EP0266857A2 - Drehströmungsfeuerung und damit ausgerüsteter Heizkessel - Google Patents

Drehströmungsfeuerung und damit ausgerüsteter Heizkessel Download PDF

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Publication number
EP0266857A2
EP0266857A2 EP87304216A EP87304216A EP0266857A2 EP 0266857 A2 EP0266857 A2 EP 0266857A2 EP 87304216 A EP87304216 A EP 87304216A EP 87304216 A EP87304216 A EP 87304216A EP 0266857 A2 EP0266857 A2 EP 0266857A2
Authority
EP
European Patent Office
Prior art keywords
chamber
combustor
boiler
wall
rear end
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.)
Ceased
Application number
EP87304216A
Other languages
English (en)
French (fr)
Other versions
EP0266857A3 (de
Inventor
Jacob Korenberg
Mark Khinkis
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.)
Donlee Technologies Inc
Original Assignee
Donlee Technologies Inc
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 Donlee Technologies Inc filed Critical Donlee Technologies Inc
Publication of EP0266857A2 publication Critical patent/EP0266857A2/de
Publication of EP0266857A3 publication Critical patent/EP0266857A3/de
Ceased 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
    • F22B7/00—Steam boilers of furnace-tube type, i.e. the combustion of fuel being performed inside one or more furnace tubes built-in in the boiler body
    • F22B7/12—Steam boilers of furnace-tube type, i.e. the combustion of fuel being performed inside one or more furnace tubes built-in in the boiler body with auxiliary fire tubes; Arrangement of header boxes providing for return diversion of flue gas flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M9/00—Baffles or deflectors for air or combustion products; Flame shields
    • F23M9/06—Baffles or deflectors for air or combustion products; Flame shields in fire-boxes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C3/00—Combustion apparatus characterised by the shape of the combustion chamber
    • F23C3/006—Combustion apparatus characterised by the shape of the combustion chamber the chamber being arranged for cyclonic combustion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23M—CASINGS, LININGS, WALLS OR DOORS SPECIALLY ADAPTED FOR COMBUSTION CHAMBERS, e.g. FIREBRIDGES; DEVICES FOR DEFLECTING AIR, FLAMES OR COMBUSTION PRODUCTS IN COMBUSTION CHAMBERS; SAFETY ARRANGEMENTS SPECIALLY ADAPTED FOR COMBUSTION APPARATUS; DETAILS OF COMBUSTION CHAMBERS, NOT OTHERWISE PROVIDED FOR
    • F23M5/00—Casings; Linings; Walls
    • F23M5/08—Cooling thereof; Tube walls
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H1/00—Water heaters, e.g. boilers, continuous-flow heaters or water-storage heaters
    • F24H1/22—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating
    • F24H1/24—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers
    • F24H1/26—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body
    • F24H1/28—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes
    • F24H1/285—Water heaters other than continuous-flow or water-storage heaters, e.g. water heaters for central heating with water mantle surrounding the combustion chamber or chambers the water mantle forming an integral body including one or more furnace or fire tubes with the fire tubes arranged alongside the combustion chamber

Definitions

  • the present invention relates to cyclonic combustors and especially to boilers incorporating such combustors.
  • cyclonic combustors have been used to produce a cyclone of turbulent gases within a combustion chamber for combusting various solid materials, including poor quality coal and vegetable refuse.
  • Such combustors are disclosed in "Combustion in Swirling Flows: A Review", N. Syred and J. M. Beer, Combustion and Flame, Volume 23, pages 143-201 (1974).
  • a fluidised bed boiler having a cyclonic combustor is disclosed in U.S. Patent No. 4,457,289 to Korenberg. These documents are incorporated by reference in this application.
  • a fire tube boiler having a cyclonic combustor has been commercially marketed by Cyclotherm Division, Oswego Package Boiler Co., Inc.
  • adiabatic cyclone combustors Although providing high specific heat release, known adiabatic cyclone combustors have the disadvantages that combustion temperature is high and NO x emissions are high. Combustion is unstable at low capacity burning and high hydrodynamic turndown ratios are not possible in non-adiabatic combustors.
  • the hydrodynamic turndown ratio of a boiler is defined as the ratio of pressurised air flow at maximum load to pressurised air flow at minimum load and measures the ability of the boiler to operate over the extremes of its load ranges.
  • a high turndown ratio would allow a wide range in the level of steam generation at a particular time.
  • a wide range of steam generation is important to allow the boiler to respond most efficiently to varying steam demands.
  • a cyclonic combustor is characterised by a first chamber having a front end, a rear end and a substationally cylindrical longitudinally extending outer wall which is substantially uncooled and refractory lined; a second chamber having a front end, a rear end and a substantially cylindrical longitudinally extending outer wall, the rear end of the first chamber being in fluid communication with and substantially longitudinally aligned with the front end of the second chamber; means for supplying air and fuel directly into the first chamber and for forming a cyclonic flow pattern of hot gases for combustion within the first chamber and the second chamber; a substantially cylindrical exit throat at the rear end of the second chamber and aligned substantially concentrically therewith, for exhausting hot gases from the second chamber, the exit throat having a diameter less than the inner diameter of the second chamber; and, heat exchange means surrounding the second chamber for substantially cooling the wall of the second chamber without substantially cooling the wall of the first chamber.
  • Fig. 1 shows a horizontally disposed fire tube boiler having a cyclonic combustor in accordance with one preferred embodiment of the invention.
  • the combustor includes a central fire tube, also known as a Morison tube, with a combustion chamber 21 including areas defined by first chamber 22 and second chamber 24.
  • First chamber 22 includes a front end 26, a rear end 28 and a substantially cylindrical longitudinally extending outer wall 30 which is substantially uncooled and refractory lined.
  • Second chamber 24 has a front end 32, a rear end 34 and a substantially cylindrical longitudinally extending outer wall 36, which is preferably constructed of metal.
  • the rear end 20 of the first chamber 22 and the front end 32 of second chamber 24 are in fluid communication and longitudinally aligned with each other.
  • Means for supplying air and fuel directly into first chamber 22 such as plenum or manifold 38 and tangential nozzles 40 form a cyclonic flow pattern of hot gases within the reaction chamber defined by first chamber 22 and second chamber 24.
  • the fuel which is preferably liquid or gaseous, is introduced tangentially by nozzles 43 and may additionally or alternatively be introduced into first chamber 22 radially by nozzle 41.
  • a substantially cy­lindrical exit throat 42 is positioned at rear end 34 of second chamber 24 and aligned concentrically with second chamber 24 so that the exit throat has a diameter less than the inner diameter of second chamber 24.
  • a source of pressur­ized air such as a blower (not shown) feeds air from plenum or manifold 38 through nozzles 40 into the first chamber 22.
  • the cross sectional area of the tangential air nozzles 40 and the geometric characteristics of first chamber 22 and second chamber 24 be adapted to provide a Swirl number (S) of at least about 0.6 and Reynolds number (Re) of at least about 18,000 which are re­quired to create a cyclone of turbulence in first chamber 22 and second chamber 24 when operating at maximum capacity.
  • S Swirl number
  • Re Reynolds number
  • the Swirl number and Reynolds number at maximum capacity must not exceed those values which would result in an unacceptable pressure drop through the tangential air nozzles 40 and the combustion chamber constituted by first chamber 22 and second chamber 24.
  • Exit throat 42 and the interior of second chamber 24 must exhibit certain geometric characteristics together with the cross sectional area of the tangential air nozzles of first chamber 22 in order to provide the requisite Swirl and Reynolds number.
  • combustion chamber 21 comprising first chamber 22 and second chamber 24 is designed and operated so as to achieve a Swirl number of at least about 0.6 and a Reynolds number of at least about 1800 in such chamber and the ratio of the diameter of the exit throat 42 (De) to the diameter of the inner wall of the second chamber 24 (Do), i.e., De/Do defined herein as X, lies within the range of about 0.4 to about 0.7, the first chamber 22 and second chamber 24 will, during operation, exhibit large in­ternal reverse flow zones with as many as three concentric toroidal recirculation zones being formed. Such recirculation zones are known generally in the field of conventional cyclone combustors. This coupled with the high level of turbulence re­sults in significantly improved heat exchange and, therefore, a relatively uniform temperature throughout combustion chambers 22 and 24.
  • ratio X preferably lies within the range of about 0.4 to about 0.7 because as X increases, the pressure drop decreases through the combustion chamber and the Swirl number in­creases. Higher values of X are preferred. However, for values of X in excess of 0.7, the internal reverse flow zones are not formed sufficiently.
  • Heat exchange means surround second chamber 24 for substan­tially cooling the wall 36 of second chamber 24 without substan­tially cooling the wall 30 of first chamber 22.
  • the heat ex­change means preferably includes an outer boiler shell 48, gas tubes 50 between outer shell 48 and Morison tube 54 for conducting hot gases from second chamber 24, and space 52 within shell 48 outside gas tubes 50 and second chamber 24 for con­ducting water which is heated by the heated gases in the second chamber 24 and the gas tubes 50, all in a conventionally known manner.
  • Stable combustion even at low boiler capacity, is achieved by not cooling the walls of first chamber 22 where the air and fuel are injected, but cooling only the walls of the second cham­ber 24.
  • This stable combustion enables high turndown ratios to be accomplished.
  • the turndown ratio can be increased from 4:1 up to and higher than 10.
  • Excess air can be decreased from 25-30% to 5% and kept constant at 5% over the high turndown ratio of 10:1.
  • the flame temperature can be decreased to 2000°F and lower, as op­posed to about 3000°F for conventional fire tube boilers. There­fore NO x emission is lower than in the standard burner/boiler unit due to the lower flame temperature and lower excess air.
  • the central fire tube preferably includes a cylindrical tube 54 extending from, aligned and continuous with wall 36 of second chamber 24. Hot gases from the second chamber 24 pass through exit throat 42 into cylindrical tube 54.
  • the heat exchange means also preferably includes means such as rear compartment 56 for directing the flow of hot gases exiting cylindrical tub 54 from second chamber 24 through a first predetermined set of the gas tubes 50 such as those in the lower part of Fig. 1 and front compartment 5 for directing the hot gases from the first set of gas pipes 50 to a second set of gas pipes 50 in the upper portion of Fig. 1 in the opposite direction.
  • This is shown by the arrows indicating gas flow and is conventionally known for fire tube boilers.
  • the means for supplying air and fuel preferably includes separate conduits for supplying air and fuel separately and directly into first chamber 22 and for mixing and combusting them in the first and second chambers 22 and 24.
  • the ratio between the length of the first and second chamber 22 and 24 affects the combustion temperature within the combus­tion chamber 21.
  • This ratio is important because low­ering the combustion temperature lowers the NO x formation.
  • This ratio for natural gas and fuel oil is normally less than 1.5 for a low capacity combustor and can become less than 0.5 for a very high capacity combustor.
  • the first to sec­ond chamber length ratio is substantially in the range of about 0.2:1 to 1.5:1. Because of this, the combustion temperature can be less than 2000-2200°F even for high capacity combustion.
  • the front end portion 32 of wall 36 is lined with a refractory material 60.
  • a cyclonic combustor comprises a first chamber having a front end, a rear end and a substantially cylindrical longitudi­nally extending outer wall which is substantially uncooled and refractory lined; a second chamber having a front end, a rear end and a substantially cylindrical longitudinally extending outer wall, the rear end of the first chamber in fluid communication with and longitudinally aligned with the front end of the second chamber; means for supplying air and fuel directly into the first chamber and for forming a cyclonic flow pattern within the first chamber and the second chamber; a substantially cylindrical exit throat at the rear end of the second chamber and aligned substan­tially concentrically therewith, the exit throat having a diame­ter less than the inner diameter of the second chamber; and means for substantially cooling the wall of the second chamber without substantially cooling the wall of the first chamber.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Pharmaceuticals Containing Other Organic And Inorganic Compounds (AREA)
  • Fluidized-Bed Combustion And Resonant Combustion (AREA)
EP87304216A 1986-11-07 1987-05-12 Drehströmungsfeuerung und damit ausgerüsteter Heizkessel Ceased EP0266857A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US92809686A 1986-11-07 1986-11-07
US928096 1986-11-07

Publications (2)

Publication Number Publication Date
EP0266857A2 true EP0266857A2 (de) 1988-05-11
EP0266857A3 EP0266857A3 (de) 1988-11-17

Family

ID=25455725

Family Applications (1)

Application Number Title Priority Date Filing Date
EP87304216A Ceased EP0266857A3 (de) 1986-11-07 1987-05-12 Drehströmungsfeuerung und damit ausgerüsteter Heizkessel

Country Status (9)

Country Link
EP (1) EP0266857A3 (de)
JP (1) JPS63131903A (de)
KR (1) KR880006498A (de)
AU (1) AU593104B2 (de)
DK (1) DK235287A (de)
FI (1) FI872037L (de)
MY (1) MY100885A (de)
NO (1) NO871975L (de)
NZ (1) NZ220266A (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0525734A3 (en) * 1991-08-01 1993-07-14 Institute Of Gas Technology Cyclonic combustion
US5473881A (en) * 1993-05-24 1995-12-12 Westinghouse Electric Corporation Low emission, fixed geometry gas turbine combustor
EP0866269A1 (de) * 1997-03-18 1998-09-23 Abb Research Ltd. Kesselanlage für eine Wärmeerzeugung

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1180954A (en) * 1980-12-09 1985-01-15 Kiyomi Okada Combustion apparatus for granular solid fuel
US4457289A (en) * 1982-04-20 1984-07-03 York-Shipley, Inc. Fast fluidized bed reactor and method of operating the reactor
EP0130225B1 (de) * 1983-07-01 1987-05-06 Ruhrkohle-Carborat GmbH Dreizugkessel für Drehströmungsfeuerung
EP0143510A1 (de) * 1983-08-08 1985-06-05 Inc. Aqua-Chem Brenner für Biomasse-Suspensionen

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0525734A3 (en) * 1991-08-01 1993-07-14 Institute Of Gas Technology Cyclonic combustion
US5473881A (en) * 1993-05-24 1995-12-12 Westinghouse Electric Corporation Low emission, fixed geometry gas turbine combustor
EP0866269A1 (de) * 1997-03-18 1998-09-23 Abb Research Ltd. Kesselanlage für eine Wärmeerzeugung
US5961315A (en) * 1997-03-18 1999-10-05 Abb Research Ltd. Boiler plant for heat generation

Also Published As

Publication number Publication date
NO871975D0 (no) 1987-05-13
FI872037A0 (fi) 1987-05-08
MY100885A (en) 1991-05-16
EP0266857A3 (de) 1988-11-17
AU7269187A (en) 1988-05-12
FI872037A7 (fi) 1988-05-08
FI872037L (fi) 1988-05-08
DK235287A (da) 1988-05-08
NO871975L (no) 1988-05-09
AU593104B2 (en) 1990-02-01
JPS63131903A (ja) 1988-06-03
KR880006498A (ko) 1988-07-23
NZ220266A (en) 1988-11-29
DK235287D0 (da) 1987-05-08

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