EP1705424A9 - Brennerkopf für Flüssigbrennstoffbrenner - Google Patents

Brennerkopf für Flüssigbrennstoffbrenner Download PDF

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Publication number
EP1705424A9
EP1705424A9 EP20050425122 EP05425122A EP1705424A9 EP 1705424 A9 EP1705424 A9 EP 1705424A9 EP 20050425122 EP20050425122 EP 20050425122 EP 05425122 A EP05425122 A EP 05425122A EP 1705424 A9 EP1705424 A9 EP 1705424A9
Authority
EP
European Patent Office
Prior art keywords
combustion
cap
combustion head
stream
head
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.)
Granted
Application number
EP20050425122
Other languages
English (en)
French (fr)
Other versions
EP1705424A1 (de
EP1705424B1 (de
Inventor
Paolo Bolognin
Michele Grandi
Francesco Guarniero
Flavio Pastorato
Giovanni Scaion
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.)
Riello SpA
Original Assignee
Riello SpA
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 Riello SpA filed Critical Riello SpA
Priority to EP05425122.8A priority Critical patent/EP1705424B1/de
Priority to CNA200610057997XA priority patent/CN1840963A/zh
Publication of EP1705424A1 publication Critical patent/EP1705424A1/de
Publication of EP1705424A9 publication Critical patent/EP1705424A9/de
Application granted granted Critical
Publication of EP1705424B1 publication Critical patent/EP1705424B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/36—Details, e.g. burner cooling means, noise reduction means
    • F23D11/40—Mixing tubes or chambers; Burner heads
    • F23D11/408—Flow influencing devices in the air tube
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D11/00—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space
    • F23D11/24—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space by pressurisation of the fuel before a nozzle through which it is sprayed by a substantial pressure reduction into a space

Definitions

  • the present invention relates to a burner combustion head, particularly suitable for burning low NO x emission liquid fuel.
  • the combustion reaction between the fuel and combustion supporter is produced by a combustion head substantially comprising a tubular conduit, which conducts the combustion supporting fluid from a blower into the combustion chamber, and the combustion supporting fluid mixes with a liquid fuel atomized by one or more nozzles.
  • a known ignition device ignites the mixture to initiate combustion.
  • burners have been devised featuring combustion heads, in which the temperature of the flame is reduced by recirculating part of the combustion fumes inside the combustion head and the flame itself.
  • the fumes are recirculated inside the flame using the high outflow speed of the air from the burner head, which produces a so-called "entrainment” effect, by which the fumes in the combustion chamber are drawn into the flame and, since they play no part in the combustion reaction, absorb heat, thus cooling the flame and reducing nitric oxide NO X emissions.
  • one object of the invention is to provide a combustion head which, as compared with known combustion heads, provides for improved mixing of the combustion supporting air and the fumes present in the combustion chamber, to reduce the presence of nitric oxides NO X .
  • Another object of the present invention is to provide a combustion head which recirculates the fumes present in the combustion chamber to premix them with the combustion supporting air upstream from the combustion region, so as to reduce the temperature of the flame.
  • Another object of the present invention is to provide a combustion head which mixes the recirculated fumes and the combustion supporting air more effectively as compared with known combustion heads.
  • the combustion head according to the present invention is also easier to produce, as compared with known combustion heads.
  • a liquid fuel e.g. gas oil
  • a central pipe 1 having a longitudinal axis of symmetry X.
  • Nozzle 2 atomizes the liquid fuel in known manner inside a combustion chamber CC (see below).
  • Pipe 1 is fitted coaxially with a cylindrical body 3, the outer cylindrical surface of which has equally spaced grooves 4 sloping with respect to longitudinal axis of symmetry X (see also Figures 4A, 4B, 4C).
  • a number of equally spaced calibrated holes 5 are formed, parallel to axis X, in the inner portion of cylindrical body 3 (see also Figure 4A), and cylindrical body 3 also comprises a central through hole FC for insertion of central pipe 1.
  • An intermediate pipe 6, of the same inside diameter as cylindrical body 3, is fixed to the outer surface of cylindrical body 3 (coaxially with both pipe 1 and cylindrical body 3), and comprises a tapered portion 6a downstream from cylindrical body 3 for the reasons explained in detail below.
  • a first channel C1 for feeding combustion supporting fluid (e.g. air) to nozzle 2 and combustion chamber CC, is therefore defined between central pipe 1 and intermediate pipe 6.
  • combustion supporting fluid e.g. air
  • Intermediate pipe 6 is fitted with a coaxial cylinder 7, which can be slid in either of the axial directions indicated by arrow F by an operator or an actuator (not shown) using a bracket 8 connected to coaxial cylinder 7.
  • Coaxial cylinder 7 is fitted (by known means) with a toroidal ring 9, which, in the Figure 1 embodiment, has a triangular cross section.
  • An outer pipe 10 is fitted coaxially with axis X, central pipe 1, cylindrical body 3, intermediate pipe 6, and coaxial cylinder 7, and terminates with a truncated-cone-shaped edge 10a at the free end facing combustion chamber CC.
  • a second channel C2 for feeding combustion supporting fluid (e.g. air) to combustion chamber CC, is therefore defined between intermediate pipe 6 and outer pipe 10.
  • the amount of combustion supporting fluid fed into combustion chamber CC along second channel C2 is regulated by adjusting the distance D between toroidal ring 9 and truncated-cone-shaped edge 10a, which is obviously done by simply moving coaxial cylinder 7 in either of the directions indicated by arrow F.
  • Cylindrical body 3 is fitted, in inventive manner, with a cap 11.
  • cap 11 comprises two superimposed cylindrical portions 11a, 11b of different diameters. More specifically, portion 11a, which is the portion actually fixed to cylindrical body 3, is larger in diameter than portion 11b.
  • a number of equally spaced, calibrated, radial holes 12 are formed in a cylindrical surface 11bc of portion 11b; and a number of equally spaced slots 13, sloping with respect to axis X (see Figures 2, 3, 5A in particular), are formed in an end surface 11bf of portion 11b.
  • slots 13 slope in the same direction as, but not necessarily at the same angle as, grooves 4.
  • an axial hole 14 ( Figures 1, 2, 5A) is formed precisely where the atomized liquid fuel comes out of nozzle 2.
  • cap 11 is supplied with combustion supporting fluid through calibrated holes 5 in cylindrical body 3.
  • a fan (not shown) supplies an adequate stream of combustion supporting fluid (e.g. air), which is conducted into outer pipe 10 enclosing the whole of combustion head 100.
  • combustion supporting fluid e.g. air
  • the air stream is then divided into three partial streams referred to respectively as primary air A1, secondary air A2, and tertiary air A3 ( Figures 1, 3, 6, 7).
  • the flow of primary air A1 is determined by the number and section of calibrated holes 5, and is subsequently further divided into radial primary air A1r (out of holes 12), swirled primary air A1sw (out of slots 13), and axial primary air A1a (out of central hole 14) ( Figures 1, 3, 7).
  • the flow of secondary air A2 is determined by the number and section of grooves 4 in cylindrical body 3.
  • secondary air stream A2 - which, downstream from cylindrical body 3, will be referred to as A2sw, for the sake of simplicity - has a high swirl component, and its expansion is contained substantially inside tapered portion 6a.
  • the flow of tertiary air A3 is determined by distance D between toroidal ring 9 and truncated-cone-shaped edge 10a; which distance D is adjustable as described previously.
  • tertiary air stream A3 produces, immediately downstream from truncated-cone-shaped edge 10a, an entrainment effect on the surrounding fluid.
  • this fluid comprises combustion products, some of which (Fr - Figures 1, 3, 6) are entrained by and mix with stream A3 (see below).
  • the combustion mechanisms are as follows.
  • the fuel is atomized by nozzle 2 ( Figure 6). Given the high kinetic energy of the fuel droplets, only a minimum number are affected by secondary air stream A2sw, while most reach tertiary air stream A3.
  • the small amount of fuel affected by secondary air stream A2sw is nevertheless sufficient to feed a secondary-combustion region (Figure 6) detached from and located further forward with respect to the end portion of combustion head 100.
  • the secondary-combustion region is characterized by a strong swirl (and turbulence) component which ensures stable combustion, also by virtue of internally recirculating hydrocarbon fragments (see below).
  • the temperature of the secondary-combustion region is fairly low (i.e. below 900°K, which is the temperature above which the thermal NO x formation process begins to have a noticeable effect) for substantially two reasons:
  • Recirculated fumes Fr also act as heat-absorbing inerts in direct proportion to the extent to which the combustion supporter and recirculated fumes are mixed.
  • combustion head 100 In combustion head 100 according to the invention, recirculated fumes Fr are allowed to mix well with tertiary air A3 before this becomes involved in the combustion process.
  • tapered portion 6a (Figure 1) (close to which the "Coanda effect” causes tertiary air A3 to flow) gives tertiary air A3 and recirculated fumes Fr enough time and space to mix effectively before reaching the tertiary-combustion region.
  • the tertiary-combustion region in which most of the fuel is burned, is located in the outer portion of the frame provides for improved heat exchange between the flame and the surrounding environment, thus further cooling the flame.
  • the above phenomena combine to reduce the formation of thermal NO x by reducing the temperature of the flame.
  • primary air stream A1 and the way in which it is distributed in cap 11 establish primary-combustion regions ( Figure 7) for mainly keeping combustion head 100 clean close to nozzle 2.
  • the hydrocarbon fragments are highly reactive, and partly fuel the secondary-combustion region to assist in stabilizing the flame.
  • the hydrocarbon fragments with greater kinetic energy manage to reach the portion of combustion head 100 surrounding nozzle 2. Since this portion of combustion head 100 is cooled by the airflow from behind, the hydrocarbon fragments, if there were no primary-combustion region, would settle on the cold surfaces, thus forming carbon deposits, which would eventually be thick enough to interfere with the fuel spray from nozzle 2, thus impairing the combustion process.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Spray-Type Burners (AREA)
EP05425122.8A 2005-03-04 2005-03-04 Brennerkopf für Flüssigbrennstoffbrenner Active EP1705424B1 (de)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP05425122.8A EP1705424B1 (de) 2005-03-04 2005-03-04 Brennerkopf für Flüssigbrennstoffbrenner
CNA200610057997XA CN1840963A (zh) 2005-03-04 2006-03-03 液体燃料喷烧器燃烧头

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05425122.8A EP1705424B1 (de) 2005-03-04 2005-03-04 Brennerkopf für Flüssigbrennstoffbrenner

Publications (3)

Publication Number Publication Date
EP1705424A1 EP1705424A1 (de) 2006-09-27
EP1705424A9 true EP1705424A9 (de) 2006-11-29
EP1705424B1 EP1705424B1 (de) 2015-07-29

Family

ID=35079403

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05425122.8A Active EP1705424B1 (de) 2005-03-04 2005-03-04 Brennerkopf für Flüssigbrennstoffbrenner

Country Status (2)

Country Link
EP (1) EP1705424B1 (de)
CN (1) CN1840963A (de)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE533995T1 (de) 2007-09-14 2011-12-15 Elco Burners Gmbh Brennerkopf und verfahren zur einstufigen verbrennung von brennstoff in einer vom brennerkopf beabstandeten verbrennungszone
IT1402828B1 (it) * 2010-12-06 2013-09-27 Riello Spa Testa di combustione per un bruciatore low-nox a combustibile liquido
CN103471098B (zh) * 2012-06-05 2018-02-23 雷乐士公司 用于低NOx液体燃料燃烧器的燃烧室缸盖
KR101738946B1 (ko) * 2016-04-07 2017-05-23 한국생산기술연구원 초 저공해 연소기
CN111981512B (zh) * 2020-07-31 2022-09-02 中国航发贵阳发动机设计研究所 一种燃油空气雾化装置
CN114183754B (zh) * 2020-09-14 2024-04-26 意大利利雅路股份有限公司 燃烧器的燃烧头

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1502459A (en) * 1974-08-30 1978-03-01 Ofr Spa Burner assembly for use in a fuel oil burner
US3979069A (en) * 1974-10-11 1976-09-07 Luigi Garofalo Air-atomizing fuel nozzle
CA1167369A (en) * 1982-01-28 1984-05-15 Gordon W. Ellis Oil burner head
DE4222839A1 (de) * 1992-07-11 1994-01-13 Kraft Industriewaermetechnik D Ölbrenner
DE4327497A1 (de) * 1993-08-16 1995-04-27 Kraft Industriewaermetechnik D Zerstäuberdüse für einen Brenner sowie Brenner
US6082113A (en) * 1998-05-22 2000-07-04 Pratt & Whitney Canada Corp. Gas turbine fuel injector

Also Published As

Publication number Publication date
EP1705424A1 (de) 2006-09-27
EP1705424B1 (de) 2015-07-29
CN1840963A (zh) 2006-10-04

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