09-09 Générateur de vapeur à récupération de chaleur

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US (1) US8701602B2 (fr)
EP (2) EP2204611A1 (fr)
CN (1) CN102171513B (fr)
ES (1) ES2614155T3 (fr)
PL (1) PL2324285T3 (fr)
RU (1) RU2011113827A (fr)
WO (1) WO2010029033A2 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004114690A1 (fr) 2003-06-05 2004-12-29 Meshnetworks, Inc. Optimisation de l'acheminement dans des reseaux de radiocommunication ad hoc
US9273865B2 (en) * 2010-03-31 2016-03-01 Alstom Technology Ltd Once-through vertical evaporators for wide range of operating temperatures
DE102010040216A1 (de) * 2010-09-03 2012-03-08 Siemens Aktiengesellschaft Solarthermischer Druchlaufdampferzeuger mit einem Dampfabscheider und nachgeschaltetem Sternverteiler für Solarturm-Kraftwerke mit direkter Verdampfung
DE102011004278A1 (de) * 2011-02-17 2012-08-23 Siemens Aktiengesellschaft Solarthermisches Kraftwerk
CN103748414B (zh) 2012-01-17 2016-06-29 阿尔斯通技术有限公司 单程水平蒸发器中的管布置
CN103732989B (zh) 2012-01-17 2016-08-10 阿尔斯通技术有限公司 单程水平蒸发器中的管和挡板布置
US10584868B2 (en) * 2014-11-04 2020-03-10 Sharkninja Operating Llc Steam generator
CN106838852B (zh) * 2017-03-10 2023-02-28 高峰 一种膜式蒸汽发生器
CN117185391B (zh) * 2023-09-08 2024-05-10 山东迈沃净水科技有限公司 一种高效多效蒸馏水机及其模块化设计方法

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19717158C2 (de) * 1997-04-23 1999-11-11 Siemens Ag Durchlaufdampferzeuger und Verfahren zum Anfahren eines Durchlaufdampferzeugers
DE10228335B3 (de) * 2002-06-25 2004-02-12 Siemens Ag Abhitzedampferzeuger mit Hilfsdampferzeugung
EP1701090A1 (fr) 2005-02-16 2006-09-13 Siemens Aktiengesellschaft Générateur de vapeur à construction horizontale
EP1701091A1 (fr) * 2005-02-16 2006-09-13 Siemens Aktiengesellschaft Générateur de vapeur à passage unique
EP1710498A1 (fr) * 2005-04-05 2006-10-11 Siemens Aktiengesellschaft Générateur de vapeur
NL2003596C2 (en) * 2009-10-06 2011-04-07 Nem Bv Cascading once through evaporator.

Also Published As

Publication number Publication date
US8701602B2 (en) 2014-04-22
CN102171513A (zh) 2011-08-31
WO2010029033A2 (fr) 2010-03-18
ES2614155T3 (es) 2017-05-29
US20110162594A1 (en) 2011-07-07
PL2324285T3 (pl) 2017-04-28
WO2010029033A3 (fr) 2010-06-10
RU2011113827A (ru) 2012-10-20
CN102171513B (zh) 2013-11-20
EP2204611A1 (fr) 2010-07-07
EP2324285A2 (fr) 2011-05-25

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