EP2440847A2 - Continuous evaporator - Google Patents

Continuous evaporator

Info

Publication number
EP2440847A2
EP2440847A2 EP10718147A EP10718147A EP2440847A2 EP 2440847 A2 EP2440847 A2 EP 2440847A2 EP 10718147 A EP10718147 A EP 10718147A EP 10718147 A EP10718147 A EP 10718147A EP 2440847 A2 EP2440847 A2 EP 2440847A2
Authority
EP
European Patent Office
Prior art keywords
steam generator
evaporator
tubes
continuous
inner profile
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Withdrawn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
EP10718147A
Other languages
German (de)
French (fr)
Inventor
Jan BRÜCKNER
Joachim Franke
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
Publication of EP2440847A2 publication Critical patent/EP2440847A2/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F28—HEAT EXCHANGE IN GENERAL
    • F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
    • F28F1/00—Tubular elements; Assemblies of tubular elements
    • F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
    • F28F1/40—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only inside the tubular element
    • 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
    • F22B37/10—Water tubes; Accessories therefor
    • F22B37/101—Tubes having fins or ribs
    • F22B37/103—Internally ribbed tubes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B1/00—Methods of steam generation characterised by form of heating method
    • F22B1/02—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers
    • F22B1/18—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines
    • F22B1/1807—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines
    • F22B1/1815—Methods of steam generation characterised by form of heating method by exploitation of the heat content of hot heat carriers the heat carrier being a hot gas, e.g. waste gas such as exhaust gas of internal-combustion engines using the exhaust gases of combustion engines using the exhaust gases of gas-turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B29/00—Steam boilers of forced-flow type
    • F22B29/06—Steam boilers of forced-flow type of once-through type, i.e. built-up from tubes receiving water at one end and delivering superheated steam at the other end of the tubes
    • F22B29/061—Construction of tube walls
    • F22B29/062—Construction of tube walls involving vertically-disposed water tubes
    • 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
    • F25B39/00—Evaporators; Condensers
    • F25B39/02—Evaporators

Definitions

  • the invention relates to a continuous evaporator for a heat recovery steam generator in lying construction with a first Verdampfersammlungflache comprising a number of substantially vertically arranged, from bottom to top flowed first steam generator tubes, and another, the first Verdampfersammlungflache flow medium side downstream second Verdampferiensflache, the Number of further, arranged substantially vertically, from bottom to top flowed through the second steam generator tubes.
  • the heat contained in the relaxed working fluid or heating gas from the gas turbine is used to generate steam for the steam turbine.
  • the heat transfer takes place in a heat recovery steam generator connected downstream of the gas turbine, in which a number of heating surfaces for water preheating, steam generation and steam superheating is usually arranged.
  • the heating surfaces are connected in the water-steam cycle of the steam turbine.
  • the water-steam cycle usually includes several, z. B. three, pressure levels, each pressure stage may have a evaporator heating surface.
  • a continuous steam generator in contrast to a natural or forced circulation steam generator is not subject to pressure limitation.
  • a high live steam pressure promotes a high thermal efficiency and thus low CO 2 emissions of a fossil-fired power plant.
  • a continuous steam generator in comparison to a circulating steam generator has a simple design and can therefore be produced with particularly little effort.
  • the use of a designed according to the flow principle steam generator as heat recovery steam generator of a gas and steam turbine plant is therefore particularly favorable to achieve a high overall efficiency of the gas and steam turbine plant with a simple design.
  • a continuous steam generator designed as a heat recovery steam generator can in principle be embodied in one of two alternative designs, namely in upright design or in horizontal construction.
  • Construction is designed for a flow through the heated medium or heating gas, for example, the exhaust gas from the gas turbine, in approximately horizontal direction, whereas a continuous steam generator is designed in standing construction for a flow of the heated medium in an approximately vertical direction.
  • a continuous steam generator in lying construction is in contrast to a continuous steam generator in a stile construction with particularly simple means and with very low
  • the invention is therefore based on the object to provide a continuous evaporator for a heat recovery steam generator of the type mentioned above, which allows for a particularly long service life, a particularly simple design.
  • the invention is based on the consideration that a particularly simple construction of the heat recovery steam generator or of the continuous evaporator could be achieved by eliminating the usual expansion bends.
  • the mechanical stresses caused by temperature imbalances in the steam generator tubes of each individual row of tubes connected in parallel must be reduced in a different manner. These occur in particular in the second evaporator heating surface, which is acted upon by a water-steam mixture.
  • the temperature imbalances are caused by different proportions of water and steam at the flow-side inlet of the individual tubes of a row of tubes and a resulting different flow through these tubes. It has been recognized that this differential flow in the tubes is caused by a low friction pressure loss in the steam generator tubes compared to the geodetic pressure loss.
  • a flow with a high vapor content of the flow medium flows namely at low friction pressure loss comparatively quickly through individual steam generator tubes, while a flow with high water content is disadvantaged due to their higher, caused by the mass geodetic pressure loss and may tend to stagnation.
  • the friction pressure loss should be increased. This is achievable by adding a number of second steam generator tubes has an inner profile, which causes such additional friction pressure loss.
  • the laminar boundary layer on the inside of the tubes should be reduced. This can be achieved by generating turbulence in the pipe. This effect can be further enhanced by creating a twist of the flow medium. Such swirl generation is possible in which the inner profile is advantageously helical spring-shaped.
  • This friction pressure loss should be determined according to the other operating parameters such as the tube geometry, the dimensions of the heating gas channel and the temperature conditions.
  • the profile geometry of the respective inner profile should be chosen such that adjusts the predetermined friction pressure loss of the flow medium via the respective second steam generator tube.
  • the respective inner profile is introduced in the manner of a réelleberippung in the respective second steam generator tube. This allows a particularly simple construction of a continuous evaporator or a heat recovery steam generator.
  • the respective inner profile is advantageously used as a built-in part in the respective second steam generator tube.
  • the inner profile is thus configured as a separate built-in part and arranged in the steam generator tubes.
  • a number of second steam generator tubes each other on the heating gas side as rows of tubes connected in series is made it possible to use a larger number of steam generator tubes connected in parallel for an evaporator heating surface, which means a better heat input due to the increased surface area.
  • successively arranged steam generator tubes are heated differently. The flow medium is heated to a comparatively high degree, in particular in the heating gas inlet-side steam generator tubes. Due to the described embodiment of the second steam generator tubes with an inner profile, however, it is also possible to use them in these
  • the first evaporator heating surface of the second evaporator heating surface is connected downstream of the heating gas side. This offers the advantage that the second evaporator heating surface designed downstream of the flow medium side and thus already vaporized for further heating is also located in a comparatively more heated region of the heating gas channel.
  • such a continuous evaporator is used in a heat recovery steam generator and the heat recovery steam generator is used in a gas and steam turbine plant.
  • the steam generator is advantageously followed by a gas turbine on the hot gas side.
  • the advantages achieved by the invention are in particular that an improvement of the distribution of the flow and thus a reduction in the temperature differences between parallel connected second steam generator tubes and the resulting mechanical stresses is achieved by the introduction of an inner profile in the second evaporator tubes.
  • an inner profile in the second evaporator tubes.
  • the corresponding arrangement of an inner profile means that additional, complex technical measures such as expansion bends can be dispensed with and at the same time a particularly simple, cost-saving construction of the heat recovery steam generator or of a combined cycle gas turbine power plant is made possible.
  • FIG. 5 shows a graphic representation of the pipe temperature against the steam content at the heating pipe inlet with internal profile.
  • the continuous evaporator 1 for the heat recovery steam generator 2 GE measure of FIG 1 is downstream of a gas turbine not shown in detail on the exhaust side.
  • the heat recovery steam generator 2 has a surrounding wall 3, which forms a heating gas duct 5 for the exhaust gas from the gas turbine which can be flowed through in an approximately horizontal heating gas direction indicated by the arrows 4.
  • a number of designed according to the flow principle evaporator 8, 10 is arranged in the heating gas channel 5, a number of designed according to the flow principle evaporator 8, 10 is arranged.
  • two evaporator heating surfaces 8, 10 are shown, but it can also a larger number of Verdampferlikflachen be provided.
  • the evaporator heating surfaces 8, 10 according to FIG. 1 each comprise, in the manner of a tube bundle, a number of rows of tubes 11 or 12 arranged behind one another in the heating gas direction.
  • Each row of tubes 11, 12 in each case comprises a number of steam generator tubes 13 arranged side by side in the heating gas direction. 14, of which only one is visible for each row of tubes 11, 12.
  • the approximately vertically arranged, for the flow of a flow medium W connected in parallel first steam generator tubes 13 of the first evaporator 8 are connected on the output side to a common outlet collector 15.
  • Flow medium W parallel connected second steam generator tubes 14 of the second evaporator 10 are also connected on the output side to a common outlet collector 16.
  • a comparatively complex collector system can also be provided for both evaporator heating surfaces 8, 10.
  • the steam generator tubes 14 of the second evaporator heating surface 10 are downstream of the steam generator tubes 13 of the first evaporator heating surface 8 via a downflow system 17.
  • the evaporator system formed from the evaporator 8, 10 evaporator system can be acted upon with the flow medium W, which is vaporized in a single pass through the evaporator system and discharged after exiting the second Verdampfersammlungflache 10 as steam D.
  • the evaporator system formed from the evaporator 8, 10 evaporator system is connected in the not shown water-steam cycle of a steam turbine.
  • a number of other, in FIG 1 schematically indicated heating surfaces 20 are connected in the water-steam cycle of the steam turbine.
  • the heating surfaces 20 may be, for example, superheaters, medium pressure evaporator to act low pressure evaporator and / or preheater.
  • the second steam generator tubes 14 now have a helical spring-shaped inner profile 22, which is shown in FIGS. 2 and 3. Its profile geometry is selected such that the friction pressure loss of the flow medium W in the steam generator tubes 14, generated by swirl and turbulence, is correspondingly high enough to ensure uniform flow within a row of tubes 11. This reduces temperature imbalances.
  • the inner profile 22 can be introduced directly into the steam generator tubes 14 in the manner of an inner nip 23.
  • built-in parts 24 serve as an inner profile 22, which in particular allows retrofitting existing continuous evaporator 1.
  • FIGS. 4 and 5 show a graphical representation of the mean tube wall temperature 25 and the tube outlet wall temperature 27, plotted against the vapor fraction 29 of the flow medium at the inlet into the tube. 4 shows the situation without an inner profile 22.
  • the average tube wall temperature 25 varies between about 460 0 C and 360 ° C
  • the Rohrausbergswandtemperatur 27 between 480 0 C and 370 0 C, depending on the vapor content 29.
  • FIG 5 the Situation illustrated with inner profile 22, it is shown that reduce these variations to about 440 0 C to 390 0 C and 470 0 C to 405 ° C. The temperature differences between pipes with different steam content at the entrance are thus significantly reduced.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Sustainable Energy (AREA)
  • Geometry (AREA)
  • Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Vaporization, Distillation, Condensation, Sublimation, And Cold Traps (AREA)

Abstract

The invention relates to a continuous evaporator (1) for a horizontal waste heat steam generator comprising a first evaporator heating surface (8) that has a number of essentially vertically arranged first steam generating tubes (13) wherein the circulation takes place from the bottom to the top, and another second evaporator heating surface (10) located downstream of the first evaporator heating surface on the side of the flow medium, said second evaporator heating surface comprising a number of other essentially vertically arranged second steam generating tubes wherein the circulation takes place from the bottom to the top. The aim of the invention is to provide said continuous evaporator with an especially simple structure and an especially long service life. To this end, a number of second steam generating tubes (14) have an inner profiled element (22).

Description

Beschreibungdescription
DurchlaufverdampferFlow evaporator
Die Erfindung betrifft einen Durchlaufverdampfer für einen Abhitzedampferzeuger in liegender Bauweise mit einer ersten Verdampferheizflache, die eine Anzahl von im Wesentlichen vertikal angeordneten, von unten nach oben durchströmten ersten Dampferzeugerrohren umfasst, und einer weiteren, der ers- ten Verdampferheizflache strömungsmediumsseitig nachgeschalteten zweiten Verdampferheizflache, die eine Anzahl von weiteren, im Wesentlichen vertikal angeordneten, von unten nach oben durchströmten zweiten Dampferzeugerrohren umfasst.The invention relates to a continuous evaporator for a heat recovery steam generator in lying construction with a first Verdampferheizflache comprising a number of substantially vertically arranged, from bottom to top flowed first steam generator tubes, and another, the first Verdampferheizflache flow medium side downstream second Verdampferheizflache, the Number of further, arranged substantially vertically, from bottom to top flowed through the second steam generator tubes.
Bei einer Gas- und Dampfturbinenanlage wird die im entspannten Arbeitsmittel oder Heizgas aus der Gasturbine enthaltene Wärme zur Erzeugung von Dampf für die Dampfturbine genutzt. Die Wärmeübertragung erfolgt in einem der Gasturbine nachgeschalteten Abhitzedampferzeuger, in dem üblicherweise eine Anzahl von Heizflächen zur Wasservorwärmung, zur Dampferzeugung und zur Dampfüberhitzung angeordnet ist. Die Heizflächen sind in den Wasser-Dampf-Kreislauf der Dampfturbine geschaltet. Der Wasser-Dampf-Kreislauf umfasst üblicherweise mehrere, z. B. drei, Druckstufen, wobei jede Druckstufe eine Ver- dampferheizflache aufweisen kann.In a gas and steam turbine plant, the heat contained in the relaxed working fluid or heating gas from the gas turbine is used to generate steam for the steam turbine. The heat transfer takes place in a heat recovery steam generator connected downstream of the gas turbine, in which a number of heating surfaces for water preheating, steam generation and steam superheating is usually arranged. The heating surfaces are connected in the water-steam cycle of the steam turbine. The water-steam cycle usually includes several, z. B. three, pressure levels, each pressure stage may have a evaporator heating surface.
Für den der Gasturbine als Abhitzedampferzeuger heizgasseitig nachgeschalteten Dampferzeuger kommen mehrere alternative Auslegungskonzepte, nämlich die Auslegung als Durchlaufdampf- erzeuger oder die Auslegung als Umlaufdampferzeuger, in Betracht. Bei einem Durchlaufdampferzeuger führt die Beheizung von als Verdampferrohren vorgesehenen Dampferzeugerrohren zu einer Verdampfung des Strömungsmediums in den Dampferzeugerrohren in einem einmaligen Durchlauf. Im Gegensatz dazu wird bei einem Natur- oder Zwangumlaufdampferzeuger das im Umlauf geführte Wasser beim Durchlauf durch die Verdampferrohre nur teilweise verdampft. Das dabei nicht verdampfte Wasser wird nach einer Abtrennung des erzeugten Dampfes für eine weitere Verdampfung denselben Verdampferrohren erneut zugeführt.For the gas turbine as a heat recovery steam generator downstream of the gas turbine steam generator come several alternative design concepts, namely the design as a continuous steam generator or the design as a circulating steam generator, into consideration. In a continuous steam generator, the heating of steam generator tubes provided as evaporator tubes leads to an evaporation of the flow medium in the steam generator tubes in a single pass. In contrast, in a natural or forced circulation steam generator, the recirculated water is only partially evaporated as it passes through the evaporator tubes. The unevaporated water will be after separation of the generated steam for further evaporation of the same evaporator tubes fed again.
Ein Durchlaufdampferzeuger unterliegt im Gegensatz zu einem Natur- oder Zwangumlaufdampferzeuger keiner Druckbegrenzung. Ein hoher Frischdampfdruck begünstigt einen hohen thermischen Wirkungsgrad und somit niedrige C02-Emissionen eines fossilbeheizten Kraftwerks. Zudem weist ein Durchlaufdampferzeuger im Vergleich zu einem Umlaufdampferzeuger eine einfache Bau- weise auf und ist somit mit besonders geringem Aufwand herstellbar. Die Verwendung eines nach dem Durchlaufprinzip ausgelegten Dampferzeugers als Abhitzedampferzeuger einer Gas- und Dampfturbinenanlage ist daher zur Erzielung eines hohen Gesamtwirkungsgrades der Gas- und Dampfturbinenanlage bei einfacher Bauweise besonders günstig.A continuous steam generator, in contrast to a natural or forced circulation steam generator is not subject to pressure limitation. A high live steam pressure promotes a high thermal efficiency and thus low CO 2 emissions of a fossil-fired power plant. In addition, a continuous steam generator in comparison to a circulating steam generator has a simple design and can therefore be produced with particularly little effort. The use of a designed according to the flow principle steam generator as heat recovery steam generator of a gas and steam turbine plant is therefore particularly favorable to achieve a high overall efficiency of the gas and steam turbine plant with a simple design.
Ein als Abhitzedampferzeuger ausgelegter Durchlaufdampferzeuger kann grundsätzlich in einer von zwei alternativen Bauformen ausgeführt sein, nämlich in stehender Bauweise oder in liegender Bauweise. Ein Durchlaufdampferzeuger in liegenderA continuous steam generator designed as a heat recovery steam generator can in principle be embodied in one of two alternative designs, namely in upright design or in horizontal construction. A continuous steam generator in horizontal
Bauweise ist dabei für eine Durchströmung des beheizenden Mediums oder Heizgases, beispielsweise des Abgases aus der Gasturbine, in annähernd horizontaler Richtung ausgelegt, wohingegen ein Durchlaufdampferzeuger in stehender Bauweise für eine Durchströmung des beheizenden Mediums in einer annähernd vertikalen Richtung ausgelegt ist.Construction is designed for a flow through the heated medium or heating gas, for example, the exhaust gas from the gas turbine, in approximately horizontal direction, whereas a continuous steam generator is designed in standing construction for a flow of the heated medium in an approximately vertical direction.
Ein Durchlaufdampferzeuger in liegender Bauweise ist im Gegensatz zu einem Durchlaufdampferzeuger in stehender Bauweise mit besonders einfachen Mitteln und mit besonders geringemA continuous steam generator in lying construction is in contrast to a continuous steam generator in a stile construction with particularly simple means and with very low
Fertigungs- und Montageaufwand herstellbar. Dabei kann insbesondere in den strömungsmediumsseitig nachgelagerten Dampferzeugerrohren der zweiten Verdampferheizflache innerhalb jeder einzelnen Rohrreihe eine ungleichmäßige Verteilung des zweiphasigen Strömungsmediums auf die Dampferzeugerrohre auftreten, die zu Temperaturschieflagen und durch unterschiedliche thermische Ausdehnung zu mechanischen Spannungen führt. Um Beschädigungen des Abhitzedampferzeugers zu vermeiden, wurden daher bisher beispielsweise Dehnbögen zur Kompensation dieser Spannungen angebracht. Diese Maßnahme kann jedoch bei einem Abhitzedampferzeuger in liegender Bauweise technisch vergleichsweise aufwändig sein.Manufacturing and assembly costs produced. In this case, in particular in the flow medium side downstream steam generator tubes of the second evaporator heating surface within each row of tubes an uneven distribution of the two-phase flow medium to the steam generator tubes occur, which leads to temperature imbalances and different thermal expansion to mechanical stresses. To avoid damage to the heat recovery steam generator, So far, for example, extension bends have been used to compensate for these stresses. However, this measure can be technically relatively complicated in a heat recovery steam generator in a horizontal design.
Der Erfindung liegt daher die Aufgabe zugrunde, einen Durchlaufverdampfer für einen Abhitzedampferzeuger der oben genannten Art anzugeben, welcher bei einer besonders hohen Lebensdauer eine besonders einfache Bauweise erlaubt.The invention is therefore based on the object to provide a continuous evaporator for a heat recovery steam generator of the type mentioned above, which allows for a particularly long service life, a particularly simple design.
Diese Aufgabe wird erfindungsgemäß gelöst, indem eine Anzahl von zweiten Dampferzeugerrohren ein Innenprofil aufweist.This object is achieved according to the invention in that a number of second steam generator tubes have an internal profile.
Die Erfindung geht dabei von der Überlegung aus, dass eine besonders einfache Konstruktion des Abhitzedampferzeugers bzw. des Durchlaufverdampfers durch einen Entfall der bisher üblichen Dehnbögen erreicht werden könnte. Dabei müssen jedoch die durch Temperaturschieflagen in den parallel geschalteten Dampferzeugerrohren jeder einzelnen Rohrreihe verur- sachten mechanischen Spannungen auf andere Weise reduziert werden. Diese treten insbesondere in der zweiten Verdampfer- heizfläche auf, die mit Wasser-Dampf-Gemisch beaufschlagt wird. Die Temperaturschieflagen werden dabei durch unterschiedliche Anteile von Wasser und Dampf am strömungsseitigen Eintritt der Einzelrohre einer Rohrreihe und einer daraus resultierenden unterschiedlichen Durchströmung dieser Rohre verursacht. Es wurde erkannt, dass diese unterschiedliche Durchströmung in den Rohren durch einen im Vergleich zum geodätischen Druckverlust geringen Reibungsdruckverlust in den Dampferzeugerrohren verursacht wird. Eine Strömung mit hohem Dampfanteil des Strömungsmediums strömt nämlich bei geringem Reibungsdruckverlust vergleichsweise schnell durch einzelne Dampferzeugerrohre, während eine Strömung mit hohem Wasseranteil aufgrund ihres höheren, durch die Masse verursachten geodätischen Druckverlustes benachteiligt ist und zur Stagnation neigen kann. Um die Durchströmungen zu vergleichmäßigen, sollte daher der Reibungsdruckverlust erhöht werden. Dies ist erreichbar, indem eine Anzahl von zweiten Dampferzeugerrohren ein Innenprofil aufweist, welches einen derartigen zusätzlichen Reibungsdruckverlust verursacht.The invention is based on the consideration that a particularly simple construction of the heat recovery steam generator or of the continuous evaporator could be achieved by eliminating the usual expansion bends. In this case, however, the mechanical stresses caused by temperature imbalances in the steam generator tubes of each individual row of tubes connected in parallel must be reduced in a different manner. These occur in particular in the second evaporator heating surface, which is acted upon by a water-steam mixture. The temperature imbalances are caused by different proportions of water and steam at the flow-side inlet of the individual tubes of a row of tubes and a resulting different flow through these tubes. It has been recognized that this differential flow in the tubes is caused by a low friction pressure loss in the steam generator tubes compared to the geodetic pressure loss. A flow with a high vapor content of the flow medium flows namely at low friction pressure loss comparatively quickly through individual steam generator tubes, while a flow with high water content is disadvantaged due to their higher, caused by the mass geodetic pressure loss and may tend to stagnation. In order to equalize the flows, therefore, the friction pressure loss should be increased. This is achievable by adding a number of second steam generator tubes has an inner profile, which causes such additional friction pressure loss.
Um einen besonders hohen zusätzlichen Reibungsdruckverlust zu erreichen, sollte die laminare Grenzschicht an der Innenseite der Rohre verringert werden. Dies kann durch die Erzeugung von Turbulenzen im Rohr erreicht werden. Verstärkt werden kann dieser Effekt weiter durch Erzeugung eines Dralls des Strömungsmediums. Eine derartige Drallerzeugung ist möglich, in dem das Innenprofil vorteilhafterweise schraubenfederförmig ist.In order to achieve a particularly high additional friction pressure loss, the laminar boundary layer on the inside of the tubes should be reduced. This can be achieved by generating turbulence in the pipe. This effect can be further enhanced by creating a twist of the flow medium. Such swirl generation is possible in which the inner profile is advantageously helical spring-shaped.
Dieser Reibungsdruckverlust sollte anhand der übrigen Betriebsparameter wie der Rohrgeometrie, den Abmessungen des Heizgaskanals und der Temperaturverhältnisse entsprechend bestimmt werden. Vorteilhafterweise sollte dann die Profilgeometrie des jeweiligen Innenprofils derart gewählt sein, dass sich über das jeweilige zweite Dampferzeugerrohr der vorgegebene Reibungsdruckverlust des Strömungsmediums einstellt. Somit ist eine noch bessere Vermeidung von Temperaturschieflagen möglich.This friction pressure loss should be determined according to the other operating parameters such as the tube geometry, the dimensions of the heating gas channel and the temperature conditions. Advantageously, then the profile geometry of the respective inner profile should be chosen such that adjusts the predetermined friction pressure loss of the flow medium via the respective second steam generator tube. Thus, an even better avoidance of temperature imbalances is possible.
In vorteilhafter Ausgestaltung ist das jeweilige Innenprofil in der Art einer Innenberippung in das jeweilige zweite Dampferzeugerrohr eingebracht. Dies ermöglicht eine besonders einfache Konstruktion eines Durchlaufverdampfers bzw. eines Abhitzedampferzeugers .In an advantageous embodiment, the respective inner profile is introduced in the manner of a Innenberippung in the respective second steam generator tube. This allows a particularly simple construction of a continuous evaporator or a heat recovery steam generator.
Um auch eine Nachrüstung bestehender Dampferzeuger bzw. eine größere Flexibilität bei der Konstruktion eines Dampferzeugers hinsichtlich der Rohrgeometrien zu erreichen, ist das jeweilige Innenprofil vorteilhafterweise als Einbauteil in das jeweilige zweite Dampferzeugerrohr eingesetzt. Das Innenprofil wird somit als separates Einbauteil ausgestaltet und in den Dampferzeugerrohren angeordnet.In order to achieve a retrofit existing steam generator or greater flexibility in the construction of a steam generator with respect to the tube geometries, the respective inner profile is advantageously used as a built-in part in the respective second steam generator tube. The inner profile is thus configured as a separate built-in part and arranged in the steam generator tubes.
In vorteilhafter Ausgestaltung ist eine Anzahl von zweiten Dampferzeugerrohren einander heizgasseitig als Rohrreihen hintereinander geschaltet. Dies ermöglicht es, eine größere Anzahl von parallel geschalteten Dampferzeugerrohren für eine Verdampferheizflache zu verwenden, was durch die vergrößerte Oberfläche einen besseren Wärmeeintrag bedeutet. Allerdings sind die in Heizgasströmungsrichtung hintereinander angeordneten Dampferzeugerrohre dabei unterschiedlich beheizt. Insbesondere in den heizgaseintrittsseitigen Dampferzeugerroh- ren wird das Strömungsmedium vergleichsweise stark beheizt. Durch die beschriebene Ausgestaltung der zweiten Dampferzeu- gerrohre mit einem Innenprofil kann jedoch auch in diesenIn an advantageous embodiment, a number of second steam generator tubes each other on the heating gas side as rows of tubes connected in series. This makes it possible to use a larger number of steam generator tubes connected in parallel for an evaporator heating surface, which means a better heat input due to the increased surface area. However, in the Heizgasströmungsrichtung successively arranged steam generator tubes are heated differently. The flow medium is heated to a comparatively high degree, in particular in the heating gas inlet-side steam generator tubes. Due to the described embodiment of the second steam generator tubes with an inner profile, however, it is also possible to use them in these
Dampferzeugerrohren eine der Beheizung angepasste Durchströmung erreicht werden. Dadurch wird bei einfacher Konstruktion eine besonders lange Lebensdauer des Abhitzedampferzeugers erreicht .Steam generator tubes adapted to the heating flow can be achieved. As a result, a particularly long life of the heat recovery steam generator is achieved with a simple design.
In vorteilhafter Ausgestaltung ist die erste Verdampferheiz- fläche der zweiten Verdampferheizflache heizgasseitig nachgeschaltet. Dies bietet den Vorteil, dass die zweite, strö- mungsmediumsseitig nachgeschaltete und somit zur weiteren Er- hitzung bereits verdampften Strömungsmediums ausgelegte Verdampferheizfläche auch in einem vergleichsweise stärker beheizten Bereich des Heizgaskanals liegt.In an advantageous embodiment, the first evaporator heating surface of the second evaporator heating surface is connected downstream of the heating gas side. This offers the advantage that the second evaporator heating surface designed downstream of the flow medium side and thus already vaporized for further heating is also located in a comparatively more heated region of the heating gas channel.
Zweckmäßigerweise kommt ein derartiger Durchlaufverdampfer in einem Abhitzedampferzeuger zum Einsatz und es wird der Abhitzedampferzeuger in einer Gas- und Dampfturbinenanlage verwendet. Dabei ist der Dampferzeuger vorteilhafterweise heizgasseitig einer Gasturbine nachgeschaltet. Bei dieser Schaltung kann zweckmäßigerweise hinter der Gasturbine eine Zusatzfeue- rung zur Erhöhung der Heizgastemperatur angeordnet sein.Expediently, such a continuous evaporator is used in a heat recovery steam generator and the heat recovery steam generator is used in a gas and steam turbine plant. In this case, the steam generator is advantageously followed by a gas turbine on the hot gas side. In this circuit, it is expedient to arrange an additional firing behind the gas turbine to increase the heating gas temperature.
Die mit der Erfindung erzielten Vorteile bestehen insbesondere darin, dass durch die Einbringung eines Innenprofils in die zweiten Verdampferrohre eine Verbesserung der Verteilung der Strömung und somit eine Reduzierung der Temperaturdifferenzen zwischen parallel geschalteten zweiten Dampferzeugerrohren und der daraus resultierenden mechanischen Spannungen erreicht wird. Dadurch ist die Lebensdauer des Abhitzedampf- erzeugers besonders hoch. Durch die entsprechende Anordnung eines Innenprofils können weitere, aufwändige technische Maßnahmen wie Dehnbögen entfallen und es wird so gleichzeitig eine besonders einfache, kostensparende Konstruktion des Ab- hitzedampferzeugers bzw. eines Gas- und Dampfturbinenkraft- werks ermöglicht.The advantages achieved by the invention are in particular that an improvement of the distribution of the flow and thus a reduction in the temperature differences between parallel connected second steam generator tubes and the resulting mechanical stresses is achieved by the introduction of an inner profile in the second evaporator tubes. As a result, the lifetime of the waste heat steam especially high. The corresponding arrangement of an inner profile means that additional, complex technical measures such as expansion bends can be dispensed with and at the same time a particularly simple, cost-saving construction of the heat recovery steam generator or of a combined cycle gas turbine power plant is made possible.
Ein Ausführungsbeispiel der Erfindung wird anhand einer Zeichnung näher erläutert. Darin zeigen:An embodiment of the invention will be explained in more detail with reference to a drawing. Show:
FIG 1 in vereinfachter Darstellung im Längsschnitt einen Dampferzeuger in liegender Bauweise,1 shows a simplified representation in longitudinal section of a steam generator in horizontal construction,
FIG 2 ein Dampferzeugerrohr mit Innenberippung im Längs- schnitt,2 shows a steam generator tube with internal ribbing in longitudinal section,
FIG 3 ein Dampferzeugerrohr mit Einbauten im Längsschnitt,3 shows a steam generator tube with internals in longitudinal section,
FIG 4 eine graphische Darstellung der Rohrtemperatur gegen den Dampfgehalt am Heizrohreintritt ohne Innenprofil und4 is a graphic representation of the tube temperature against the vapor content at the Heizrohreintritt without inner profile and
FIG 5 eine graphische Darstellung der Rohrtemperatur gegen den Dampfgehalt am Heizrohreintritt mit Innenprofil.5 shows a graphic representation of the pipe temperature against the steam content at the heating pipe inlet with internal profile.
Gleiche Teile sind in allen Figuren mit denselben Bezugszeichen versehen.Identical parts are provided with the same reference numerals in all figures.
Der Durchlaufverdampfer 1 für den Abhitzedampferzeuger 2 ge- maß der FIG 1 ist einer nicht näher dargestellten Gasturbine abgasseitig nachgeschaltet. Der Abhitzedampferzeuger 2 weist eine Umfassungswand 3 auf, die einen in einer annähernd horizontalen, durch die Pfeile 4 angedeuteten Heizgasrichtung durchströmbaren Heizgaskanal 5 für das Abgas aus der Gastur- bine bildet. Im Heizgaskanal 5 ist eine Anzahl von nach dem Durchlaufprinzip ausgelegten Verdampferheizflachen 8, 10 angeordnet. Im Ausführungsbeispiel gemäß der FIG 1 sind jeweils zwei Verdampferheizflachen 8, 10 gezeigt, es kann aber auch eine größere Anzahl von Verdampferheizflachen vorgesehen sein .The continuous evaporator 1 for the heat recovery steam generator 2 GE measure of FIG 1 is downstream of a gas turbine not shown in detail on the exhaust side. The heat recovery steam generator 2 has a surrounding wall 3, which forms a heating gas duct 5 for the exhaust gas from the gas turbine which can be flowed through in an approximately horizontal heating gas direction indicated by the arrows 4. In the heating gas channel 5, a number of designed according to the flow principle evaporator 8, 10 is arranged. In the embodiment shown in FIG 1, two evaporator heating surfaces 8, 10 are shown, but it can also a larger number of Verdampferheizflachen be provided.
Die Verdampferheizflachen 8, 10 gemäß der FIG 1 umfassen je- weils in der Art eines Rohrbündels eine Anzahl von in Heizgasrichtung hintereinander angeordneten Rohrreihen 11 bzw. 12. Jede Rohrreihe 11, 12 wiederum umfasst jeweils eine Anzahl von in Heizgasrichtung nebeneinander angeordneten Dampferzeugerrohren 13 bzw. 14, von denen für jede Rohrreihe 11, 12 nur jeweils eines sichtbar ist. Die annähernd vertikal angeordneten, zur Durchströmung eines Strömungsmediums W parallel geschalteten ersten Dampferzeugerrohre 13 der ersten Verdampferheizfläche 8 sind dabei ausgangsseitig an einen ihnen gemeinsamen Austrittssammler 15 angeschlossen. Die ebenfalls annähernd vertikal angeordneten, zur Durchströmung einesThe evaporator heating surfaces 8, 10 according to FIG. 1 each comprise, in the manner of a tube bundle, a number of rows of tubes 11 or 12 arranged behind one another in the heating gas direction. Each row of tubes 11, 12 in each case comprises a number of steam generator tubes 13 arranged side by side in the heating gas direction. 14, of which only one is visible for each row of tubes 11, 12. The approximately vertically arranged, for the flow of a flow medium W connected in parallel first steam generator tubes 13 of the first evaporator 8 are connected on the output side to a common outlet collector 15. The also approximately vertically arranged to flow through a
Strömungsmediums W parallel geschalteten zweiten Dampferzeugerrohre 14 der zweiten Verdampferheizflache 10 sind ebenso ausgangsseitig an einen ihnen gemeinsamen Austrittssammler 16 angeschlossen. Es kann dabei auch bei beiden Verdampferheiz- flächen 8, 10 ein vergleichsweise aufwändigeres Sammlersystem vorgesehen sein. Die Dampferzeugerrohre 14 der zweiten Verdampferheizfläche 10 sind den Dampferzeugerrohren 13 der ersten Verdampferheizflache 8 strömungstechnisch über ein Fallrohrsystem 17 nachgeschaltet.Flow medium W parallel connected second steam generator tubes 14 of the second evaporator 10 are also connected on the output side to a common outlet collector 16. In this case, a comparatively complex collector system can also be provided for both evaporator heating surfaces 8, 10. The steam generator tubes 14 of the second evaporator heating surface 10 are downstream of the steam generator tubes 13 of the first evaporator heating surface 8 via a downflow system 17.
Das aus den Verdampferheizflachen 8, 10 gebildete Verdampfersystem ist mit dem Strömungsmedium W beaufschlagbar, das bei einmaligem Durchlauf durch das Verdampfersystem verdampft und nach dem Austritt aus der zweiten Verdampferheizflache 10 als Dampf D abgeführt wird. Das aus den Verdampferheizflachen 8, 10 gebildete Verdampfersystem ist in den nicht näher dargestellten Wasser-Dampf-Kreislauf einer Dampfturbine geschaltet. Zusätzlich zu dem die Verdampferheizflachen 8, 10 umfassenden Verdampfersystem sind in den Wasser-Dampf-Kreislauf der Dampfturbine eine Anzahl weitere, in der FIG 1 schematisch angedeutete Heizflächen 20 geschaltet. Bei den Heizflächen 20 kann es sich beispielsweise um Überhitzer, um Mittel- druckverdampfer, um Niederdruckverdampfer und/oder um Vorwärmer handeln.The evaporator system formed from the evaporator 8, 10 evaporator system can be acted upon with the flow medium W, which is vaporized in a single pass through the evaporator system and discharged after exiting the second Verdampferheizflache 10 as steam D. The evaporator system formed from the evaporator 8, 10 evaporator system is connected in the not shown water-steam cycle of a steam turbine. In addition to the evaporator heating surfaces 8, 10 comprehensive evaporator system, a number of other, in FIG 1 schematically indicated heating surfaces 20 are connected in the water-steam cycle of the steam turbine. The heating surfaces 20 may be, for example, superheaters, medium pressure evaporator to act low pressure evaporator and / or preheater.
Die zweiten Dampferzeugerrohre 14 weisen nun ein schrauben- federförmiges Innenprofil 22 auf, welches in den FIG 2 und 3 dargestellt ist. Dessen Profilgeometrie ist so gewählt, dass der durch Drall und Turbulenzen erzeugte Reibungsdruckverlust des Strömungsmediums W in den Dampferzeugerrohren 14 entsprechend so hoch ist, dass eine gleichmäßige Durchströmung in- nerhalb einer Rohrreihe 11 gewährleistet ist. Dadurch werden Temperaturschieflagen reduziert. Das Innenprofil 22 kann dabei direkt in die Dampferzeugerrohre 14 in der Art einer In- nenberippung 23 eingebracht sein. Alternativ können auch Einbauteile 24 als Innenprofil 22 dienen, was insbesondere eine Nachrüstung bestehender Durchlaufverdampfer 1 ermöglicht.The second steam generator tubes 14 now have a helical spring-shaped inner profile 22, which is shown in FIGS. 2 and 3. Its profile geometry is selected such that the friction pressure loss of the flow medium W in the steam generator tubes 14, generated by swirl and turbulence, is correspondingly high enough to ensure uniform flow within a row of tubes 11. This reduces temperature imbalances. The inner profile 22 can be introduced directly into the steam generator tubes 14 in the manner of an inner nip 23. Alternatively, built-in parts 24 serve as an inner profile 22, which in particular allows retrofitting existing continuous evaporator 1.
Der Effekt des Innenprofils 22 auf die Temperaturdifferenzen ist in den FIG 4 und 5 dargestellt. Sie zeigen jeweils eine graphische Darstellung der mittleren Rohrwandtemperatur 25 und der Rohraustrittswandtemperatur 27, aufgetragen gegen den Dampfanteil 29 des Strömungsmediums am Eintritt in das Rohr. FIG 4 zeigt dabei die Situation ohne Innenprofil 22. Hier variiert die mittlere Rohrwandtemperatur 25 zwischen ca. 460 0C und 360 °C, die Rohraustrittswandtemperatur 27 zwischen 480 0C und 370 0C, abhängig von Dampfgehalt 29. In FIG 5, die die Situation mit Innenprofil 22 erläutert, ist gezeigt, dass sich diese Variationen auf ca. 440 0C bis 390 0C bzw. 470 0C bis 405 °C reduzieren. Die Temperaturdifferenzen zwischen Rohren mit unterschiedlichem Dampfgehalt am Eintritt werden also deutlich reduziert.The effect of the inner profile 22 on the temperature differences is shown in FIGS. 4 and 5. They each show a graphical representation of the mean tube wall temperature 25 and the tube outlet wall temperature 27, plotted against the vapor fraction 29 of the flow medium at the inlet into the tube. 4 shows the situation without an inner profile 22. Here, the average tube wall temperature 25 varies between about 460 0 C and 360 ° C, the Rohraustrittswandtemperatur 27 between 480 0 C and 370 0 C, depending on the vapor content 29. In FIG 5, the Situation illustrated with inner profile 22, it is shown that reduce these variations to about 440 0 C to 390 0 C and 470 0 C to 405 ° C. The temperature differences between pipes with different steam content at the entrance are thus significantly reduced.
Durch die Verringerung der Temperaturdifferenzen von Rohren mit unterschiedlichem Dampfgehalt am strömungsseitigen Eintritt wird die mechanische Spannungsbelastung des Abhitze- dampferzeugers 2 reduziert und es ist eine besonders langeBy reducing the temperature differences of pipes with different steam content at the flow-side inlet, the mechanical stress load of the waste heat steam generator 2 is reduced and it is a particularly long
Lebensdauer bei gleichzeitig einfacher Bauweise durch Entfall der bisher üblichen Dehnbögen gewährleistet. Lifetime with a simple design ensured by omitting the usual stretch bends.

Claims

Patentansprüche claims
1. Durchlaufverdampfer (1) für einen Abhitzedampferzeuger (2) in liegender Bauweise mit einer ersten Verdampferheizflache (8), die eine Anzahl von im Wesentlichen vertikal angeordneten, von unten nach oben durchströmten ersten Dampferzeugerrohren (13) umfasst, und einer weiteren, der ersten Verdampferheizflache (8) strömungsmediumsseitig nachgeschalteten zweiten Verdampferheizflache (10), die eine Anzahl von weiteren, im Wesentlichen vertikal angeordneten, von unten nach oben durchströmten zweiten Dampferzeugerrohren (14) umfasst, wobei eine Anzahl von zweiten Dampferzeugerrohren (14) ein Innenprofil (22) aufweist.1. continuous evaporator (1) for a heat recovery steam generator (2) in horizontal construction with a first Verdampferheizflache (8) comprising a number of substantially vertically arranged, from bottom to top flowed through first steam generator tubes (13), and another, the first Evaporator heating surface (8) downstream of the second medium evaporation evaporator surface (10), which comprises a number of further, arranged substantially vertically, from bottom to top through the second steam generator tubes (14), wherein a number of second steam generator tubes (14) has an inner profile (22) ,
2. Durchlaufverdampfer (1) nach Anspruch 1, bei dem das Innenprofil (22) schraubenfederförmig ist.Second continuous evaporator (1) according to claim 1, wherein the inner profile (22) is helical spring-shaped.
3. Durchlaufverdampfer (1) nach Anspruch 1 oder 2, bei dem die Profilgeometrie des jeweiligen Innenprofils (22) derart gewählt ist, dass sich über das jeweilige zweite Dampferzeugerrohr (14) ein vorgegebener Reibungsdruckverlust des Strömungsmediums einstellt.3. continuous evaporator (1) according to claim 1 or 2, wherein the profile geometry of the respective inner profile (22) is selected such that adjusts a predetermined friction pressure loss of the flow medium via the respective second steam generator tube (14).
4. Durchlaufverdampfer (1) nach einem der Ansprüche 1 bis 3, bei dem das jeweilige Innenprofil (22) in der Art einer4. continuous evaporator (1) according to one of claims 1 to 3, wherein the respective inner profile (22) in the manner of a
Innenberippung (23) in das jeweilige zweite Dampferzeugerrohr (14) eingebracht ist.Inner ribbing (23) is introduced into the respective second steam generator tube (14).
5. Durchlaufverdampfer (1) nach einem der Ansprüche 1 bis 3, bei dem das jeweilige Innenprofil (22) als Einbauteil (24) in das jeweilige zweite Dampferzeugerrohr (14) eingesetzt ist .5. continuous evaporator (1) according to one of claims 1 to 3, wherein the respective inner profile (22) is inserted as a built-in part (24) in the respective second steam generator tube (14).
6. Durchlaufverdampfer (1) nach einem der Ansprüche 1 bis 5, bei dem eine Anzahl von zweiten Dampferzeugerrohren (14) einander heizgasseitig als Rohrreihen (11) hintereinander geschaltet sind. 6. continuous evaporator (1) according to one of claims 1 to 5, wherein a number of second steam generator tubes (14) are connected to each other on the heating gas side as a row of tubes (11) in series.
7. Durchlaufverdampfer (1) nach einem der Ansprüche 1 bis 6, bei dem die erste Verdampferheizflache (8) der zweiten Verdampferheizflache (10) heizgasseitig nachgeschaltet ist.7. continuous evaporator (1) according to one of claims 1 to 6, wherein the first evaporator heating surface (8) of the second evaporator heating surface (10) is connected downstream of the heating gas.
8. Abhitzedampferzeuger (2) mit einem Durchlaufverdampfer (1) nach einem der Ansprüche 1 bis 7.8. heat recovery steam generator (2) with a continuous evaporator (1) according to one of claims 1 to 7.
9. Abhitzedampferzeuger (2) nach Anspruch 8, dem heizgasseitig eine Gasturbine vorgeschaltet ist. 9. heat recovery steam generator (2) according to claim 8, the heating gas side is preceded by a gas turbine.
EP10718147A 2009-06-10 2010-04-30 Continuous evaporator Withdrawn EP2440847A2 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102009024587A DE102009024587A1 (en) 2009-06-10 2009-06-10 Flow evaporator
PCT/EP2010/055886 WO2010142495A2 (en) 2009-06-10 2010-04-30 Continuous evaporator

Publications (1)

Publication Number Publication Date
EP2440847A2 true EP2440847A2 (en) 2012-04-18

Family

ID=43069748

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10718147A Withdrawn EP2440847A2 (en) 2009-06-10 2010-04-30 Continuous evaporator

Country Status (12)

Country Link
US (1) US20120073520A1 (en)
EP (1) EP2440847A2 (en)
JP (1) JP2012529613A (en)
KR (1) KR20120027021A (en)
CN (1) CN102667337A (en)
AU (1) AU2010257702A1 (en)
BR (1) BRPI1013116A2 (en)
CA (1) CA2764939A1 (en)
DE (1) DE102009024587A1 (en)
RU (1) RU2011153331A (en)
TW (1) TW201043874A (en)
WO (1) WO2010142495A2 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2180250A1 (en) * 2008-09-09 2010-04-28 Siemens Aktiengesellschaft Continuous-flow steam generator
EP2390567A1 (en) * 2010-05-31 2011-11-30 Siemens Aktiengesellschaft Device for producing fixture units for steam generator pipes
DE102013206014A1 (en) * 2013-04-05 2014-10-09 Dürr Systems GmbH Energy converter system and assemblies for this
CN105202509B (en) * 2014-06-20 2019-05-31 松下知识产权经营株式会社 Evaporator, Rankine cycle devices and cogeneration system
CN108263904B (en) * 2018-01-15 2020-04-14 芜湖航天特种电缆厂股份有限公司 Preheating cable transmission machine
CN110094709B (en) * 2019-05-28 2024-04-26 上海锅炉厂有限公司 Direct-current evaporator and design method thereof

Family Cites Families (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63189793A (en) * 1987-02-02 1988-08-05 Mitsubishi Electric Corp Heat transfer pipe for evaporation and condensation
EP0349834B1 (en) * 1988-07-04 1996-04-17 Siemens Aktiengesellschaft Once-through steam generator
DE58909259D1 (en) * 1989-10-30 1995-06-29 Siemens Ag Continuous steam generator.
DE4333404A1 (en) * 1993-09-30 1995-04-06 Siemens Ag Continuous steam generator with vertically arranged evaporator tubes
US5772793A (en) * 1996-08-28 1998-06-30 The United States Of America As Represented By The United States Department Of Energy Tube-in-tube thermophotovoltaic generator
DE19644763A1 (en) * 1996-10-28 1998-04-30 Siemens Ag Steam generator pipe
DE19651678A1 (en) * 1996-12-12 1998-06-25 Siemens Ag Steam generator
DE19717158C2 (en) * 1997-04-23 1999-11-11 Siemens Ag Continuous steam generator and method for starting up a continuous steam generator
KR100439080B1 (en) * 1997-06-30 2004-07-05 지멘스 악티엔게젤샤프트 Waste heat steam generator
US5924389A (en) * 1998-04-03 1999-07-20 Combustion Engineering, Inc. Heat recovery steam generator
DE19914760C1 (en) * 1999-03-31 2000-04-13 Siemens Ag Fossil-fuel through-flow steam generator for power plant
EP1288567A1 (en) * 2001-08-31 2003-03-05 Siemens Aktiengesellschaft Steam generator and process for starting a steam generator with a heating gas channel through which a heating gas can flow in a substantially horizontal direction
EP1443268A1 (en) * 2003-01-31 2004-08-04 Siemens Aktiengesellschaft Steam generator
US6957630B1 (en) * 2005-03-31 2005-10-25 Alstom Technology Ltd Flexible assembly of once-through evaporation for horizontal heat recovery steam generator
EP1793164A1 (en) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Steam generator tube, method of manufacturing the same and once-through steam generator
EP1793163A1 (en) * 2005-12-05 2007-06-06 Siemens Aktiengesellschaft Steam generator tube, method of manufacturing the same and once-through steam generator
EP2182278A1 (en) * 2008-09-09 2010-05-05 Siemens Aktiengesellschaft Continuous-flow steam generator

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2010142495A2 *

Also Published As

Publication number Publication date
BRPI1013116A2 (en) 2016-04-05
US20120073520A1 (en) 2012-03-29
RU2011153331A (en) 2013-07-20
JP2012529613A (en) 2012-11-22
DE102009024587A1 (en) 2010-12-16
CA2764939A1 (en) 2010-12-16
KR20120027021A (en) 2012-03-20
CN102667337A (en) 2012-09-12
WO2010142495A3 (en) 2012-06-07
WO2010142495A2 (en) 2010-12-16
TW201043874A (en) 2010-12-16
AU2010257702A1 (en) 2012-01-12

Similar Documents

Publication Publication Date Title
EP2438351B1 (en) Continuous evaporator
EP1588095B1 (en) Steam generator
EP2440847A2 (en) Continuous evaporator
EP2324285B1 (en) Heat recovery steam generator
EP2321578B1 (en) Continuous steam generator
EP2438352B1 (en) Once-through evaporator
EP2324287B1 (en) Continuous-flow steam generator
EP2324286B1 (en) Continuous-flow steam generator
EP2409078B1 (en) Method for designing a continuous evaporator
EP3014177B1 (en) Continuous flow steam generator with a two-pass boiler design
WO2015039831A2 (en) Combined cycle gas turbine plant having a waste heat steam generator
WO2000042352A1 (en) Fossil fuel fired steam generator
DE102010038883B4 (en) Once-through steam generator
DE102005023082B4 (en) Through steam generator
DE102010038885B4 (en) Once-through steam generator
EP2564117B1 (en) Steam generator
DE381001C (en) Water tube boiler
DE102011004272A1 (en) Continuous evaporator for steam generator of solar thermal tower power plant, comprises evaporator heating surface with multiple vertically arranged steam generator tubes, through which flow medium flows from bottom to top

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

17P Request for examination filed

Effective date: 20111207

AK Designated contracting states

Kind code of ref document: A2

Designated state(s): 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 SE SI SK SM TR

R17D Deferred search report published (corrected)

Effective date: 20120607

RAP1 Party data changed (applicant data changed or rights of an application transferred)

Owner name: SIEMENS AKTIENGESELLSCHAFT

17Q First examination report despatched

Effective date: 20130319

DAX Request for extension of the european patent (deleted)
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: 20130730