EP0717826B1 - Dampferzeuger - Google Patents

Dampferzeuger Download PDF

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Publication number
EP0717826B1
EP0717826B1 EP94926416A EP94926416A EP0717826B1 EP 0717826 B1 EP0717826 B1 EP 0717826B1 EP 94926416 A EP94926416 A EP 94926416A EP 94926416 A EP94926416 A EP 94926416A EP 0717826 B1 EP0717826 B1 EP 0717826B1
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EP
European Patent Office
Prior art keywords
boiler
furnace
steam
boiler according
back pass
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP94926416A
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English (en)
French (fr)
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EP0717826A1 (de
Inventor
Lennart Nordenberg
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Metso Fiber Karlstad AB
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Kvaerner Pulping Technologies AB
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Priority claimed from CA002105602A external-priority patent/CA2105602A1/en
Application filed by Kvaerner Pulping Technologies AB filed Critical Kvaerner Pulping Technologies AB
Publication of EP0717826A1 publication Critical patent/EP0717826A1/de
Application granted granted Critical
Publication of EP0717826B1 publication Critical patent/EP0717826B1/de
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  • the invention relates to boilers for the production of steam having a maximum capacity of 100 ton/hr or more, and more particularly to boilers capable of burning solid fuel.
  • Such boilers comprise a furnace and a back pass, wherein said furnace and said back pass are mounted in close relation to each other.
  • Such boilers are used as large power plants to produce superheated steam for driving steam-powered turbines.
  • GB-A-1 418 456 discloses a small scale conventional steam boiler comprising a furnace having a substantially constant rectangular cross-section and a back pass with a substantially constant rectangular cross-section, wherein the furnace and back pass are mounted in close relation to each other, and wherein means are provided for superheating the steam, the steam superheating means being positioned within said back pass, so that no means for superheating the steam are positioned within the furnace.
  • the boiler is a low capacity boiler using either oil or gas as fuel, said boiler being fired from a number of locations around the boiler in either the floor or roof.
  • the fuel burned in solid fuel boilers principally comprises biomass, bark, deinking sludge and primary sludge as well as possible auxiliary fuels such as oil and gas.
  • steam generating boilers which may be considered as prior art for this invention, are generally constructed with a central furnace and one or more lower grates on to which fuel is fed for burning.
  • the walls of the furnace may comprise pipes for containing the water/steam which is to be passed, in a first stage, to the water/steam separation drum at the upper part of the furnace before proceeding on to a superheating stage.
  • the boilers of the prior art are expensive to construct due to the overall number of pipes, the type of pipes involved and due to the manner in which they are attached to various structural support members. Additionally, the systems for separating and later superheating the steam are complicated, difficult to design, difficult to manufacture and fit as well as being difficult to service.
  • the steam separation system which comprises a separation drum (e.g. a cyclone separator) normally requires several pipes each extending from the upper steam side of the drum all the way to the inlets for the superheater(s), the superheaters being themselves positioned vertically in the furnace or the back draft.
  • the fitting of such a multiplicity of pipes is inconvenient and expensive, but has previously been found necessary if an even steam distribution along the drum is to be achieved.
  • Such an even distribution is however important in order not to disturb the moisture-removing function of the de-mister element which otherwise would produce detrimental effects on the turbine, such as deposits which cause unbalance in the rotor.
  • An object of the invention is thus to improve the overall structure and efficiency of a boiler by the novel construction of its various elements and/or their combination.
  • a boiler system may be provided which is, amongst other things, very compact, flexible with respect to its size and which results in low manufacturing, assembly, installation and maintenance costs.
  • the boiler according to the invention is defined in claim 1.
  • the boiler of this invention is of the large type i.e. having a capacity capable of producing steam at the rate of 100 tons per hour or more.
  • the boiler consists of two main sections, a furnace section 1 and one or more back pass (or back draft) sections 2, 20.
  • the first back pass 2 and the furnace 1 are separated from each other by means of a common dividing wall 3.
  • the furnace and the back pass could however be separated from one another by a certain distance, thus requiring individual opposing walls on each of the sections 1 and 2.
  • the fuel is fed from a feed unit 7, commonly a series of driven screw feeders 7' (see Fig.lc), onto a first sloping grate section 4 which is constructed as a bare-tube membrane floor having individual pipes connected to each other by "fins" of flat sheet metal.
  • the fins have a series of holes therein for the passage of air therethrough from the underside and are fitted with individual downstream-directed deflector plate sections (not depicted), known as eyelids, covering the holes to prevent the ingress of material from above the grate and also to minimise fluidizing of the bed.
  • a second grate section 5 e.g. of the reciprocating type such as a Kablitz grate, is positioned downstream of the first grate section 4.
  • This section could for example comprise stationary and alternately interposed movable members.
  • the members are typically serrated and stepped, and the reciprocating movement occurs at low velocity automatically over a period of e.g. a few minutes. In this way, fuel will be fed down along the grate towards the final or dump grate 6 where the ash is discharged onto an ash conveyor 8 below.
  • the dump grate 6 may simply be a manually operated grate which is actuated whenever the operator feels that this is required due to the build up of ash, or an automatically operated device functioning on e.g. a time basis, for instance twice a day.
  • the wall 3 is in fact arranged on a side of the furnace which is parallel to the direction of feed on the grate section 4, 5, 6 as is clearly shown in Figs. 1b and 1c.
  • the furnace is at an angle of 90° to the longitudinal section of the boiler.
  • the feeding means 7 has a direction of feed parallel with the wall(s) dividing the furnace from the back pass.
  • movable support such as sliding feet means for the base of the boiler must be provided in order to allow for expansion.
  • the design of the downcoming system as well as the distribution system can be significantly simplified since a smaller number of pipes is required compared to previous constructions.
  • the first back pass 2 for example, which contains the convection heating surfaces of the generating banks, can now be supplied by only two distribution pipes.
  • the arrows A, B and C in Fig. la denote the flow of primary, secondary and tertiary air respectively, which are input via suitable conduits from an air supply, e.g. a forced air supply from a fan.
  • an air supply e.g. a forced air supply from a fan.
  • a narrow throat or venturi section 12 is formed between the drying arch 10 and the burn-out arch 11 in order to allow a low amount of excess air to be used whilst still maintaining a low content of unburnt matter.
  • combustible gases and air are thus forced to mix.
  • improved burning can be effected by providing turbulence in this zone by means of tertiary air c being input at high velocity.
  • the furnace 1 presents an essentially constant rectangular cross-sectional area.
  • the back pass 2 has a cross-sectional area which is substantially rectangular and constant.
  • the ratio of the cross-sectional areas of the furnace to the back pass ideally lies in the range of 2:1 to 6:1. This fact is a major contributor which influences the overall cost effectiveness of the boiler, since it provides, in combination with the reduced total footprint (covered ground area) and the features of this high capacity boiler, a minimal use of pipes, ducts and supports.
  • both the furnace and back pass thus allow a great flexibility with respect to the choice of overall size of the boiler since the back pass and furnace can be constructed as modules which are easily fitted together to give the required size. Moreover, the size of both the back pass and furnace can be modified separately by further modular addition if this is required.
  • the overall structure of the boiler which in part relies on the position of the air inlets (whereby the majority of air inlets can be arranged on one side only (see later description) make such a modular structure and modification even more readily usable.
  • the air inlets supplying the furnace are able to be positioned, due to the compact structure and arrangement of the boiler (due to a large extent to the aforementioned 90° furnace/boiler arrangement), such that the air supply (e.g. main fan duct) may be positioned in one corner of the housing such that only the supply conduits 74 for drying air and the supply conduit(s) 75 for secondary and tertiary air run from one vertically extending side of the boiler to the other.
  • This minimal number of pipes ducts for channelling of air thus also allows easier modular expansion of the furnace and/or back pass.
  • the supply conduits for the secondary and tertiary air may if desired be joined in one joint conduit 75 which is divided by a separation wall 76 into two channels. Additionally, means for measuring the air-flow in said joint conduit may be provided, comprising one single unit which penetrates the separation wall 76 in said joint conduit.
  • One or more oil and/or gas inlets 9 for supplying oil and/or gas are positioned in the furnace for the case that either should be required for assisting ignition start-up and/or to cope with very high loads or severe load swings.
  • the hot flow gas from the furnace passes through one or more openings in the upper part of the furnace wall 3 and is directed downwardly into the back pass 2.
  • a water/steam separator drum 13 (e.g. including a cyclone separator) having a single steam outlet 14 is positioned at the top of the boiler.
  • This steam drum 13 will be described in more detail later.
  • further drums 13 may also be fitted.
  • the water/steam mixture which collects on the water side of the drum 13 after separation is transferred back to the walls of the boiler by means of pipes called "downcomers" which are normally present in large numbers in prior art devices.
  • downcomers which are normally present in large numbers in prior art devices.
  • the boiler of this invention it is now possible to limit the number of downcomers to less than four.
  • only two metal downcomers having a relatively large diameter and thickness of, for instance, 450 mm and 60 mm respectively, can be suitably used.
  • Such downcomers have sufficient strength in order that the downcomers themselves may provide the structural support for the drum 13 from below (bottom support).
  • the downcomers may even be used to provide support for other parts of the boiler.
  • Two downcomers of such dimension are more expensive than the many smaller ones of the prior art. However their use directly results in a significant number of more important advantages, which reduce overall cost significantly.
  • downcomers provide support for the drum, they will also have to be mounted, directly or indirectly on to some sliding arrangement to account for boiler expansion.
  • the pipes which are part of the sidewalls of the grate section may also function as part of the downcoming system for partial supply of the furnace boiler tubes, these being fed via a small number of large diameter distribution branches 67', 67" (see e.g Fig.1b) from the downcomers.
  • a secondary superheater stage 15 is arranged above a primary superheater stage 16, the inlet to the primary superheater being fed from the outlet 14 of the drum 13 into a header 49, 50 (see e.g. Fig.3).
  • a header 49, 50 see e.g. Fig.3
  • Efficiency of the superheating stage may be increased by using an attemperator 21 (known per se) for injecting water into the steam between the two superheating stages 15 and 16.
  • Reference 17 denotes a steam generation bank section which uses heat from the flow gas for supplying additional steam to the drum 13. Whilst only two banks are shown, it is clear that any suitable number may be used.
  • the generation bank 17 is preferably formed by convection boiler tubes which form a flag heater surface (i.e. in the shape of a flag). Said boiler tubes may also be part of the wall which divides the boiler from the back draft 2 and thus provides support therefor.
  • the hot flow gas On arriving at a lower section of the back pass 2, the hot flow gas is diverted back upwardly before arriving at a second back pass 20, in which both an air heater 18 and one or more economizer banks 19 are positioned.
  • the air heater 18 is used for additional heating of the primary air A which is fed from the fan into the sloping bare-tube grate 4 in order to act as drying air, e.g. for wet bark, and may thus be capable of heating the air to 350°C or more. Additional means may also be provided for heating the primary air such as a steam coil air heater (not shown).
  • the economizer banks 19 are used to extract remaining heat in the flow gas for initially heating the feed water used in e.g. the furnace walls.
  • the walls of the boiler comprise a series of panels, a portion of one of said panels being shown in Fig.2.
  • a panel consists of pipes 30, 30' etc. for carrying the water/steam mixture in the boiler, said pipes being interconnected by fins 31 of metal plate which are double seam welded (i.e. seam welded on either side) onto one side of two respective pipes along diametrically opposed parts of each pipe as shown.
  • the superheaters are positioned substantially horizontally in the back pass.
  • the superheaters are hung in the upper part of the furnace such that the superheater pipes extend vertically downwardly into the furnace.
  • a complicated design and fitting of various connection brackets is required between the individual pipes of the superheaters and the walls of the furnace to enable an adequately rigid structure to be produced capable of withstanding the thermal loads which would otherwise lead to bending and distortion of the tubes.
  • Fig.3 shows a partially schematic representation of one panel of a superheater 15 or 16 of Fig. la, located inside the back pass 2. Positioning in the back pass allows the superheater(s) to be shielded from flame, which not only guarantees a longer life, but also reduces the formation of deposits on the superheaters with direct flame action and thus maintains efficiency.
  • the temperature in the back pass is also less than in the furnace.
  • the walls of the back pass are made up of alternate pipes 45, 46 and fins 47, 48. This structure can be seen clearly in Figs. 5 and 6. As is shown, the pipes 40, 41, 42, 43 of the superheater are positioned between the steam header 50 and the steam header 49.
  • the pipes 40-43 are positioned horizontally and pass across substantially the total width of the back pass 2 between the vertical walls.
  • the free length of the pipes i.e. the self supporting length of the pipes
  • the pipes 40 to 43 might require only one, centrally-positioned, intermediate, vertical hanger support (not shown) giving a free length of approximately 3m for the pipes.
  • the pipes diverge downwardly as substantially vertical sections 40'-43' and then back horizontally to the superheater header 50.
  • double seam-welded fins 51 are arranged between each of the pipes 40-43 to act as the support means to resist the deformation forces of thermal loading at this point.
  • the prior art method which required expensive and time consuming fitting and installation of many clamps and brackets etc. between the individual pipes and to the walls of the boiler is no longer required.
  • the thermal load on the fins 51 results from the temperature of the flue gas at this point which may be around 800°C for example.
  • the steam in the pipes 40 to 43 is at a lower temperature and, due to the fact that the fins 51 are connected to the pipes along a large portion thereof by continuous double seam welds, the fins 51 are thus effectively cooled by the effect of the steam.
  • the distance between the pipes 45 and 45' in the back pass wall, as shown in Fig.5, which determines the width of the fins 47 which span this distance, is such that the diameter of the pipes 40 to 43 is less than the distance between two adjacent pipes 45, 45'.
  • the horizontal pipes 40 to 43 may pass through the fin 47 of the wall panel without involving the complications of bending the various pipes, as required by vertical superheaters.
  • This larger dimensioning of the fin width between pipes 45 and 45', to accommodate the pipes 40-43, is made possible due to the fact that the superheater is positioned in the back pass where lower temperatures occur.
  • the back pass wall closest to, or in common with, the furnace is formed by alternating pipes 46, 46' and fin sections 48, 48' and 48" similar to the other wall of Fig.5.
  • the vertically extending portion 40' of the superheater (see also Fig.4) is supported against sideways movement by its position between the pipes 46 and 46' and the use of a pin 90 connection with associated sealing cap 91 (see Fig.6).
  • no bracket or clamp of any type is required to secure the part 40' to the fin 48, which results in significantly easier installation and maintenance compared to prior art installations.
  • Sootblowing means 80, 81 such as steam lance means, are positioned in the back pass 2 and act to clean the surfaces of the various elements such as the superheaters. Due to the arrangement of the boiler the steam lances, including (where required) further sootblowing means for the generator banks etc., may be placed in the back pass sections without requiring any extra space in the building which houses the boiler, than that provided already.
  • Figs. 7 and 8 show a steam drum 60 with a steam outlet 61, corresponding respectively to drum 13 and pipe 14 in Figs.la to 1c.
  • the steam drum may have a diameter of about 2 metres, some 80mm wall thickness and about 100mm end face thickness.
  • Access doors 63 and instrument connections 64 are located at either end of the drum and two downcomers 67 support the drum from below.
  • a steam demister 65 of a per se known type which is the final separation point of any water from the steam which is present in the drum having been inlet through the vapour/water inlets 66.
  • a further manner of arriving at the same effect as described above is to have a plurality of equal diameter pipes 62a to 62f feeding into one single saturated steam pipe 61.
  • the steam connection pipes 62a to 62f are then provided with throttling means which would be either preset or variable, but arranged so that a substantially quadratic relationship of pressure drop between the outlet connections 62a to 62f is achieved. In this way, the distance between the pipes may be made constant, in addition to them having the same internal diameter.
  • fuel such as wet bark for example
  • feed unit 7 After start-up of the boiler, fuel, such as wet bark for example, is fed in from feed unit 7.
  • the amount of fuel fed into the furnace depends on the prevailing load conditions.
  • the fuel is first dried on the sloping bare-tube grate 4 by primary, high-temperature (e.g. above 100°C or even more than 350°C) drying air A coming from below the grate 4. Due mainly to gravity, the fuel passes down the grate 4 on to the reciprocating grate 5 (e.g. a Kablitz grate) where it is transported by reciprocal motion along the grate while being fired before it has become ash to be discharged from the dump grate 6.
  • the reciprocating grate 5 e.g. a Kablitz grate
  • the heat output of the boiler can be increased by supplying more air and more fuel, and assisted by supplying auxiliary fuel via inlets 9, connected to fuel and air sources.
  • the heat energy produced heats the water/steam mixture which is present in the furnace walls such that steam passes to the drum 13 for further separation.
  • the hot gas flow proceeds onward downstream to the back pass 2 after passing through the dividing wall 3, heating the various surfaces in its path.
  • the steam which has entered drum 13, 60 via inlets 66 passes through the cyclone separator unit(s) in order that water will be separated from the steam.
  • This separated water is passed back to the boiler walls via the downcomers 67 which feed the water partly into branch distribution pipes such as 67'and 67".
  • the steam passes through demister 65 and into the various outlets 62a-f into the pipe 61 which feeds into the primary superheater 16.
  • the steam flows through these pipes and is further heated by the flow gas passing thereover.
  • the steam passes through an attemperator 21, which e.g. injects water and cools it, and then into the secondary superheater 15.
  • the steam is then heated as it passes through the superheater 15 and is then finally used to drive a turbine.

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  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Combustion Of Fluid Fuel (AREA)

Claims (23)

  1. Kessel zur Erzeugung von Dampf, bei dem der Kessel einen Feuerraum mit einem im wesentlichen konstanten rechtwinkligen Querschnitt und eine Rückführung mit einem im wesentlichen konstanten rechtwinkligen Querschnitt umfaßt, wobei der Feuerraum und die Rückführung in enger Beziehung zueinander montiert sind und Mittel zum Überhitzen des Dampfes vorgesehen sind, wobei die Mittel zum Überhitzen des Dampfes innerhalb der Rückführung positioniert sind, so daß keine Mittel zum Überhitzen des Dampfes innerhalb des Feuerraums positioniert sind, dadurch gekennzeichnet, daß der Kessel eine maximale Leistung von 100 Tonnen/Stunde oder mehr aufweist und daß der Feuerraum mit einem geneigt angeordneten Rost ausgestattet ist, dessen Zuführungsrichtung parallel zu einer oder mehreren Wänden verläuft, die den Feuerraum von der Rückführung trennen.
  2. Kessel nach Anspruch 1, bei dem der Feuerraum und die Rückführung durch eine gemeinsame Wand getrennt sind.
  3. Kessel nach Anspruch 1, bei dem es sich bei dem Kessel um einen Kessel für Festbrennstoff, insbesondere für Biomassebrennstoff, handelt.
  4. Kessel nach Anspruch 1, bei dem bestimmte Teile des Kessels als Module konstruiert sind, so daß die Größe des Feuerraums und die Größe der Rückführung unabhängig voneinander festgelegt werden können.
  5. Kessel nach Anspruch 1, bei dem der Feuerraum und die Rückführung jeweils eine Querschnittsfläche aufweisen, und bei dem das Verhältnis zwischen der Querschnittsfläche des Feuerraums und der Rückführung zwischen 2:1 - 6:1 liegt.
  6. Kessel nach Anspruch 1, bei dem der Feuerraum Wände umfassende Seiten besitzt und mindestens eine der Seiten des Kessels frei von schräg verlaufenden Rohren und dergleichen ist, so daß der Kessel bei seiner Konstruktion durch Erweiterung an dieser Seite problemlos vergrößert werden kann.
  7. Kessel nach Anspruch 1, der weiterhin mit einer Austragsvorrichtung für Asche ausgestattet ist, wobei das geneigt angeordnete Rost so positioniert ist, daß die Austragsvorrichtung in der Nähe einer Außenwand des Kessels angeordnet ist.
  8. Kessel nach Anspruch 1, der weiterhin eine Dampftrommel und mehrere Rücklaufrohre umfaßt, die als Abstützung der Dampftrommel von unten vorgesehen sind, wobei die Anzahl der Rücklaufrohre weniger als vier beträgt.
  9. Kessel nach Anspruch 8, bei dem die Anzahl der Rücklaufrohre lediglich zwei beträgt.
  10. Kessel nach Anspruch 1, bei dem der Kessel ein Rost mit Seitenwänden besitzt, wobei die Rostseitenwände als Teil des Rücklaufsystems zur teilweisen Beschickung von Kesselrohren innerhalb des Feuerraums dienen.
  11. Kessel nach Anspruch 1, bei dem eine Rußblaseinrichtung, einschließlich Rußbläser, so in der Rückführung positioniert ist, daß für die Anordnung der Rußbläser innerhalb eines den Kessel umgebenden Gebäudes kein zusätzlicher Platz erforderlich ist.
  12. Kessel nach Anspruch 1, bei dem Konvektionskesselrohre in der Rückführung positioniert sind, wobei diese Rohre die Form einer Platte aufweisen.
  13. Kessel nach Anspruch 12, bei dem die Konvektionskesselrohre an einer der äußeren Seitenwände des Kessels montiert sind.
  14. Kessel nach Anspruch 1, bei dem eine oder mehrere Überhitzerstufen vorgesehen sind, wobei jede der Überhitzerstufen Tafeln aus horizontal verlaufenden und sich im wesentlichen über die gesamte Breite der Rückführung erstreckenden Rohren mit dazwischen angeschweißten Metallblechrippen umfaßt.
  15. Kessel nach Anspruch 1, bei dem die Rückführung Wände besitzt, wobei diese Wände durch Rippen verbundene Rohr-Tafeln umfaßt, wobei diese Rippen eine solche Breite aufweisen, daß die Überhitzerrohre ohne Biegung der Rohre in der Wand durch die Rippen geführt werden können, d.h. der Durchmesser der Rohre für den Überhitzer geringer als oder von gleicher Größe wie die Breite einer Rippe von einem dieser Paneele ist.
  16. Kessel nach Anspruch 1, bei dem ein Verbindungsrohr zwischen einem primären und einem sekundären Überhitzer vorgesehen ist, wobei lediglich ein Verbindungsrohr vorgesehen und nur ein Temperaturregler zwischen dem primären und dem sekundären Überhitzer angeordnet ist.
  17. Kessel nach Anspruch 1, bei dem nur eine Zufuhrleitung zwischen einer Reihe von Dampfaustritten einer Dampftrommel und einem primären Überhitzer angeordnet ist.
  18. Kessel nach Anspruch 1 oder 17, bei dem eine erste und eine zweite Dampfaustrittsverbindung, die nebeneinanderliegen, bei dem von einer Dampfabscheidetrommel durch einen ersten Abstand L1 getrennt sind, und bei dem ein zweiter und ein dritter Dampfaustritt durch einen Abstand L2 getrennt sind, wobei dieser Abstand L nach der Gleichung Ln = a + knb ermittelt wird, wobei "a" und "k" Konstanten sind, "b" im wesentlichen 2 beträgt und "n" der nte Abstand von "L" ist.
  19. Kessel nach Anspruch 1 oder 18, bei dem mehrere Dampfaustrittsverbindungen von einer Dampftrommel zu einer Zufuhrleitung vorgesehen sind, die einen primären Überhitzer speist, wobei sich diese Dampfaustritte individuell drosseln lassen, um für ein im wesentlichen quadratisches Druckabfallverhältnis zwischen angrenzenden Dampfaustritten zu sorgen, so daß gleichmäßige Strömungsbedingungen über die Länge der Dampftrommel geschaffen werden.
  20. Kessel nach Anspruch 1, bei dem mehr als 60% der in dem Feuerraum benötigten Luft diesem Feuerraum von einer Seite des Kessels aus zugeführt werden.
  21. Kessel nach Anspruch 1, bei dem dem Feuerraum Luft durch Zufuhrleitungen für Primärluft, Sekundärluft und Tertiärluft zugeführt und ein Teil der Primärluft als Trocknungsluft zugeführt wird, wobei die Zufuhrleitungen so angeordnet sind, daß lediglich die Zufuhrleitungen für die Trocknungsluft und die Zufuhrleitungen für die Sekundär- und Tertiärluft von einer sich vertikal erstreckenden Seite des Kessels aus zu einer anderen verlaufen.
  22. Kessel nach Anspruch 21, bei dem die Zufuhrleitungen für die Sekundär- und Tertiärluft zu einer gemeinsamen Leitung verbunden sind, die in zwei Kanäle unterteilt ist.
  23. Kessel nach Anspruch 22, bei dem Mittel zur Messung des Luftstroms in der einen gemeinsamen Leitung vorgesehen sind, wobei diese Mittel aus einer einzelnen Einheit bestehen, die durch eine Trennwand in der einen gemeinsamen Leitung geführt ist.
EP94926416A 1993-09-07 1994-08-24 Dampferzeuger Expired - Lifetime EP0717826B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CA2105602 1993-09-07
CA002105602A CA2105602A1 (en) 1993-09-07 1993-09-07 Steam boiler
PCT/SE1994/000761 WO1995007437A1 (en) 1993-09-07 1994-08-24 Steam boiler

Publications (2)

Publication Number Publication Date
EP0717826A1 EP0717826A1 (de) 1996-06-26
EP0717826B1 true EP0717826B1 (de) 1999-06-23

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EP94926416A Expired - Lifetime EP0717826B1 (de) 1993-09-07 1994-08-24 Dampferzeuger

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EP (1) EP0717826B1 (de)
AT (1) ATE181592T1 (de)
BR (1) BR9407396A (de)
DE (1) DE69419257T2 (de)
FI (1) FI111751B (de)

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Publication number Publication date
FI111751B (fi) 2003-09-15
BR9407396A (pt) 1996-11-05
ATE181592T1 (de) 1999-07-15
FI961050A0 (fi) 1996-03-07
EP0717826A1 (de) 1996-06-26
FI961050L (fi) 1996-03-29
DE69419257D1 (de) 1999-07-29
DE69419257T2 (de) 2000-02-03

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