WO2011022846A1 - Brûleur à mazout, en particulier pour huile lourde - Google Patents

Brûleur à mazout, en particulier pour huile lourde Download PDF

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Publication number
WO2011022846A1
WO2011022846A1 PCT/CH2009/000286 CH2009000286W WO2011022846A1 WO 2011022846 A1 WO2011022846 A1 WO 2011022846A1 CH 2009000286 W CH2009000286 W CH 2009000286W WO 2011022846 A1 WO2011022846 A1 WO 2011022846A1
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WO
WIPO (PCT)
Prior art keywords
burner
flow channel
oil
air
flow
Prior art date
Application number
PCT/CH2009/000286
Other languages
German (de)
English (en)
Inventor
Philippe Maeder
Matthias Bobst
Original Assignee
Ammann Schweiz Ag
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 Ammann Schweiz Ag filed Critical Ammann Schweiz Ag
Priority to PCT/CH2009/000286 priority Critical patent/WO2011022846A1/fr
Publication of WO2011022846A1 publication Critical patent/WO2011022846A1/fr

Links

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
    • F23D11/001—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space spraying nozzle combined with forced draft fan in one unit
    • 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
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/101—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet
    • F23D11/102—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber
    • F23D11/103—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting before the burner outlet in an internal mixing chamber with means creating a swirl inside the mixing chamber
    • 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
    • F23D11/10—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour
    • F23D11/106—Burners using a direct spraying action of liquid droplets or vaporised liquid into the combustion space the spraying being induced by a gaseous medium, e.g. water vapour medium and fuel meeting at the burner outlet

Definitions

  • the invention relates to an oil burner, in particular for heavy oil, and a hot gas generator with the oil burner according to the preambles of the independent claims.
  • the burner output is controlled by the injected oil quantity and the temperature of the generated hot gas flow by the supplied air volume.
  • some burners also have the option to change the flow cross-section for the atomizing air.
  • Even though the latter burners offer a clear improvement in terms of adaptability to different operating conditions compared to solid geothermal burners. have shown in practice that there is still a need for improvement, since these burners are used not only under a variety of conditions, but are operated with different fuel qualities, and it often happens that the fuel quality varies during operation.
  • the invention relates in a first aspect to a preferably suitable for heavy oil oil burner.
  • the oil burner has a first flow channel, which is traversed by atomized air during operation and in which, during operation with oil injection means, such as injectors, the oil to be burned is injected and entrained by the Zerstäuber Kunststoffströmung, whereby it is atomized and transported into the combustion zone , Furthermore, the oil burner comprises a second flow channel, which is traversed during operation with combustion air in order to supply it to the combustion zone.
  • the burner outlet side or combustion zone side exits of these two flow channels are designed such that during operation of emerging from the outlet of the second flow channel combustion air flow forms an enveloping flow around the emerging from the outlet of the first flow channel and the atomized atomizing Zerstäuber Kunststoff- ström around, the Zerstäuberluftstrom circumferential is completely surrounded by the combustion air flow.
  • the oil burner is configured such that a separate adjustment of the atomizing air quantity flowing through the first flow channel during operation and the amount of combustion air flowing through the second flow channel is possible, that is, these air volumes are individually, i. via separately operable adjustment, are adjustable.
  • the terms "atomizing air quantity” and “amount of combustion air” are used here and below to denote in each case the amount of air per unit of time, that is to say the volume or mass flow of atomizing air and combustion air passing through the respective flow channel during operation.
  • the separate adjustability of atomizing air quantity and amount of combustion air can be realized by a wide variety of setting members, e.g.
  • separately adjustable throttle bodies for the atomizer and combustion air provided by a common fan, by two separately controllable fans for the atomizing air and the combustion air and / or by independently adjustable geometries of the flow cross sections for the atomizing air and the combustion air.
  • the operating states in the burner itself can be influenced in a wide range by separate regulation or adjustment of the atomizing air quantity, the amount of combustion air and the amount of fuel supplied per unit of time, which results in a significantly improved adaptability with respect to a wide variety of operating conditions compared with the prior art and fuel qualities results.
  • the outlet of the first flow channel for the atomized atomizing atomizing air flow has a circular or annular outlet cross-section and the combustion zone-side outlet of the second Flow channel for the combustion air flow to an annular outlet cross-section, which is seen in the flow direction concentric with the outlet cross-section of the first flow channel.
  • the means for oil injection comprise a burner lance with one or more nozzles which, viewed in the flow direction of the atomizer air flow, preferably spray radially outwardly.
  • the first flow channel has an annular cross-section in the region of the nozzles, since this results in a particularly uniform distribution of the injected oil in the atomizer air stream emerging from the first flow channel leaves .
  • the flow cross-section of the first flow channel is adjustable in the region of the outlet of the nozzles of the burner lance, preferably during operation of the burner. This makes it possible to influence the flow speed of the atomizing air in the area of the nozzle outlets as well as the pressure loss in the first flow channel for the atomizing air, and thus the atomizing power of the atomizing air and its quantity. It is preferred that the adjustment of the flow cross-section of the first flow channel by axial displacement of the burner lance against an outer boundary of the first flow channel in this Area can be done. This makes it possible to realize a relatively simple and reliable way the setting ⁇ bility of the flow cross section of the flow channel formed between the burner lance and Zerstäuber Kunststoffesterability.
  • the oil burner to realize the separate adjustability of the atomizing air quantity and the amount of combustion air separately operable throttle for the atomizing air and the combustion air.
  • the atomizer and combustion air streams which flow through the first and the second flow channel during operation, can be adjusted individually to the desired air quantities in a simple manner, even if they are generated by a common blower.
  • the oil burner is designed such that an adjustment of the amount of atomizing air, the amount of combustion air or the Zerstäububer- and the combustion air amount during operation of the burner is possible.
  • This makes it possible to adapt the oil burner without interrupting operation to changing operating conditions or fuel qualities.
  • the setting can be done manually or via actuators of a control, resulting in the latter case, the advantage that the burner can be integrated into a control loop, which allows automatic adjustment of Zerstäububer- and combustion air quantity to the respective operating conditions and fuel qualities.
  • a swirling device is provided in the first atomizing air flow channel upstream of the region in which the oil to be atomized is injected in operation, which constitutes the atomizing air flow prior to impinging on the injected oil Impose twist.
  • a swirl device is arranged in the second flow channel for the combustion air upstream of the outlet end thereof, which forces the combustion air flow during operation before exiting from the second flow channel to a twist ⁇ .
  • This ensures that the combustion air emerging from this flow channel during operation forms a spiral enveloping flow around the atomizer air flow that is discharged from the first flow channel and atomizes the oil. This in turn favors the formation of a stable, rotationally symmetric combustion zone and complete combustion of the injected oil.
  • the aforementioned swirl devices are preferably designed as a swirl body with a plurality of swirl vanes or as helical vanes. Such swirl devices have proven to be expedient and reliable in the field of oil burners.
  • the oil burner also has a third flow channel, which is flowed through with additional air during operation, for supplying additional air to the combustion zone.
  • the outlet region of this flow channel for the additional air is designed in such a way that the combustion air stream exiting from the second flow channel as the sheath flow is surrounded by additional air flowing out of the third flow channel.
  • further air can be supplied to the outer region of the combustion zone, which further promotes complete combustion.
  • the additional air can simultaneously serve the cooling of external burner components.
  • the outlet of the third flow channel advantageously has an annular shape. Cross-section, which is seen in the flow direction concentric with the outlet cross-sections of the first flow channel and the second flow channel. This makes it possible to realize a rotationally symmetrical flow structure at the burner outlet, which is conducive to a uniform flame pattern and good combustion.
  • the oil burner with a third flow channel for additional air guidance, it is preferred for the oil burner to have injectors and to be designed in such a way that in the
  • the oil burner is designed in such a way that the injectors are supplied during operation with a subset of the adjustable amount of combustion air, which is preferred, then a coupling between combustion air quantity and additional air quantity results such that an increase in the quantity of combustion air also leads to an increase in the additional air quantity leads and vice versa.
  • the oil burner comprises a single-stage blower which serves to provide both the atomizing air and the combustion air.
  • Such oil burners are inexpensive and robust.
  • a second aspect of the invention relates to a hot gas generator with a
  • Combustion chamber which forms a combustion chamber into which an oil burner according to the first aspect of the invention opens, such that the combustion chamber surrounds the combustion zone during operation.
  • Hot gas generator has this a plurality of preferably identical oil burner according to the first aspect of the invention, which open into the combustion chamber, wherein it is further preferred that they open at identical axial positions with respect to the flow direction of the hot gas generated in operation with the hot gas generator in the furnace.
  • hot gas generators according to the invention having virtually any heating power can be provided with a burner size.
  • FIG. 1 is a perspective top view obliquely from above of a heavy oil burner according to the invention
  • FIG. 2 shows a vertical section through the heavy oil burner from FIG. 1; FIG. and
  • FIGS. 1 and 2 shows a perspective sectional view through the burner arrangement of the burner from FIGS. 1 and 2.
  • FIGS. 1 and 2 A preferred embodiment of the inventive oil burner in the form of a heavy oil burner 1 is shown in FIGS. 1 and 2, once in a perspective plan view and once in a vertical section.
  • the oil burner basically consists of a single-stage radial fan 2 for providing the atomizing and combustion air and a burner assembly 3, which are screwed together.
  • the fan 2 provides compressed air during operation with an overpressure of about 100 to 150 mbar for Ver ⁇ addition.
  • Fig. 2 in conjunction with Fig. 3, which shows the burner assembly 3 in perspective in section, located in the center of the burner assembly 3, a burner lance 4, at the burner outlet side or bewed Vietnamese splashszonen sum end of a nozzle body 5 with radial outwardly extending nozzle bores (not shown) which form claims nozzles, is arranged.
  • the burner lance 4 is connected to a supply line 20 for heavy oil.
  • a central bore is present, which connects the supply line 20 with the nozzle bores.
  • the burner lance 4 is coaxially surrounded by a first tube 6, which in the region of the outlet of the nozzle bores from the nozzle body 5 has an insert 7, which tapers the tube cross section in this area to a venturi.
  • a first, annular flow channel 8 is formed (demanding first flow channel), which in the region of the outlet of the nozzle holes from the nozzle body 5 its smallest flow cross-section has and via a separately operable first throttle valve 9 with the outlet side of the blower 2 is connectable.
  • a spiral baffle 10 Upstream of the nozzle body 5 in the first flow channel 8 is a spiral baffle 10, which imparts a twist to the atomizing air Z flowing through the flow channel 8 during its operation into the region of the flow channel 8 bounded by the insert 7.
  • the baffle 10 is supported by the burner lance 4 and is firmly connected thereto.
  • the burner lance 4 is held at the "cold" end of the burner assembly 3 in a releasable clamping device 11 and can after releasing this Klemmvorrich- tion 11 are axially displaced within the first tube 6. This makes it possible, formed between the insert 7 and the nozzle body 5 in the region of the outlet of the nozzle bores smallest cross-section of the first flow channel 8 by axial displacement of the
  • the first tube 6 is coaxially surrounded by a second tube 12, which in turn is coaxially surrounded by a third tube 16, which has a nozzle-like insert 19 in the region of its burner outlet end.
  • the insert 19 tapers the tube cross-section in this area towards the burner outlet-side end first suddenly and then steadily increasing.
  • a second, annular flow channel 17 is formed for combustion air (demanding second flow channel).
  • This second flow channel 17 can be connected via a separately operable second throttle valve 18 with the outlet side of the blower 2.
  • the insert 19 surrounds the first tube 6 with the insert 7 arranged therein in the region of the outlet-side end of the insert 7 and delimits the second flow channel 17 for the combustion air V formed in this region between it and the nozzle ring 14 in such a way that Operation emerging from the second flow channel 17 combustion air V forms a sheath flow around the emerging from the insert 7 and thus from the first flow channel 8 and atomized atomized atomizing air flow Z around.
  • the third tube 16 is coaxially surrounded by a fourth tube 21. Between the third tube 16 and the fourth tube 21, a third annular flow channel 22 for additional air L is formed (demanding third flow channel).
  • the fourth tube 21 surrounds the third tube 16 in the region of the outlet-side end the same so that in the operation of the third
  • Flow channel 22 exiting additional air L forms a sheath flow to the emerging from the third tube 16 and thus from the second flow channel 17 combustion air flow V.
  • the third is
  • Flow channel 22 for the additional air L via injector tubes 23 connected to a space 25 which is bounded by the second throttle valve 18 for the combustion air V.
  • the fourth tube 21 has suction openings 24 which connect the third flow channel 22 surrounded by the latter and the outlet sides of the injector tubes 23 to the environment.
  • the burner lance 4 is fed via a fuel pump (not shown) to heavy oil with an overpressure of 2 to 3 bar, which is then injected via the nozzle bores of the nozzle body 5 into the first flow channel 8.
  • atomizing air Z from the blower 2 is supplied to the first flow channel 8 via the first throttle flap 9 and a first collecting space 26, and combustion air V from the blower 2 is supplied to the second flow channel 17 via the second throttle flap 18 and a second plenum 25.
  • the atomizing air Z flowing in the first flow channel 8 passes through the region in which the spiral guide plate 10 is arranged, and then enters the region in which the heavy oil is injected via the nozzle bores of the nozzle body 5 into the first flow channel 8 as swirling flow , It tears the injected heavy oil with it and then exits as atomizing air flow Z with finely dispersed heavy oil particles from the insert 7 of the first tube 6, in order then to be burned in the combustion zone.
  • Combustion air V occurs in the area of the exit side End of this flow channel 17 in a swirl body 27 arranged there, which it leaves as a swirl flow. Subsequently, it enters the nozzle-shaped insert 19, which forms the outlet-side end of the second flow channel 17. The latter then leaves it as a spirally rotating flow which forms an envelope flow of combustion air V around the atomizer air stream Z exiting from the insert 7 and thus out of the first flow channel 8 with the atomized heavy oil contained therein.
  • a subset of the combustion air quantity V entering the second plenum 25 via the second throttle valve 18 is expanded via the injector tubes 23 into the third flow channel 22.
  • 24 fresh air from the environment is sucked into the third flow channel 22 by the injector generated thereby via the intake openings 24, which then mixed with the air expanded through the injectors 23 and continues as claim-compliant additional air L in the third flow channel 23.
  • the additional air flow Z passes through an arrangement of guide ribs 28 before it emerges therefrom, thereby forming a straightened envelope flow around the spiral envelope flow of combustion air V emerging from the second flow channel 17.
  • the burner 1 can also be operated with a fuel gas.
  • a further annular flow channel 13 is formed between the first tube 6 and the second tube 12, which opens into a nozzle ring 14 on the burner outlet side and is connected at its other end to a fuel gas feed line 15.
  • Fuel gas can be conducted from the fuel gas feed 15 to the nozzle ring 14 via this further flow channel 13, for injecting the fuel gas into the combustion zone.
  • the throttle valves 9, 18 can be adjusted individually in such a way that a desired flame pattern is obtained, optionally with additional adjustment of the axial position of the burner lance 4 and the amount of fuel supplied. If an operation with fuel gas takes place, the supplied fuel gas amount can be adjusted.

Abstract

L'invention concerne un brûleur à mazout (1) comportant une lance (4) qui sert à injecter l'huile à brûler, lors du fonctionnement, par l'intermédiaire de buses s'étendant vers l'extérieur, dans un premier canal d'écoulement (8) parcouru par de l'air pulvérisé (Z) et présentant une section transversale annulaire. Dans la région de la sortie du premier canal d'écoulement (8), ce dernier est entouré coaxialement par un deuxième canal d'écoulement (17) annulaire qui, lors du fonctionnement, est parcouru par de l'air de combustion (V) et dont la zone de sortie est formée de sorte que, lors du fonctionnement, le flux d'air pulvérisé (Z) comportant l'huile injectée et sortant du premier canal d'écoulement (8) est entouré d'un écoulement enveloppant, sortant du deuxième canal d'écoulement (17). Le brûleur à mazout (1) selon l'invention est conçu de façon à permettre un réglage séparé des volumes d'air pulvérisé et d'air de combustion parcourant le premier canal d'écoulement (8) et le deuxième canal d'écoulement (17).
PCT/CH2009/000286 2009-08-26 2009-08-26 Brûleur à mazout, en particulier pour huile lourde WO2011022846A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
PCT/CH2009/000286 WO2011022846A1 (fr) 2009-08-26 2009-08-26 Brûleur à mazout, en particulier pour huile lourde

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CH2009/000286 WO2011022846A1 (fr) 2009-08-26 2009-08-26 Brûleur à mazout, en particulier pour huile lourde

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WO2011022846A1 true WO2011022846A1 (fr) 2011-03-03

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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1139703A (fr) * 1954-11-26 1957-07-04 Wistra Ofenbau Brûleur à huile, en particulier pour huiles lourdes de chauffage
US4303386A (en) * 1979-05-18 1981-12-01 Coen Company, Inc. Parallel flow burner
DE3040830A1 (de) * 1980-10-30 1982-05-13 L. & C. Steinmüller GmbH, 5270 Gummersbach Verfahren zur verminderung der no(pfeil abwaerts)x(pfeil abwaerts) -emission
EP0684428A2 (fr) * 1994-05-24 1995-11-29 E.E.T. UMWELT- und GASTECHNIK GmbH Dispositif pour l'injection d'air dans l'espace de combustion d'un brûleur de torche et brûleur de torche
EP2085145A1 (fr) * 2008-02-01 2009-08-05 Delavan Inc Buse de combustible unidirectionnelle assistée par air comprimé

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1139703A (fr) * 1954-11-26 1957-07-04 Wistra Ofenbau Brûleur à huile, en particulier pour huiles lourdes de chauffage
US4303386A (en) * 1979-05-18 1981-12-01 Coen Company, Inc. Parallel flow burner
DE3040830A1 (de) * 1980-10-30 1982-05-13 L. & C. Steinmüller GmbH, 5270 Gummersbach Verfahren zur verminderung der no(pfeil abwaerts)x(pfeil abwaerts) -emission
EP0684428A2 (fr) * 1994-05-24 1995-11-29 E.E.T. UMWELT- und GASTECHNIK GmbH Dispositif pour l'injection d'air dans l'espace de combustion d'un brûleur de torche et brûleur de torche
EP2085145A1 (fr) * 2008-02-01 2009-08-05 Delavan Inc Buse de combustible unidirectionnelle assistée par air comprimé

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