EP1144910B1 - Fossilbeheizter dampferzeuger - Google Patents

Fossilbeheizter dampferzeuger Download PDF

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Publication number
EP1144910B1
EP1144910B1 EP00902545A EP00902545A EP1144910B1 EP 1144910 B1 EP1144910 B1 EP 1144910B1 EP 00902545 A EP00902545 A EP 00902545A EP 00902545 A EP00902545 A EP 00902545A EP 1144910 B1 EP1144910 B1 EP 1144910B1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
steam generator
evaporator tubes
tubes
flow medium
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP00902545A
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German (de)
English (en)
French (fr)
Other versions
EP1144910A1 (de
Inventor
Joachim Franke
Rudolf Kral
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
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Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP1144910A1 publication Critical patent/EP1144910A1/de
Application granted granted Critical
Publication of EP1144910B1 publication Critical patent/EP1144910B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • F22B21/34—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes grouped in panel form surrounding the combustion chamber, i.e. radiation boilers
    • 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
    • F22B37/40—Arrangements of partition walls in flues of steam boilers, e.g. built-up from baffles
    • 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
    • F22B21/34—Water-tube boilers of vertical or steeply-inclined type, i.e. the water-tube sets being arranged vertically or substantially vertically built-up from water tubes grouped in panel form surrounding the combustion chamber, i.e. radiation boilers
    • F22B21/346—Horizontal radiation boilers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22B—METHODS OF STEAM GENERATION; STEAM BOILERS
    • F22B31/00—Modifications of boiler construction, or of tube systems, dependent on installation of combustion apparatus; Arrangements of dispositions of combustion apparatus
    • F22B31/04—Heat supply by installation of two or more combustion apparatus, e.g. of separate combustion apparatus for the boiler and the superheater respectively

Definitions

  • the invention relates to a steam generator having a first and a second combustion chamber, each having a number of fossil fuel burners, wherein the first and the second combustion chamber are designed for an approximately horizontal main flow direction of the heating gas, wherein the first and the second combustion chamber lead into a common horizontal gas train upstream of a vertical gas train in a vertical gas train.
  • the energy content of a fuel used for evaporation of a flow medium in the steam generator In a power plant with a steam generator, the energy content of a fuel used for evaporation of a flow medium in the steam generator.
  • the steam generator has evaporator tubes for the evaporation of the flow medium, the heating of which leads to an evaporation of the flow medium guided therein.
  • the steam provided by the steam generator can in turn be provided, for example, for a connected external process or else for the drive of a steam turbine. If the steam drives a steam turbine, usually a generator or a working machine is operated via the turbine shaft of the steam turbine.
  • the power generated by the generator may be provided for feeding into a composite and / or island grid.
  • the steam generator can be designed as a continuous steam generator.
  • a continuous steam generator is from the essay " Evaporator Concepts for Benson Steam Generators "by J. Franke, W. Köhler and E. Wittchow, published in VGB Kraftwerkstechnik 73 (1993), No. 4, pp. 352-360 , known.
  • 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.
  • Fossil-fired steam generators are typically designed for a particular type and quality of fuel and for a particular performance range. This means that the combustion chamber of the steam generator is adapted in its main dimensions, ie length, width, height, to the combustion and ash properties of the given fuel and to the predetermined power range. Therefore, each steam generator with its associated fuel and power range has an individual design of the combustion chamber with respect to the main dimensions.
  • the combustion chamber of a steam generator can be redesigned, for example, for a new power range and / or a fuel of other nature or quality.
  • it can be used on planning documents of existing steam generators.
  • With the help of the documents then usually an adjustment of the main dimensions of the combustion chamber to the requirements of the newly to be constructed steam generator.
  • the design of a steam generator for new given boundary conditions is still associated with a comparatively high design effort due to the complexity of the underlying systems. This is especially true if the respective steam generator is to have a particularly high overall efficiency.
  • Continuous steam generators are usually designed with a combustion chamber in a vertical design. This means that the combustion chamber is designed for a flow through the heating medium or heating gas in approximately vertical direction.
  • the combustion chamber can be followed by a horizontal gas train, wherein the transition from the combustion chamber in the horizontal gas train, a deflection of the Schugasstroms takes place in an approximately horizontal flow direction.
  • the combustion chamber generally requires due to the temperature-induced changes in length of the combustion chamber a framework on which the combustion chamber is hung. This requires considerable technical effort in the manufacture and assembly of the continuous steam generator, which is the greater, the greater the height of the continuous steam generator.
  • a particularly simple concept for a modular steam generator therefore offers a horizontally constructed combustion chamber with a first and a second combustion chamber, wherein the first and the second combustion chamber are designed for an approximately horizontal main flow direction of the heating gas, wherein the first and the second combustion chamber in open a common horizontal gas flue upstream of a vertical gas train.
  • the burners are arranged on the end wall of the first combustion chamber and on the end wall of the second combustion chamber, that is on the surrounding wall of the first and the second combustion chamber, which faces the outflow opening to the horizontal gas train, and both in the first and in the second combustion chamber arranged the height of the horizontal gas flue in the combustion chamber wall.
  • the two combustion chambers are flowed through by the heating gas in approximately horizontal main flow direction during operation of the steam generator.
  • Such a steam generator is from the AT 376 026 B known.
  • the invention is based on the object of specifying a steam generator of this type, in which material damage and undesired contamination of the horizontal gas flue, for example, due to the entry of molten ash of a high temperature, are kept particularly low.
  • This object is achieved in that the defined by the distance from the end wall to the inlet region of the horizontal gas train length L of the first and the second combustion chamber at least equal to the Ausbrandwin of Fuel is at full load operation of the steam generator.
  • This horizontal length L of the first combustion chamber and the second combustion chamber will generally be greater than the height of the first and the second combustion chamber, measured from the funnel upper edge to the combustion chamber ceiling.
  • the steam generator is thus adaptable to the burn-out length of the fuel. Under Ausbrandrat of the fuel while the fuel gas velocity in the horizontal direction at a certain average heating gas temperature multiplied by the burnout time t A of the fuel to understand.
  • the maximum burn-out length for the respective steam generator results in the steam output of the steam generator at full load, the so-called full-load operation of the steam generator.
  • the burn-out time t A is the time required, for example, a coal dust grain medium size to burn out completely at a certain mean heating gas temperature.
  • the length L (indicated in m) of the first and the second combustion chamber is for a particularly favorable utilization of the combustion heat of the fossil fuel in an advantageous embodiment as a function of the BMCR value W (indicated in kg / s) of the steam generator, the number N Combustion chambers, the burn-out time t A (indicated in s) of the fuel and the outlet temperature T BRK (indicated in ° C) of the heating gas selected from the combustion chambers.
  • BMCR stands for Boiler maximum continuous rating and is the internationally commonly used term for the highest continuous output of a steam generator. This also corresponds to the design performance, ie the power at full load operation of the steam generator.
  • the end wall of the first combustion chamber and the end wall of the second combustion chamber, and the side walls of the first and the second combustion chamber, the horizontal gas flue and / or the vertical gas train are advantageously formed of gas-tight welded together, vertically arranged evaporator or steam generator tubes, wherein a number of Evaporator or steam generator tubes in each case can be acted upon in parallel with flow medium.
  • flow medium advantageously has a number of evaporator tubes on its inner side in each case a Herzoges thread forming ribs.
  • a pitch angle ⁇ between a plane perpendicular to the tube axis and the flanks of the arranged on the tube inside ribs is advantageously less than 60 °, preferably less than 55 °.
  • a so-called smooth tube, evaporator tube can namely no longer be maintained by a certain vapor content of the required for a particularly good heat transfer wetting the tube wall. If there is no wetting, there may be a partially dry pipe wall. The transition to such a dry pipe wall leads to a kind of heat transfer crisis with deteriorated heat transfer behavior, so that in general increase the pipe wall temperatures at this point particularly strong. In an internally ribbed pipe, however, this crisis of heat transfer now occurs only at a steam mass content> 0.9, ie shortly before the end of the evaporation, compared to a smooth pipe. This is due to the spin experienced by the flow through the spiral ribs.
  • a number of the evaporator tubes of the combustion chamber advantageously has means for reducing the flow of the flow medium. It proves to be particularly advantageous if the means are designed as throttle devices. Throttling devices can be, for example, internals in the evaporator tubes, which reduce the pipe inside diameter at a point in the interior of the respective evaporator tube. In this case, also prove to be means for reducing the flow in a multiple parallel lines comprehensive piping system advantageous through which the evaporator tubes of the combustion chamber flow medium can be fed. In one line or in several lines of the line system, for example, throttle valves can be provided.
  • Adjacent evaporator or steam generator tubes are advantageously welded together via metal bands, so-called fins, gas-tight.
  • the fin width affects the heat input into the steam generator tubes. Therefore, the fin width is preferably adapted depending on the position of the respective evaporator or steam generator tubes in the steam generator to a gas side prescribable heating profile. In this case, a typical heating profile determined from empirical values or else a rough estimate, such as, for example, a step-shaped heating profile, can be predefined as the heating profile. Due to the suitably chosen fin widths, heat input into all evaporator or steam generator tubes is achievable even with very different heating of different evaporator or steam generator tubes, so that temperature differences at the outlet of the evaporator or steam generator tubes are kept particularly low. In this way, premature material fatigue is reliably prevented. As a result, the steam generator on a particularly long life.
  • the tube inner diameter of a number of the evaporator tubes of the first and the second combustion chamber is selected depending on the respective position of the evaporator tubes in the first and the second combustion chamber. In this way, a number of the evaporator tubes of the first and the second combustion chamber can be adapted to a gas-side prescribable heating profile. As a result, temperature differences at the outlet of the evaporator tubes of the first and the second combustion chamber are kept particularly low.
  • a number of parallel-connected evaporator tubes which are assigned to the first or the second combustion chamber, preceded by a common inlet collector system for the flow medium and connected downstream of a common outlet collector system.
  • a designed in this embodiment steam generator allows reliable pressure equalization between the parallel connected evaporator tubes and thus a particularly favorable distribution of the flow medium in the flow through the evaporator tubes.
  • the respective inlet header system may be preceded by a line system provided with throttle fittings.
  • the evaporator tubes of the end wall of the first and the second combustion chamber are advantageously upstream of the evaporator tubes of the side walls of the first and the second combustion chamber flow medium side. This ensures a particularly favorable cooling of the end wall of the first and the second combustion chamber.
  • a number of superheater heating surfaces are advantageously arranged, which are arranged approximately perpendicular to the main flow direction of the hot gas and whose tubes are connected in parallel for a flow through the flow medium.
  • These arranged in a hanging design, also referred to as Schottsammlung lake, Studentshitzersammlung lake are predominantly heated convection and downstream of the evaporator tubes of the first and the second combustion chamber downstream of the flow medium side. This ensures a particularly favorable utilization of the supplied via the burner fuel gas heat.
  • the vertical gas train has a number of convection heating surfaces which are formed from tubes arranged approximately perpendicular to the main flow direction of the heating gas. These tubes of a convection heating surface are connected in parallel for flow through the flow medium. These convection heating surfaces are heated predominantly convection.
  • the structure of the combustion chamber is advantageously provided in a modular manner.
  • similar modules prove to be particularly easy to use and allow in relation to a desired performance of the combustion chamber a particularly high degree of flexibility.
  • the modules should also make the combustion chamber particularly easy to enlarge or reduce.
  • the vertical gas train advantageously has an economizer.
  • the advantages achieved by the invention are, in particular, that the concept of a modular construction of the combustion chamber of the steam generator, this requires a particularly low design and manufacturing costs.
  • this requires a particularly low design and manufacturing costs.
  • the respective redesign of the dimensioning of the combustion chamber only the addition or removal of one or more combustion chambers is now provided in the design of the combustion chamber of the steam generator for a given power range and / or a certain fuel quality.
  • two or more combustion chambers of smaller power can be connected in parallel upstream of a common horizontal gas draft on the gas side.
  • the steam generator 2 according to FIG. 1 is associated with a power plant not shown, which also includes a steam turbine plant.
  • the steam generated in the steam generator is used to drive the steam turbine, which in turn drives a generator for generating electricity.
  • the electricity generated by the generator is provided for feeding into a network or an island network.
  • a diversion of a subset of the steam for feeding into an external process connected to the steam turbine plant may be provided, which may be a heating process.
  • the fossil-heated steam generator 2 according to FIG. 1 is advantageously designed as a continuous steam generator. It comprises a first horizontal combustion chamber 4 and a second horizontal combustion chamber 5, on the basis of which in the FIG. 1 shown side view of the steam generator 2 only one can be seen.
  • the combustion chambers 4 and 5 of the steam generator 2 is a common horizontal gas train 6 downstream of the hot gas side, which opens into a vertical gas 8.
  • the front wall 9 and the side walls 10 of the first combustion chamber 4 and second combustion chamber 5 are each formed of gas-tight welded together, vertically arranged evaporator tubes 11, wherein in each case a number of evaporator tubes 11 can be acted upon in parallel with flow medium S.
  • the evaporator tubes 11 have - as in FIG. 2 shown on its inside ribs 40, which form a kind multi-threaded and have a rib height R.
  • the pitch angle ⁇ between a plane perpendicular to the tube axis 41 and the flanks 42 of the pipe inside arranged on the ribs 40 is less than 55 °. This results in a particularly high heat transfer from the inner wall of the evaporator tubes 11 to the flow medium S guided into the evaporator tubes 11 and, at the same time, particularly low temperatures of the tube wall.
  • Adjacent evaporator or steam generator tubes 11, 14, 15 are gas-tight welded together in a manner not shown by fins.
  • the respective fin width namely the heating of the evaporator or steam generator tubes 11, 14, 15 can be influenced. Therefore, the respective fin width is adapted depending on the position of the respective evaporator or steam generator tubes 11, 14, 15 in the steam generator 2 to a gas side prescribable heating profile.
  • the heating profile can be a typical heating profile determined from empirical values or else a rough estimate. As a result, temperature differences at the outlet of the evaporator or steam generator tubes 11, 14, 15 are kept particularly low even with very different heating of the evaporator or steam generator tubes 11, 14, 15.
  • the tube inner diameter D of the evaporator tubes 11 of the combustion chamber 4 or 5 is selected depending on the respective position of the evaporator tubes 11 in the combustion chamber 4 and 5 respectively. In this way, the steam generator 2 is adapted to the different degrees of heating of the evaporator tubes 11. This design of the evaporator tubes 11 of the combustion chamber 4 and 5 ensures particularly reliable that temperature differences at the outlet of the evaporator tubes 11 are kept particularly low.
  • a number of the evaporator tubes 11 of the side walls 10 of the combustion chamber 4 and 5 upstream of an inlet manifold system 16 is preceded by the flow medium side for flow medium S and in each case an outlet collector system 18 downstream.
  • the entry collector system 16 comprises a number of parallel admission collectors.
  • a line system 19 is provided for supplying flow medium S into the inlet header system 16 of the evaporator tubes 11 of the combustion chamber 4 or 5, a line system 19 is provided.
  • the line system 19 includes a plurality of parallel lines, each connected to one of the inlet header of the inlet header system 16.
  • throttling devices As a means for reducing the flow of the flow medium S, a part of the evaporator tubes 11 are equipped with throttling devices, which are not shown in detail in the drawing.
  • the throttling devices are embodied as pinhole diaphragms reducing the internal pipe diameter D and, during operation of the steam generator 2, effect a reduction of the throughput of the flow medium S in underheated Evaporator tubes 11, whereby the flow rate of the flow medium S of the heating is adjusted.
  • throttle devices as a means for reducing the flow rate of the flow medium S in a number of the evaporator tubes 11 of the combustion chamber 4 and 5 one or more not shown in the drawing lines of the line system 19 with throttle devices, in particular throttle valves equipped.
  • the evaporator tubes 11 of the end walls 9 of the combustion chamber 4 and 5 respectively the evaporator tubes 11 of the side walls 10 of the combustion chamber 4 or 5 upstream of the flow medium side.
  • the horizontal gas flue 6 has a number of superheater heating surfaces 22 designed as Schott heating surfaces, which are arranged in a hanging construction approximately perpendicular to the main flow direction 24 of the heating gas G and whose tubes are each connected in parallel for flow through the flow medium S.
  • the superheater heating surfaces 22 are heated predominantly convectively and are downstream of the evaporator tubes 11 of the combustion chamber 4 and 5, respectively, on the flow medium side.
  • the vertical gas train 8 has a number of convection heating surfaces 26 which can be heated predominantly convectively and which are formed from tubes arranged approximately perpendicular to the main flow direction 24 of the heating gas G. These tubes are each connected in parallel for a flow through the flow medium S.
  • 8 economizer 28 is arranged in the vertical gas train.
  • the vertical gas train 8 opens into a further heat exchanger, for example into an air preheater and from there via a dust filter into a chimney.
  • the vertical gas train 8 downstream components are in FIG. 1 not shown in detail.
  • the steam generator 2 is designed in a horizontal design with a particularly low height and thus can be built with very low manufacturing and assembly costs.
  • a number of burners 30 for fossil fuel B which are arranged on the end wall 9 of the combustion chamber 4 and 5 in the height of the horizontal gas flue 6, as the FIG. 3 can be seen.
  • the lengths L of the combustion chambers. 4 and 5 are selected such that they exceed the burnout length of the fuel B at full load operation of the steam generator 2.
  • the length L is the distance from the end wall 9 of the combustion chamber 4 and 5 to the inlet region 32 of the horizontal gas flue 6.
  • the burn-out length of the fuel B is defined as the fuel gas velocity in the horizontal direction at a certain average heating gas temperature multiplied by the burn-out time t A of The burn-out time t A of the fuel B, in turn, is the time required, for example, a coal dust grain medium size to burn out completely at a certain mean temperature of the heating gas.
  • BMCR stands for Boiler maximum continuous rating. BMCR is an internationally commonly used term for the highest continuous power a steam generator. This also corresponds to the design performance, ie the power at full load operation of the steam generator.
  • This horizontal length L of the combustion chambers 4 and 5 is greater than the height H of the combustion chamber 4 and 5.
  • the height H is thereby from the funnel upper edge of the combustion chamber 4 and 5, in FIG. 1 marked by the line with the end points X and Y, measured up to the combustion chamber ceiling.
  • the length L is determined only once and then applies to each of the N combustion chambers 4 and 5, respectively.
  • the length L of the two combustion chambers 4 and 5 is determined approximately via the two functions (1) and (2).
  • K 1 : t A 3s according to (1)
  • K 2 : t A 2.5s according to (1)
  • K 3 : t A 2s according to (1)
  • K 4 : T BRK 1200 ° C according to (2)
  • K 5 : T BRK 1300 ° C according to (2)
  • the flames F of the burner 30 are aligned horizontally during operation of the steam generator 2.
  • a flow of the heating gas G produced during combustion is generated in an approximately horizontal main flow direction 24. This passes through the common horizontal gas train 6 in the approximately directed towards the bottom vertical gas train 8 and leaves it in the direction of the fireplace, not shown.
  • Flow medium S entering the economizer 28 passes via the convection heating surfaces arranged in the vertical gas train 8 into the inlet header system 16 of the combustion chamber 4 or 5 of the steam generator 2.
  • gas-tight welded evaporator tubes 11 of the combustion chamber 4 and 5 of the steam generator 2 takes place the evaporation and optionally a partial overheating of the flow medium S instead.
  • the resulting vapor or a water-vapor mixture is collected in the outlet collector system 18 for flow medium S.
  • the steam or the water-vapor mixture enters the walls of the horizontal gas flue 6 and the vertical gas flue 8 and from there in turn into the superheater heating surfaces 22 of the horizontal flue 6.
  • the superheater heating 22 further overheating of the steam, which then use , For example, the drive of a steam turbine is supplied.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
  • Spray-Type Burners (AREA)
  • Hydrogen, Water And Hydrids (AREA)
EP00902545A 1999-01-18 2000-01-10 Fossilbeheizter dampferzeuger Expired - Lifetime EP1144910B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19901621A DE19901621A1 (de) 1999-01-18 1999-01-18 Fossilbeheizter Dampferzeuger
DE19901621 1999-01-18
PCT/DE2000/000055 WO2000042352A1 (de) 1999-01-18 2000-01-10 Fossilbeheizter dampferzeuger

Publications (2)

Publication Number Publication Date
EP1144910A1 EP1144910A1 (de) 2001-10-17
EP1144910B1 true EP1144910B1 (de) 2008-07-02

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EP00902545A Expired - Lifetime EP1144910B1 (de) 1999-01-18 2000-01-10 Fossilbeheizter dampferzeuger

Country Status (11)

Country Link
US (1) US6446584B1 (da)
EP (1) EP1144910B1 (da)
JP (1) JP4953506B2 (da)
KR (1) KR100776423B1 (da)
CN (2) CN1192187C (da)
CA (1) CA2359936C (da)
DE (2) DE19901621A1 (da)
DK (1) DK1144910T3 (da)
ES (1) ES2307493T3 (da)
RU (1) RU2221195C2 (da)
WO (1) WO2000042352A1 (da)

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KR20010112243A (ko) 2001-12-20
CN1287111C (zh) 2006-11-29
DK1144910T3 (da) 2008-11-03
CA2359936A1 (en) 2000-07-20
US6446584B1 (en) 2002-09-10
KR100776423B1 (ko) 2007-11-16
DE50015236D1 (de) 2008-08-14
JP2002535587A (ja) 2002-10-22
CN1192187C (zh) 2005-03-09
JP4953506B2 (ja) 2012-06-13
CN1550710A (zh) 2004-12-01
WO2000042352A1 (de) 2000-07-20
CA2359936C (en) 2007-11-20
EP1144910A1 (de) 2001-10-17
DE19901621A1 (de) 2000-07-27
US20020026905A1 (en) 2002-03-07
RU2221195C2 (ru) 2004-01-10
CN1336997A (zh) 2002-02-20
ES2307493T3 (es) 2008-12-01

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