EP0062797B1 - Procédé pour le service d'un brûleur à gaz dans un courant d'air et brûleur pour la réalisation du procédé - Google Patents

Procédé pour le service d'un brûleur à gaz dans un courant d'air et brûleur pour la réalisation du procédé Download PDF

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Publication number
EP0062797B1
EP0062797B1 EP82102431A EP82102431A EP0062797B1 EP 0062797 B1 EP0062797 B1 EP 0062797B1 EP 82102431 A EP82102431 A EP 82102431A EP 82102431 A EP82102431 A EP 82102431A EP 0062797 B1 EP0062797 B1 EP 0062797B1
Authority
EP
European Patent Office
Prior art keywords
burner
air
baffle plate
combustion
plate means
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
Application number
EP82102431A
Other languages
German (de)
English (en)
Other versions
EP0062797A1 (fr
Inventor
Hans Dipl.-Ing. Sommers
Hans Berg
Theo Dipl.-Phys. Jannemann
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.)
EON Ruhrgas AG
Original Assignee
Ruhrgas 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 Ruhrgas AG filed Critical Ruhrgas AG
Priority to AT82102431T priority Critical patent/ATE15536T1/de
Publication of EP0062797A1 publication Critical patent/EP0062797A1/fr
Application granted granted Critical
Publication of EP0062797B1 publication Critical patent/EP0062797B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F23D14/62—Mixing devices; Mixing tubes
    • F23D14/64—Mixing devices; Mixing tubes with injectors
    • 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
    • F23D14/04—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner
    • F23D14/08—Premix gas burners, i.e. in which gaseous fuel is mixed with combustion air upstream of the combustion zone induction type, e.g. Bunsen burner with axial outlets at the burner head

Definitions

  • the invention relates to a method for operating a burner exposed to an air flow, which consists of at least one gas nozzle, at least one conical mixing tube, a burner plate and flow guide plates for the air flow flowing through the housing, and is arranged in a shaft-shaped housing and the exhaust gases of which are mixed with the air flow be, as well as a burner to carry out the process.
  • the air flow, the influences of which the burner is exposed to, can, for. B. caused by a blower or the draft of a fireplace.
  • gas burners are used to directly heat a fan air flow by mixing the burner exhaust gases with the air flow.
  • This direct heating of an air stream is very advantageous in terms of energy, because in this way the entire heat content of the exhaust gas is used and the fuel is thus optimally utilized.
  • the exhaust gases of the premix burners used to date have a relatively high proportion of pollutants, in particular NO x content, which could have a negative effect on the material coming into contact with the blown air / exhaust gas mixture, the field of application of the direct heating burners is restricted.
  • the previously used premix burners are only supplied with a part of the air required for combustion by the injector effect of the gas through the mixing tube. The rest of the air needed for complete combustion diffuses into the resulting flames. If these burners are arranged directly in a fan air flow, they can only be operated with a certain throughput of fan air and in most cases only with a certain burner heat load. Changes in the temperature of the blower air flow by changing the burner heat load or changing the blower air quantity are only possible in a narrow range because this changes the flame stability, so that there is a risk that the burner is unsanitary, ie. H. works with incomplete combustion or that the flames go out.
  • a burner for vehicle heaters has become known, in which a fuel gas supply is arranged in the constriction of a venturi tube.
  • a first air fraction required for combustion is mixed at the narrow point of the Venturi tube with fuel gas flowing out of nozzle openings.
  • a second proportion of air required for combustion is directed past the Venturi tube and, viewed in the direction of flow, flows behind the burner plate from the outer circumference into the combustion process.
  • This burner is controlled by changing the first air fraction with a constant total air flow. This changes the influence of the second proportion of air on the combustion.
  • the change in the air ratio also means that the pressure ratios at different burner heat loads differ in the individual sections of the burner, so that optimal combustion conditions can only result with a single heat load setting.
  • the burner must be arranged outside the fan air flow, with the new disadvantage that the heat radiated from the burner housing does not contribute to the heating of the air flow.
  • the heat content contained in the fuel can therefore not be fully used to heat the air flow.
  • space must be available for the burner outside the blower duct, which often causes problems, particularly in the case of household appliances.
  • the object of the invention is to provide a generic method and a gas burner for carrying out the method with which a low-pollutant, in particular low-NO x Ab Gas is generated so that it is independent of the heat load of the burner and the flow velocity or the throughput of air in the housing, an optimal combustion and use of the heat content of the fuel is achieved.
  • the burner should be as compact and structurally simple as possible and allow a high heat load which can be varied over a wide range.
  • the object is achieved by the method according to claim 1 and the burner according to claim 2.
  • An essential feature of the method according to the invention is to switch off the effect of the air flow on the burner operation and at the same time to create the possibility of taking the total amount of combustion air required from the air flow before the combustion.
  • This is achieved in that, in the burner according to the invention for carrying out the method, on the one hand the gas nozzle and the mixing tube inlet and the flames on the burner plate are protected from direct access to air, and on the other hand in that the flow cross sections for the air are of the same size and thus the flow velocity the air in the area of the flow guide plates are kept almost the same.
  • the latter measure ensures that within the flow guide plates, ie. H.
  • the same pressure prevails both in the vicinity of the mixing tube inlet and on the flame side of the burner plate or at the exhaust gas inlet into the air flow - regardless of the air flow.
  • the burner can therefore work completely independently of the amount or flow velocity of the air flowing around it. Changes in the throughput of air and congestion behind the burner have no effect on the amount of air drawn in by the burner and, as a result, on flame stability and burnout. As a result, the burner according to the invention can be operated in a large thermal load range without the air ratio and thus the flame stability changing.
  • the burner has a burner plate which is connected to the mixing tube and is made of a good heat-conducting material and has a multiplicity of mixture passage openings, at least 4 openings per cm 2 , which are distributed over the entire burner plate cross section.
  • cooling fins made of a good heat-conducting material on the circumference of the burner plate, which protrude into the air flow and dissipate heat from the burner plate to the air, or a cooling coil through which water flows, so that the burner plate temperature remains almost constant.
  • the NOx content of the burner exhaust gas is extremely low because the flame temperature is homogeneous and lower than for burners in which only part of the required combustion air is premixed with the gas becomes.
  • the exhaust gas is used to directly heat the air flow, there is therefore no risk of possible damage to the goods or persons coming into contact with the exhaust gas or the exhaust gas / air mixture.
  • the burner is arranged directly in the air flow, the heat radiated from the burner housing contributes to heating the air flow, so that practically the entire heat content of the fuel gas is used to heat the air flow.
  • FIGS. 1 and 2 can, for. B. used in a household clothes dryer.
  • the burner is arranged concentrically in the cylindrical, horizontally lying shaft-shaped housing 1, through which the dry air to be heated flows, which is conveyed by a blower (not shown).
  • the burner consists essentially of the gas nozzle 2 and the conical mixing tube 3 with the inlet opening 8, to which the burner plate 4 is connected.
  • the well heat-conducting material z. B. copper existing burner plate 4 has a nominal heat load of 5 kW about 500 mixture passage openings 14, which are evenly distributed over the entire burner plate cross section of about 50 cm 2 .
  • the heat load on the burner plate is so great that the plate has to be cooled in order to prevent it from overheating and thus preventing the air ratio from changing or the flames from flashing back.
  • cooling fins 7 which also consist of a good heat-conducting material and which protrude into the air flow and transfer the burner plate heat to the air.
  • the burner plate temperature is kept almost constant even when the burner load changes.
  • the burner plate including the cooling fins can be cast from one part.
  • the gas nozzle 2 and the lower part of the mixing tube res 3 are surrounded by the flow guide plate 5, which consists of a hemispherical lower part and an adjoining cylinder jacket.
  • both cylindrical flow guide plates 5 and 6 is equal to the diameter of the burner plate 4, so that the free flow cross-section for the blower air - which is formed by the flow guide plates 5, 6 and the wall of the housing 1 - and thus their flow speed in the area of the flow guide plates is about the same size. In this way the influence of the fan air on the burner is switched off. It is therefore possible to reduce the heat load on the burner to less than 50% of its nominal heat load, regardless of the fan air flow.
  • the mixing tube 3 Immediately in front of the burner plate, the mixing tube 3 has a short cylindrical section for better mixing of the fuel gas / combustion air mixture. -
  • the air ratio of the burner is at a Nenn certificationbelastun g of 5 kW with the use of natural gas, depending on the calorific value of about 1.05 to 1.35.
  • the cross section of the shaft-shaped housing 1, the burner parts and the flow guide plates can deviate from the shape described in the example above.
  • the housing can have, for example, a rectangular or conically widening cross section.
  • the outer shape of the burner plate and the guide plates can also be made rectangular in accordance with the shape of the housing; however, a cylindrical design is also possible. If the diameter of the housing changes in the area of the burner, the diameter of the flow guide plates must change accordingly and z. B. with a conical extension form a larger opening angle than the air shaft, since otherwise the condition of the same flow cross-sections for the blower air would not be met.
  • the shaft-shaped housing does not have to lie horizontally, as in the example above, but can be arranged as desired, depending on the space available.
  • the blower effect is based on the buoyancy or draft of the exhaust gases in the fireplace.
  • the burner plate 4 is also cooled due to the large surface heat load, with the help of the cooling coil 13 attached to the edge of the burner plate, through which the heated domestic or heating water flows as a cooling medium.
  • the flow plate 6 connects the burner to the heat exchanger 10 and is at the same time the lateral boundary of the combustion chamber 12.
  • the flow guide plates 5 and 6 cause the formation of a differential pressure between the mixing pipe inlet 8 and the exhaust gas outlet 9 into the air flow - here behind the heat exchanger 10 - prevents.
  • a lift occurs in the combustion chamber, which only affects the surface of the burner, but not the air supply to the injectors, and thus influences the air ratio with changing loads.
  • This buoyancy can be prevented either by horizontal arrangement of the gas water heater or by measures such as. B. are mentioned in the unpublished DE-A-3 018 752 can be compensated.
  • the housing 1 forms, together with the flow guide plates 5 and 6 according to the invention, a constant free flow cross section for the air. A larger than the amount of air required for complete combustion is sucked in according to the invention with the help of the gas jets emerging from the gas nozzles 2 transversely to the flow direction of the air completely independently of the changing chimney draft.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)

Claims (6)

1. Procédé pour le service d'un brûleur à gaz dans un courant d'air, composé au moins d'un injecteur (2), au moins d'un tube mélangeur conique (3), d'une plaque de brûleur (4) et de tôles de guidage (5, 6) pour le courant d'air traversant le corps (1), et disposé dans un corps (1) en forme de cuve et dont les fumées sont mélangées avec le courant d'air, caractérisé par le fait qu'un débit d'air de combustion en excès de celui requis en fonction du débit calorifique est aspiré perpendiculairement au sens de l'écoulement du courant d'air en étant induit par le gaz sortant de l'injecteur (2) et entrant dans le tube mélangeur (3) et que la formation d'une différence de pression entre l'entrée du tube mélangeur (8) et la sortie des fumées (9) est empêchée par les tôles de guidage (5, 6).
2. Brûleur pour la réalisation du procédé selon la revendication 1, dont la plaque de brûleur (4) immédiatement en aval du tube mélangeur (3) consiste d'un matériau fort conducteur de chaleur et est munie d'un nombre relativement grand d'ouvertures de sortie du mélange (14) reparties sur toute la section de la plaque de brûleur (4), et dont au moins une tôle de guidage (5) est disposée dans la zone de l'injecteur (2) et une autre tôle de guidage (6) entoure la zone des flammes en aval de la plaque de brûleur (4), caractérisé par le fait que la plaque de brûleur (4) est munie d'au moins quatre ouvertures de sortie du mélange (14) par cm2 et que la tôle de guidage (5), disposée dans la zone de l'injecteur (2), entoure au moins l'injecteur et la partie inférieure du tube mélangeur (3), les tôles de guidage (5, 6) formant conjointement avec les parois du corps (1) des sections libres identiques pour l'écoulement de l'air.
3. Brûleur selon la revendication 2, caractérisé par le fait que la circonférence de la plaque de brûleur (4) est munie de plusieurs ailettes de refroidissement (7) en matériau fort conducteur de chaleur, faisant saillie dans le courant d'air.
4. Brûleur pour appareils de production d'eau chaude selon la revendication 2, caractérisé par le fait que la circonférence de la plaque de brûleur (4) est munie d'un serpentin de refroidissement à l'eau (13).
5. Brûleur selon l'une des revendications 2 à 4, caractérisé par le fait que la plaque de brûleur (4) est de forme circulaire et que la tôle de guidage (5) dans la zone de l'injecteur (2) et de l'ouverture d'entrée (8) du tube mélangeur (3) est de forme hémisphérique ou conique se prolongeant dans un corps cylindrique et que la tôle de guidage (6) située dans la zone des flammes prend la forme d'un corps cylindrique partant de la plaque de brûleur (4), le diamètre de chacune des deux tôles de guidage cylindriques (5, 6) étant égal au diamètre de la plaque du brûleur (4).
6. Brûleur selon l'une des revendications 2 à 5, caractérisé par le fait que la longueur de la tôle de guidage (6) dans la zone des flammes représente environ le double jusqu'au septuple, de préférence environ le triple jusqu'au quintuple de la longueur des flammes.
EP82102431A 1981-04-03 1982-03-24 Procédé pour le service d'un brûleur à gaz dans un courant d'air et brûleur pour la réalisation du procédé Expired EP0062797B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT82102431T ATE15536T1 (de) 1981-04-03 1982-03-24 Verfahren zum betrieb eines einem luftstrom ausgesetzten gasbrenners sowie brenner zur durchfuehrung des verfahrens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3113416A DE3113416A1 (de) 1981-04-03 1981-04-03 Verfahren zum betrieb eines einem luftstrom ausgesetzten gasbrenners sowie brenner zur durchfuehrung des verfahrens
DE3113416 1981-04-03

Publications (2)

Publication Number Publication Date
EP0062797A1 EP0062797A1 (fr) 1982-10-20
EP0062797B1 true EP0062797B1 (fr) 1985-09-11

Family

ID=6129204

Family Applications (1)

Application Number Title Priority Date Filing Date
EP82102431A Expired EP0062797B1 (fr) 1981-04-03 1982-03-24 Procédé pour le service d'un brûleur à gaz dans un courant d'air et brûleur pour la réalisation du procédé

Country Status (5)

Country Link
US (1) US4457704A (fr)
EP (1) EP0062797B1 (fr)
AT (1) ATE15536T1 (fr)
CA (1) CA1192829A (fr)
DE (1) DE3113416A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN110822424A (zh) * 2019-11-22 2020-02-21 青岛天正洁能环保科技有限公司 一种静态混风器

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CN107013912B (zh) * 2017-05-31 2023-09-19 深圳智慧能源技术有限公司 自冷却引射式燃烧装置
CN107062225B (zh) * 2017-05-31 2023-09-19 深圳智慧能源技术有限公司 自冷却引射式燃烧器
CN109140439A (zh) * 2017-06-28 2019-01-04 青岛海尔洗衣机有限公司 一种燃烧筒、干衣设备加热装置及干衣设备
CN109579003B (zh) * 2018-11-09 2020-06-23 鞍钢股份有限公司 一种组合型内燃式低温低NOx天然气燃烧器及燃烧方法
CN109579004B (zh) * 2018-11-09 2020-06-23 鞍钢股份有限公司 一种低温低NOx天然气燃烧系统及燃烧方法

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN110822424A (zh) * 2019-11-22 2020-02-21 青岛天正洁能环保科技有限公司 一种静态混风器
CN110822424B (zh) * 2019-11-22 2021-10-19 青岛天正洁能环保科技有限公司 一种静态混风器

Also Published As

Publication number Publication date
ATE15536T1 (de) 1985-09-15
DE3113416C2 (fr) 1989-11-23
EP0062797A1 (fr) 1982-10-20
DE3113416A1 (de) 1982-10-21
US4457704A (en) 1984-07-03
CA1192829A (fr) 1985-09-03

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