EP3414490B1 - Fired heating system and method - Google Patents

Fired heating system and method Download PDF

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Publication number
EP3414490B1
EP3414490B1 EP16884234.2A EP16884234A EP3414490B1 EP 3414490 B1 EP3414490 B1 EP 3414490B1 EP 16884234 A EP16884234 A EP 16884234A EP 3414490 B1 EP3414490 B1 EP 3414490B1
Authority
EP
European Patent Office
Prior art keywords
fuel
burner
fuel discharge
discharge ring
burner wall
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP16884234.2A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP3414490A4 (en
EP3414490A1 (en
Inventor
Darton J. Zink
Rex K. Isaacs
Jonathon Barnes
Parker Imel
Seth MARTY
Cody Little
John Mcdonald
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.)
Zeeco Inc
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Zeeco Inc
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Filing date
Publication date
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Publication of EP3414490A1 publication Critical patent/EP3414490A1/en
Publication of EP3414490A4 publication Critical patent/EP3414490A4/en
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Publication of EP3414490B1 publication Critical patent/EP3414490B1/en
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Classifications

    • 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 
    • F23C9/00—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber
    • F23C9/006—Combustion apparatus characterised by arrangements for returning combustion products or flue gases to the combustion chamber the recirculation taking place in the combustion chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/02—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/34—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air
    • F23D14/36—Burners specially adapted for use with means for pressurising the gaseous fuel or the combustion air in which the compressor and burner form a single unit
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/48—Nozzles
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/48—Nozzles
    • F23D14/58—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration
    • F23D14/583—Nozzles characterised by the shape or arrangement of the outlet or outlets from the nozzle, e.g. of annular configuration of elongated shape, e.g. slits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/46—Details, e.g. noise reduction means
    • F23D14/70—Baffles or like flow-disturbing devices

Definitions

  • the present invention relates to burner assemblies and to methods and apparatuses for reducing NO x emissions from burners of the type used in process heaters, boilers, furnaces and other fired heating systems.
  • thermal NO x is the primary mechanism of NO x production. Thermal NO x is produced when the flame reaches a high enough temperature to break the covalent N 2 bond so that the resulting "free" nitrogen atoms then bond with oxygen to form NO x .
  • the temperature of combustion is not great enough to break all of the N 2 bonds. Rather, most of the nitrogen in the air stream passes through the combustion process and remains as diatomic nitrogen (N 2 ) in the combustion products. However, some of the N 2 will typically reach a high enough temperature in the high intensity regions of the flame to break the N 2 bond and form "free" nitrogen. Once the covalent nitrogen bond is broken, the "free" nitrogen is available to bond with other atoms. Fortunately, the free nitrogen will most likely react with other free nitrogen atoms to form N 2 . However, if another free nitrogen atom is not available, the free nitrogen will react with oxygen to form NO x .
  • thermal NO x reduction is generally achieved by slowing the rate of combustion. Since the combustion process is a reaction between oxygen and the burner fuel, the objective of delayed combustion is typically to reduce the rate at which the fuel and oxygen mix together and burn. The faster the oxygen and the fuel mix together, the faster the rate of combustion and the higher the peak flame temperature.
  • US 6 499 990 B1 discloses a low NOx burner apparatus and method.
  • US 4 411 617 discloses burners for soaking pit furnaces.
  • US 2010/291492 A1 discloses an air flare apparatus and method.
  • the present invention provides a fired heating system and a method of operating a burner which achieve further reductions in NO x emissions at lower cost, reduced complexity, and higher efficiency.
  • the inventive system and method provide both staged fuel operation and internal flue gas recirculation (IFGR) for lowering combustion temperatures and reducing NO x emissions.
  • IFGR internal flue gas recirculation
  • the inventive burner and method allow the entire fuel stream to be conditioned with flue gas.
  • the inventive system and method preferably employ a single ejector ring with tip, or an elongate bar-type fuel ejector, which increases the level of IFGR provided by the burner by (a) increasing the available ejection tip area of the burner, (b) increasing the number of ejection ports which can be used, (c) allowing the ejection ports and the resulting ejection streams to be positioned much closer together, and/or (d) allowing the use of a continuous or elongated ejection slot.
  • the inventive system and method also provide high levels of performance in regard to flame length, available turndown ratio, and stability.
  • the burner 10 preferably comprises: a housing 12 having an outlet end 14; a burner wall 16 which is positioned at the outlet end 14 of the housing 12 and has a longitudinal axis 18 which extends therethrough; an air flow passageway 22 which extends through and is surrounded by the burner wall 16 and has a longitudinally forward discharge opening 24 at the forward end 20 of the burner wall 16; a fuel discharge ring assembly 26 for ejecting a gaseous or liquid burner fuel outside of the burner wall 16 toward the forward discharge end 20 thereof; and at least one pilot burner assembly 25 which extends through the discharge section 28 of the housing 12 and into the air flow passageway 22 of the burner wall 16.
  • the housing 12 has a windbox or other inlet 32 upstream of the discharge section 28 for receiving combustion air or other oxygen containing gas.
  • Combustion air (or an alternative oxygen-containing gas) is received through the inlet 32 and flows through the housing 12 to the inlet end 35 of the burner wall 16.
  • the air (or other oxygen-containing gas) then flows through the flow passageway 22 of the burner wall 16 and exits the forward discharge opening 24 of the passageway 22.
  • the quantity of combustion air entering housing 12 can be regulated using an inlet damper (not shown) or any other regulating device known in the art.
  • Combustion air can be provided to housing 12 by forced circulation, natural draft, a combination thereof, or in any other manner employed in the art.
  • the burner wall 16 is preferably constructed of a high temperature refractory burner tile material.
  • the burner wall 16 could alternatively be formed of or provided by the furnace floor, a metal band, a refractory band, or any other material or structure which is capable of (a) providing an acceptable combustion air flow orifice (i.e., passageway) into the fired heating system and (b) withstanding high temperature operating conditions.
  • the burner 10 can be installed, for example, through a floor or wall 38 of a boiler, fired heater, furnace or other fired heating system 40. Consequently, the forward (discharge) end 20 of burner wall 16 is in communication with the interior 42 of the fired heating system 40 in which combustion takes place. As a result of the combustion process, the interior 42 of the fired heating system 40 will contain inert combustion product gases (i.e., flue gas) 44. An insulating material 46 will also typically be secured to the interior surface of the floor or wall 38 outside of the burner wall 16.
  • the burner wall 16 and the air flow passageway 22 extending therethrough will preferably have round (circular) cross-sectional shapes.
  • the cross-sectional shapes of the burner wall 16 and the air flow passageway 22 can alternatively be square, rectangular, oval, or generally any other shape desired.
  • the fuel discharge tip assembly 26 used in the burner 10 preferably comprises a fuel discharge ring 30 which is positioned rearwardly of the forward discharge end 20 of the burner wall 16 and outside of the air flow passageway 22.
  • a “ring” may typically be thought of as having a circular shape, the "fuel discharge ring” referred to herein and in the claims, unless otherwise expressly specified or limited, can be circular, square, rectangular, oval, or any other desired shape.
  • the shape of the fuel discharge tip 30 correspond to the lateral cross-sectional shape of the burner wall 16, or at least the forward end 20 thereof.
  • the fuel discharge ring 30 will preferably have an inside diameter, or other inside dimensions in the case of a square, rectangular, oval, or other non-circular burner, which is/are greater than or equal to the outside diameter or other outer dimensions of the discharge end 20 of the burner wall 16.
  • the fuel discharge ring assembly 26 preferably also comprises: a fuel supply manifold 48; a fuel supply line (not shown) which supplies a gas or liquid burner fuel to the fuel manifold 48; and one or more (preferably a plurality of) fuel riser lines 50 which extend from the fuel supply manifold 48 to the fuel discharge ring 30.
  • the fuel manifold 48 of the fuel discharge ring assembly 26 is preferably positioned outside of the floor or wall 38 of the fired heating system 40.
  • the fuel riser lines 50 of the ring assembly 26 can extend from the fuel supply manifold 48, which is positioned outside of the heating system 40, to the fuel discharge ring 30 in the interior 42 of the heating system 40 either (a) through a radially extending refractory base which can be formed on and as part of the burner wall 16, (b) through the layer of insulating material 46 which is secured to the interior surface of the floor or wall 38 of the heating system 40 outside of the burner wall 16, or (c) through a gap 52 between the base of the burner wall 16 and the surrounding layer of insulating material 46.
  • the fuel discharge ring assembly 26 will preferably comprise at least 2, more preferably comprise at least 3, and most preferably at least 4, riser line connections 54 which are evenly spaced around the fuel discharge ring 30.
  • the fuel discharge ring assembly 26 will preferably further comprise an outer protection sleeve 56 which surrounds the riser lines 50.
  • the outer protection sleeve 56 preferably extends longitudinally from the furnace wall attachment flange 58 of the burner 10 to, or proximately to, the fuel discharge ring 30.
  • the fuel discharge ring 30 entirely surrounds or substantially surrounds (i.e., extends from at least 95% to 100% of the entire distance around) the air flow passageway 22 of the burner wall 16.
  • the fuel discharge ring 30 has either one fuel discharge slot 60 (see alternative discharge ring 36 shown in FIG. 5 ) or a plurality of fuel discharge slots, ports or other openings 62 which is/are formed through the forward surface 64 of the fuel discharge ring 36 or 30 such that the slot or the plurality of other openings 60 or 62 substantially surround(s) or entirely surround(s) the air flow passageway 22.
  • the plurality of fuel discharge openings 62 if used, will preferably be a plurality of round holes which are spaced from about 0.5 to about 200 diameters apart.
  • the size and orientation of the fuel discharge slot 60 or the plurality of other openings 62 and the fuel pressure supplied to the fuel discharge ring 30 or 36 are such that the gas or liquid burner fuel is discharged from the slot 60 or other openings 62 in free jet flow outside of the burner wall in a direct or angled forward direction such that the ejected fuel flows along any desired straight or curving forward path to a combustion zone 66 which begins at or proximate to (i.e., within from 0 to + 0.5 inches of) the forward end 20 of the burner wall 16.
  • the fuel discharge slot 60 or plurality of other openings 62 is/are preferably oriented such that the fuel is ejected toward the outer edge 68 of the forward end 20 of the burner wall 16.
  • IFGR Internal Flue Gas Recirculation
  • This conditioning of the fuel with inert flue gas slows the burning of the fuel in the combustion zone 66, thus reducing NOx production by lowering the peak temperature of the burner flame.
  • IFGR mixing is further enhanced significantly by the momentum of the combustion air (or other oxygen-containing gas) exiting the forward discharge opening 24 of the burner wall 16 which pulls additional flue gas into the fuel and into the combustion zone 66.
  • the burner 10 preferably includes one or more exterior impact structures positioned at least partially in the flow path of the fuel ejected from the fuel discharge ring 30 or 36.
  • Each impact structure can generally be any type of obstruction which will decrease the flow momentum and/or increase the turbulence of the fuel stream sufficiently to promote flue gas entrainment and mixing while allowing the resulting mixture to flow on to the combustion zone 66.
  • the burner wall 16 employed in the burner 10 is preferably formed to provide a tiered exterior shape wherein the outer diameter of the base 70 of the burner wall 16 is broader than the outer diameter of the forward end 20 thereof and the exterior of the burner wall 16 includes one or a series of surrounding, spaced apart, impact ledges.
  • the outermost impact ledge of the burner wall 16 is defined by the outer edge 68 of the forward end 20 of the burner wall 16.
  • At least one additional impact ledge 72 is then positioned around the exterior of the burner wall 16 between the fuel discharge ring 30 and the forward end 20 of the burner wall 16.
  • the forward end 20 of the burner wall 16, which surrounds the forward air discharge opening 24, also forms a flame stabilization ledge for the combustion zone 66 of the burner 10.
  • IFGR and flame stability are additionally increased in the burner 10 by the formation of a plurality of ports, slots, or other openings 62, or of a single slot 60, in the fuel discharge ring 30 or 36, as discussed above, which substantially surround(s) or entirely surround(s) the air flow passageway 22.
  • the ports or slots 62 will preferably be spaced close together (i.e., preferably only from about 0.5 to about 200 port diameters or slot widths apart).
  • the inventive fuel discharge ring 30 or 36 significantly increases the total effective available tip area, thus allowing either (a) the use of a significantly greater number of ports 62 which are positioned closer together or (b) the use of a single surrounding fuel ejection slot 60 or a plurality of slots that are spaced only a short distance apart. These port or slot arrangements and reduced spacing provide an even greater degree of flue gas entrainment and flame stability.
  • a swirler 74 of the type commonly used in burners can optionally be positioned in the air flow passageway 22.
  • the burner 10 In addition to providing reduced peak flame temperatures and lower NO x levels using IFGR as discussed above, the burner 10 also achieves further flame temperature and NO x level reductions by providing staged fuel operation in the combustion zone 66. By ejecting the fuel outside of the burner wall 16 into the exterior base portion 76 of the air flow discharged from the outer end 20 of the burner wall 16, the burner 10 causes the combustion zone 66 to have (a) an outer surrounding fuel rich combustion region 78 and (b) an interior fuel lean combustion region 80.
  • combustion occurs in an excess fuel to air ratio.
  • combustion occurs in an excess air to fuel ratio.
  • air or other oxygen-containing gas is delivered through the flow passageway 22 surrounded by the burner wall 16.
  • a flow of the burner fuel is discharged forwardly, in free jet form, from the fuel discharge ring 30 or 36 such that the flow of burner fuel is received in the combustion zone 66.
  • the free jet flow of burner fuel from the fuel discharge ring 30 or 36 is ejected directly toward the outer edge 68 of the forward end 20 of the burner wall 16.
  • the flow preferably has a lateral cross-sectional shape which (a) substantially surrounds the flow passageway 22 and (b) corresponds to the outer lateral cross-sectional shape of the forward end 20 of the burner wall 16.
  • FIGS. 6 and 7 An alternative embodiment 100 of the inventive burner is illustrated in FIGS. 6 and 7 .
  • the structure and operation of the burner 100 are substantially the same as the burner 10 except that the burner 100 is a flat flame burner wherein (a) the burner wall 116 and the air flow passageway 126 extending therethrough have a wide, flatter, rectangular shape, (b) the fuel discharge ring 30 of burner 10 is replaced with a T-bar ejector 130 having an elongate ejection tube or other conduit 132 which extends laterally adjacent to and across the exterior of the flat side 125 of the burner wall 116, (c) the burner 100 preferably does not include a burner fuel manifold, and (d) the T-bar ejector preferably has only a single fuel riser 134 which extends to the middle of the lateral ejection conduit 132.
  • the T-bar ejector 130 preferably has either a single elongate slot or a plurality of ports, slots or other openings 135 which extend(s) along at least most of the length of the forward surface 136 of the lateral ejection conduit 132, preferably from or proximately from one end 138 to or proximately to the other end 140 of the lateral conduit 132. Where a plurality of slot openings or circular port openings 135 are used, the openings are preferably only spaced from about 0.5 to 200 diameters or slot widths apart.
  • the single slot, or at least most, preferably all, of the plurality of slots or other openings, 135 provided in the lateral ejection conduit 132 is/are preferably oriented to eject the burner fuel toward the laterally extending outer edge 142 of the forward end 144 of the burner wall 116 on the flat side 125 of the burner.
  • At least one additional impact ledge 146 is preferably also provided or formed in the exterior of the burner wall 116 between the forward outer edge 142 and the fuel ejection conduit 132.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
EP16884234.2A 2016-01-08 2016-12-30 Fired heating system and method Active EP3414490B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
US14/991,258 US20170198902A1 (en) 2016-01-08 2016-01-08 LOW NOx BURNER APPARATUS AND METHOD
PCT/US2016/069466 WO2017120114A1 (en) 2016-01-08 2016-12-30 LOW NOx BURNER APPARATUS AND METHOD

Publications (3)

Publication Number Publication Date
EP3414490A1 EP3414490A1 (en) 2018-12-19
EP3414490A4 EP3414490A4 (en) 2019-11-20
EP3414490B1 true EP3414490B1 (en) 2021-09-15

Family

ID=59274482

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16884234.2A Active EP3414490B1 (en) 2016-01-08 2016-12-30 Fired heating system and method

Country Status (5)

Country Link
US (1) US20170198902A1 (zh)
EP (1) EP3414490B1 (zh)
CN (1) CN108603659B (zh)
CA (1) CA3009668C (zh)
WO (1) WO2017120114A1 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
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US10982846B2 (en) 2017-06-14 2021-04-20 Webster Combustion Technology Llc Vortex recirculating combustion burner head
US11198073B2 (en) * 2017-11-13 2021-12-14 Technifex Products, Llc Apparatus for producing a fire special effect
USD932001S1 (en) * 2019-07-22 2021-09-28 Oilon Technology Oy Burner
US11353212B2 (en) 2019-09-12 2022-06-07 Zeeco, Inc. Low NOxburner apparatus and method

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US3174527A (en) * 1962-06-13 1965-03-23 Zink Co John Combination oil and/or gaseous fuel burner
US4411617A (en) * 1977-11-10 1983-10-25 Maksim Jr John Burners for soaking pit furnaces
US4496306A (en) * 1978-06-09 1985-01-29 Hitachi Shipbuilding & Engineering Co., Ltd. Multi-stage combustion method for inhibiting formation of nitrogen oxides
US4470262A (en) * 1980-03-07 1984-09-11 Solar Turbines, Incorporated Combustors
US5098282A (en) * 1990-09-07 1992-03-24 John Zink Company Methods and apparatus for burning fuel with low NOx formation
US5073105A (en) * 1991-05-01 1991-12-17 Callidus Technologies Inc. Low NOx burner assemblies
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US5195884A (en) * 1992-03-27 1993-03-23 John Zink Company, A Division Of Koch Engineering Company, Inc. Low NOx formation burner apparatus and methods
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US6499990B1 (en) * 2001-03-07 2002-12-31 Zeeco, Inc. Low NOx burner apparatus and method
US6672858B1 (en) * 2001-07-18 2004-01-06 Charles E. Benson Method and apparatus for heating a furnace
AU2003238524A1 (en) * 2002-05-16 2003-12-02 Alstom Technology Ltd Premix burner
US6695609B1 (en) * 2002-12-06 2004-02-24 John Zink Company, Llc Compact low NOx gas burner apparatus and methods
US7670135B1 (en) * 2005-07-13 2010-03-02 Zeeco, Inc. Burner and method for induction of flue gas
US8696348B2 (en) * 2006-04-26 2014-04-15 Air Products And Chemicals, Inc. Ultra-low NOx burner assembly
US7878798B2 (en) * 2006-06-14 2011-02-01 John Zink Company, Llc Coanda gas burner apparatus and methods
CN201302162Y (zh) * 2008-11-03 2009-09-02 广东万家乐燃气具有限公司 一种全预混燃气燃烧器装置
US20100291492A1 (en) * 2009-05-12 2010-11-18 John Zink Company, Llc Air flare apparatus and method
BR112014011437B1 (pt) * 2011-11-10 2021-02-17 Zeeco, Inc. aparelho queimador para um sistema de forno, e, método para operar um queimador

Also Published As

Publication number Publication date
CA3009668A1 (en) 2017-07-13
EP3414490A4 (en) 2019-11-20
CN108603659B (zh) 2021-05-04
CA3009668C (en) 2024-01-30
CN108603659A (zh) 2018-09-28
US20170198902A1 (en) 2017-07-13
WO2017120114A1 (en) 2017-07-13
EP3414490A1 (en) 2018-12-19

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