EP0487700B1 - Brenner - Google Patents

Brenner Download PDF

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Publication number
EP0487700B1
EP0487700B1 EP91912132A EP91912132A EP0487700B1 EP 0487700 B1 EP0487700 B1 EP 0487700B1 EP 91912132 A EP91912132 A EP 91912132A EP 91912132 A EP91912132 A EP 91912132A EP 0487700 B1 EP0487700 B1 EP 0487700B1
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EP
European Patent Office
Prior art keywords
burner
apertures
aperture
fuel
boundary
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 - Lifetime
Application number
EP91912132A
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English (en)
French (fr)
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EP0487700A1 (de
Inventor
David Thomas Kirk
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.)
LANEMARK Ltd
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LANEMARK Ltd
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Publication date
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Publication of EP0487700A1 publication Critical patent/EP0487700A1/de
Application granted granted Critical
Publication of EP0487700B1 publication Critical patent/EP0487700B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D17/00—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel
    • F23D17/002—Burners for combustion conjointly or alternatively of gaseous or liquid or pulverulent fuel gaseous or liquid fuel
    • 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
    • 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

Definitions

  • This invention relates to improvements in or relating to burners more particularly of a type known in the art as a "Matrix burner”.
  • Matrix burners are versatile in application and can be used both in domestic and in industrial plants or installations. Relatively large numbers of these burners may be employed in industrial furnaces and can be used to burn off waste gases with the potential of recycling the energy back into the processing plant.
  • a burner having a head provided with an array or matrix of combustion air apertures, said burner head having an outer boundary, spaced plate portions defining a fuel supply gallery or passageway to said apertures, characterised by the combustion air apertures being arranged in outer, middle and inner aperture rings, the outer ring closely following the outer boundary of the burner head and being adjacent to said boundary.
  • the matrix of apertures is configured to prevent or restrict any anomalous high temperature or high corrosion regions occurring on the plate portions by giving substantially the same freedom of access of the fuel supply in the gallery to each of the apertures.
  • the plate portions may be spaced from one another by spacers and, accordingly, the aperture matrix may be configured to allow for substantially even flow characteristics of the fuel supply through the gallery around said spacers.
  • the aperture ring comprises a series of combustion air apertures, at least half or the majority of which are spaced at a distance from said boundary by an amount which is less than or equal to the spacings between one another.
  • One embodiment of the burner of the present invention has a head with circular shaped plate portions and said aperture ring consists of a circle of apertures spaced closely to one another and close to said boundary.
  • the apertures in the circular ring are, preferably, spaced equidistantly from one another and are preferably of circular form.
  • each aperture is spaced from the boundary by a distance not more than two (and preferably not more than three) times the distance in between each aperture.
  • the inner aperture ring comprises a series of circular apertures which are arranged concentrically with the outer aperture ring so that each of the apertures in the inner ring is radially aligned with respective apertures in the outer ring, said inner and outer ring apertures being concentrically aligned with the circular plate portions of the burner head.
  • the middle aperture ring may comprise a series of circular apertures which are displaced circumferentially relative to the outer and inner aperture rings and preferably such that the aperture configuration results in an array of substantially triangular shaped sector regions extending around the circumference of the plate portions with spacers being provided inbetween the triangular shaped sectors.
  • the burner is provided with radial ports at said boundary for radial discharge of the fuel and many other advantageous features of the burner will be apparent from the following description and drawings.
  • the radial ports may be spaced equally around said boundary in between said apertures in the outer ring.
  • the plate portions will normally be of 16 gauge metal.
  • the burner may be a dual fuel burner in which the gallery or passageway is for a main fuel supply to be fed to said apertures, the arrangement being such that the burner can be run on the first or main fuel supplied along the gallery or passageway to said apertures and may alternatively be operated on a second fuel mixed with combustion air supplied through said apertures.
  • the burner may be operated on a mixture of the first main fuel and the secondary fuel.
  • the secondary fuel is introduced into the burner by way of a supply line arranged within the supply line of the main fuel supply.
  • the secondary fuel may be oil and accordingly an oil lance may be inserted in the main fuel supply line to the burner.
  • the oil lance may have a tip which extends beyond said plate portions in order to spray fuel oil above said plate portions for mixing with combustion air drawn through said apertures for ignition at the burner, preferably by a spark ignitor.
  • the amount by which the lance tip extends beyond the burner head is, preferably, adjustable.
  • separate controls are provided for delivery of either or both fuels to the burner.
  • the same burner may be employed in a single fuel situation or in a double fuel situation, an inner pipe (e.g. guide pipe for the oil lance where applicable) being used for the secondary supply merely being closed off where the burner is to be used in a single fuel application only.
  • an inner pipe e.g. guide pipe for the oil lance where applicable
  • An advantage of such a dual fuel system is the production of a desirable and controllable flame shape which is most important in a furnace application, e.g. a hydrocarbon cracking process in the petrochemical industry, where, for example, £500,000 worth of ceramic tube equipment may be needed to constrain the flame production by the burners.
  • a matrix burner head 1 suitable for use in a furnace, or for example a petrochemical plant, has an upper circular metal plate portion 2 joined to a lower circular metal plate portion 3 at the circumferential boundary wall 4, for example by welding.
  • Boundary wall 4 provides an outer boundary of the burner head 1.
  • the upper and lower plate portions 2 and 3 are spaced apart from one another by spacers 5 in a generally known manner in order to provide a gallery or passageway G inbetween the plate portions 2 and 3 leading to individual apertures 6a,7a,8a of outer 6, middle 7, and inner 8 aperture rings.
  • a gaseous fuel is conveyed down the central fuel pipe 9 and flows through the gallery G to the apertures 6a,7a,8a where it mixes with combustion air being drawn up through the centre of said apertures 6a,7a,8a providing a mixture for burning.
  • the apertures 6a,7a and 8a are of the broached or pierced type in which small holes or ports P (see FIGURE 1) are provided around the circumference of the individual apertures 6a,7a,8a to allow fuel gas to flow therethrough into the apertures.
  • the apertures 6a,7a,8a are formed by a downwardly depending tubular portion a of the upper plate 2 snugly overlapping with an upwardly depending tubular portion b of the lower plate as shown best in FIGURE 2.
  • the present invention is not confined to the apertures 6a,7a,8a being of the broached type and could instead be of the "annular gap" form in which the gas escapes from the gallery G into the apertures via an annular gap left inbetween the overlapping tube pcrtions a,b of the upper and lower plates, which overlapping tube portions form the individual apertures.
  • Both the broached and annular gap type apertures are known generally.
  • the burner 1 is also provided with radial ports P' around the circumference or boundary 4 between the two plate portions 2,3.
  • the radial ports P' are formed in the upper plate portion and allow a radial discharge of gaseous fuel around the boundary of the burner head 1.
  • the outer aperture ring 6 consists of a series (in this case 24) of apertures 6a of the same size and spaced equiangularly around the centre of the burner and following the boundary 4 and arranged closely adjacent thereto.
  • the array of apertures 6a,7a,8a form a matrix which has been produced in order to seemingly optimise fuel flow characteristics within the gallery G to the individual apertures, whilst also taking into account the resistance to flow afforded by the spacers 5.
  • the aperture matrix is configured in order to substantially eliminate anomalous hot spots which could ultimately give rise to corrosion in the burner, as well as to equalise flow distribution to the apertures 6a,7a,8a.
  • burners can be individually designed to meet specific site requirements.
  • the aperture matrix comprises 8 circumferentially spaced triangular sector regions (one of these regions is outlined by a chain dotted line X) consisting of 6 individual apertures, one aperture 8a being from the innermost ring 8, two apertures 7a being from the middle ring and three apertures 6a being from the outer ring 6.
  • Spacers 5 are provided inbetween the triangular sectors and alternate from the provision of two spacers to one spacer on a circumferential path around the burner.
  • These type of burners are very versatile and can be run for example to produce 2 million B.T.U.'s per hour or 100 B.T.U.'s per hour.
  • the apertures 6a are positioned very close to the boundary line and indeed are closer to the boundary wall 4 than they are to one another.
  • Each aperture 8a aligns radially with the centre aperture 6a of the arcuate line of 3 apertures of a particular triangular shaped sector X.
  • the centre of the upper plate portion 2 may be slightly dished (not shown here) as is known in this type of burner.
  • This design of burner head 1 seeks to obviate any anomalous flow patterns or resistances to flow which could substantially affect the equal distribution of fuel to the individual apertures 6a,7a and 8a to thereby provide a more even temperature distribution and extend the burner life.
  • FIGURES 3 and 4 show a dual fuel burner assembly 100 for use in a furnace (not shown).
  • the burner assembly 100 may be utilised to burn a main, gaseous fuel and/or a secondary fuel in the form of oil or oil by-products produced by a processing plant incorporating a plurality of such burner assemblies. In this way the efficiency of the processing plant can be upgraded by the utilisation of the oil by-products.
  • the burner assembly 100 has a burner head B which may or may not be identical or similar to the burner head 1 shown in FIGURES 1 and 2 of this Specification.
  • the overall layout of the assembly 100 is generally known in the provision of a gas inlet to the burner head which is surrounded by a refractory quarl.
  • the assembly 100 has a gas inlet 103 leading to a central main fuel supply delivery tube or pipe 104 positioned centrally of the burner head B.
  • the main fuel supply passes up this pipe 104 to the gallery system of the burner head B and to the matrix of apertures as previously discussed in relation to FIGURES 1 and 2 of the drawings.
  • the assembly 100 further includes an air inlet 105, a wind box 106 with windbox top plate 107 and generally cylindrical refractory quarl 108 surrounding the burner head B.
  • an oil lance 109 is positioned centrally and coaxially with the gas supply pipe 104.
  • the oil burner tip 110 has a conical end which extends beyond the front plate portion f of the burner B and joins the oil burner station pipe 111 at the other end thereof. Provision may be made to adjust the position of the oil lance longitudinally of the supply pipe 104 in order to attempt to optimise flame profile above the burner head B and the oil lance will be received in a guide tube T (not shown in FIGURE 3 - see FIGURES 5 and 6) running along the length of gas pipe 104.
  • FIGURE 4 shows the location of the U.V detector mounting tube 112, view port 113 and igniter tube and cap 114, the operation of which should be readily apparent; 115 (see FIGURE 3) designates the purge interlock safety valve of the fuel oil lance 109.
  • a main gaseous fuel supply is delivered by the gas inlet 103 and flows upwardly (in use) through the gas pipe 104, through the annular space provided inbetween the guide tube T and wall of the pipe 104. Since the assembly 100 incorporates a fuel lance 109 running along the axis of the burner B the width of the pipe 104 is subsequently greater than required for single fuel burners because of the physical space taken up in the pipe 104 by the lance 109.
  • the gaseous fuel is delivered to the gallery system of the burner head B in a similar manner as in a single fuel burner and is delivered to the aperture matrix through the gallery system either in a generally known manner or in the manner as previously described in relation to FIGURES 1 and 2 of the Specification.
  • a secondary fuel oil is delivered from the station pipe 111 along the fuel lance 109 to the oil burner tip 110 which sprays oil above the upper burner plate f for ignition thereabove by an igniter which is of a form generally known per se.
  • the burner may run on a main gaseous fuel alone, or on the oil alone, or alternatively on a mixture of both.
  • the position of the oil lance 109 can be varied along the length of the gas supply pipe 104 in order to optimise the flame profile produced when the burner is operating on both fuels or on oil alone.
  • the burner head B in this instance is 22.4 cm diameter.
  • FIGURES 5 and 6 show more detailed views of a burner head 1' of a dual fuel supply type.
  • the burner head 1' has plate portions 2',3' showing the same matrix configuration of apertures as in FIGURE 1 of this Specification.
  • the apertures 6'a,7'a,8'a are formed from downwardly depending portions a' and upwardly depending portions b' which overlap one another to leave an annular gap g for fuel gas to enter the aperture 6a,7a,8a, rather than being provided with ports as in FIGURE 1. Either design may be used in the dual fuel application.
  • the central gas supply pipe 104 has a central guide tube T (not shown in FIGURES 3 and 4) for the fuel lance 109.
  • Item C represents a locating collar for the guide tube T and the pipe 104 is much wider than in prior art arrangements in order to allow the main gaseous fuel to enter the gallery G whilst also providing a housing for the oil lance 109.
  • the burner head aperture matrix 6a,7a,8a may be modified to that shown to take into account the wider pipe 104, for example by omission of the inner aperture ring 8a.
  • the dual fuel burner could be provided in a single gaseous fuel application in which case the open end of the tube T protruding from the burner head 1' would be blocked off.
  • the inlet pipe 104 and guide tube T comprises a subassembly and the burner head 1' is screwed to the pipe 104, after lock nut N is fitted with guide tube T entering locating collar C.
  • the burner head is screwed down until approximately 2 mm of guide tube protrudes from the upper plate when it is locked tightly with locking nut N.
  • a circular stabiliser plate Y is shown positioned on top of the upper plate portion 2.
  • the dual fuel burner assembly may be provided with any convenient burner head design and accordingly FIGURE 7 shows a burner head 1" corresponding more closely with prior art designs of the applicant.
  • the arrangement of combustion air apertures follows a general hexagonal shape which is known (and which burner head design has at least some of the disadvantages outlined at the beginning of the specification) but the apertures A (shown in chain dotted lines) which are present in a single fuel application are omitted in the dual fuel application.
  • the stabilising plate is hexagonal and weld lines are shown in this view.
  • the Applicant has carried out test analysis of a prior art burner head of hexagonal matrix pattern and a burner head in accordance with the present invention (circular matrix pattern) in order to illustrate the dramatic reduction in temperature of the plate portions near the boundary of the burner head.
  • FIGURES 8 to 16 This test analysis is shown in FIGURES 8 to 16 in which:
  • thermocouples 1 to 4 were located to measure the temperature occuring in different regions of the plate portions.
  • Thermocouple 1 was located in the centre of the burner head, thermocouples 2 and 3 in mid regions of the plate portions with thermocouple 3 being located at one of the inner spacers and thermocouple 4 located at the outer boundary region of the plate.
  • thermocouple 1 After some minutes the temperature registered by thermocouple 1 has reached the value of about 800°C (see upper part of trace 1), whilst the temperature of thermocouple 4 is also at about the same level i.e. the temperature at the centre of the burner is in the same order as the temperature at the boundary. This indicates that in the field the temperature of the boundary area that will be registered by thermocouple 4 would be very significantly higher (for example 150 to 200°C or more higher). The difference would be enough for the centre region to be emitting effectively a black heat radiation with the outer boundaries emitting a dull red radiation.
  • the temperature measured by thermocouple 2 is the lowest at about 660°C (see upper part of trace 2).
  • thermocouple 4 Comparing this data to the data given in FIGURE 15 shows that the temperature at the boundary regions (measured by thermocouple 4) has dramatically dropped to about 660°C (see upper part of trace 4) and there is also a slightly lower operating temperature at the middle of the burner which is measured by thermocouple 1. Thus the temperature at the boundary has been lowered to within about 30° of the temperature measured by thermocouple 2 and the temperature measured by thermocouple 2 has also been lowered by about 30° or so.
  • the overall operating temperature of the burner head has been lowered but most significantly the temperature has been reduced very significantly at the boundary regions so that in the field the temperature of the middle of the burner and of the boundary will be of the same order.
  • the centre of the burner may in some circumstances not be subject to an accelerated corrosion rate because of the speed of gas flow through to the apertures, whereas the corrosion rate is accelerated abnormally at elevated temperatures where there is a lingering presence of the gas i.e. particularly inbetween the hexagonal matrix configuration termination and the boundary of the burner (i.e. in the segmental regions of the hexagonal shape burner head).
  • thermocouple 2 Even under the test conditions the temperature of the boundary region is not substantially higher than any other region of the plate portion (as shown in FIGURE 12 the temperature of the boundary region is only approximately 30° higher than the region of the plate detected by thermocouple 2).
  • temperatures may range from 800-850°C in the central regions of the plate and at the periphery of the burner in areas of higher metal content.
  • temperatures result in the majority of the burner emitting a black heat radiation whilst dull red heat radiation is emitted from areas near the periphery, said areas being defined between the periphery of the burner and the aperture matrix (refer FIGURE 7). It is at temperatures of 700°C or above that the corrosion rate of the plate portions, subjected to that heat, is very significantly accelerated (particularly where gas flow is restricted) i.e. decarbonisation of the plate material may be dramatically increased.
  • Test experiments with burner heads of the present invention illustrate significant temperature variation between boundary regions of the plate and middle or central regions i.e. a very significant reduction in temperature of the boundary regions (reduction of approximately 150°C ). This indicates that the boundary temperature in the field will be substantially lower than with the prior art hexagonal burner configuration. This is due to improved gas and air cooling achieved by the burner in accordance with the present invention.
  • the matrix array adopted in accordance with the present invention effectively prevents any part of the burner plate reaching an elevated temperature which would result in excess corrosion when compared with any other area of the plate.
  • the burner of hexagonal matrix design and the circular matrix burner were tested under identical conditions on the same test furnace and conditions were maintained under very close tolerances throughout the duration of the tests.
  • gas in the burner head develops pressure as its velocity reduced.
  • gas glows outwards, radially, its velocity reduces due to an expanding flow area.
  • the flow through the gas ports is proportional to the pressure developed at the port. Hence to achieve even flow of gas per port, all ports must be at the same position relative to the source of supply. With a single ring of ports gas flow will be even from port to port.
  • the hexagonal matrix port spacing does not totally meet this criteria as port positions vary radially and the port spacing (gallery size) is not optimum for the sharing of gas between inner and outer ports.
  • the burner head in accordance with the present invention has many beneficial aspects on burner performance and application, a number of which are listed below:-

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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)
  • Materials For Medical Uses (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Nozzles For Spraying Of Liquid Fuel (AREA)
  • Pre-Mixing And Non-Premixing Gas Burner (AREA)
  • Combustion Of Fluid Fuel (AREA)
  • Transition And Organic Metals Composition Catalysts For Addition Polymerization (AREA)
  • Addition Polymer Or Copolymer, Post-Treatments, Or Chemical Modifications (AREA)

Claims (9)

  1. Brenner mit einem Kopf (1), welcher mit einer Anordnung oder Matrix von Verbrennungsluftöffnungen (6, 7, 8) versehen ist, wobei der Brennerkopf (1) einen Außenrand (4) sowie voneinander beabstandete Plattenabschnitte (2, 3) hat, welche einen Gang oder Durchgang (G) zum Zuführen von Brennstoff zu den Öffnungen (6, 7, 8) festlegen, dadurch gekennzeichet daß die Verbrennungsluftöffnungen (6, 7, 8) in äußeren mittleren und inneren Öffnungsringen (6, 7, 8) angeordnet sind, wobei der äußere Ring (6) dicht dem Außenrand (4) des Brennerkopfes (1) folgt und nahe an dem Rand (4) vorgesehen ist.
  2. Brenner nach Anspruch 1, dadurch gekennzeichnet, daß die Plattenabschnitte (2, 3) durch Abstandshalter (5) voneinander beabstandet sind und daß der Brenner derart eingerichtet ist, daß er nahe dem Randbereich (4) bei Betriebstemperaturen unterhalb von etwa 650 bis 700 °C oder unterhalb des Strahlungsniveaus der dunklen Rotglühhitze arbeitet.
  3. Brenner nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der äußere Öffnungsring (6) eine Reihe von Verbrennungsluftöffnungen (6a) aufweist, von denen wenigstens die Hälfte oder die Mehrheit von dem Rand (4) mit einer Entfernung beabstandet sind, die geringer als die gegenseitigen Abstände der Öffnungen oder gleich den gegenseitigen Abständen ist.
  4. Brenner nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Brennerkopf (1) kreisförmige Plattenabschnitte (23) hat und der äußere Öffnungsring (6) aus einem Kreis von Verbrenngsluftöffnungen (6a) besteht, welche eng voneinander beabstandet sind.
  5. Brenner nach Anspruch 4, dadurch gekennzeichnet, daß die Öffnungen (6a) in dem Kreisring (6) gleichmäßig voneinander beabstandet sind und/oder daß die Öffnungen (6a) kreisförmig sind und/oder daß jede Öffnung (6a) vom Rand (4) in einer Entfernung beabstandet ist, welche die dreifache Entfernung zwischen jeder Öffnung (6a) nicht übersteigt.
  6. Brenner nach Anspruch 5, dadurch gekennzeichnet, daß jede Öffnung (6a) vom Rand (4) in einer Entfernung beabstandet ist, die den zweifachen Abstand zwischen jeder Öffnung (6a) nicht übersteigt.
  7. Brenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß jeder der mittleren und inneren Öffnungsringe (7, 8) aus einer Reihe von Kreisöffnungen (7a, 8a) besteht und daß der innere Öffnungsring (8) eine Reihe von Kreisöffnungen (8a) aufweist, die konzentrisch mit dem äußeren Öffnungsring (6) derart angeordnet sind, daß jede Öffnung (8a) im Innenring (8) in radialer Richtung mit jeweiligen Öffnungen (6a) im Außenring (6) fluchtet, wobei die inneren (8a) und äußeren Ringöffnungen (6a) konzentrisch zu den kreisförmigen Plattenabschnitten (2, 3) des Brennerkopfes (1) ausgerichtet sind, und daß der mittlere Öffnungsring (7) vorzugsweise eine Reihe von Kreisöffnmgen (7a) aufweist, welche in Umfangsrichtung relativ zu dem äußeren und inneren Öffnungsring (6, 8) verschoben sind, und daß der Brenner vorzugsweise derart ausgebildet ist, daß die Öffnungskonfiguration zu einer Anordnung (6, 7, 8) von im wesentlichen dreieckigen Sektorbereichen führt die sich entlang dem Umfang der Plattenabschnitte (2, 3) erstrecken, und daß die Brennerplatten (2, 3) vorzugsweise im wesentlichen aus einem austenitischen Chromlegierungsstahl bestehen.
  8. Brenner (100) nach Anspruch 1, dadurch gekennzeichnet, daß der Brenner ein Zweistoffbrenner ist, bei welchem der Gang oder Durchgang für eine zu den Öffnungen (6'a, 6'b, 6'c) zu leitende Hauptbrennstoffzufuhr bestimmt ist, wobei die Anordnung derart gestaltet ist, daß der Brenner mit dem ersten oder Hauptbrennstoff, welcher entlang dem Gang oder Durchgang zu den Öffnungen (6'a, 6'b, 6'c) geleitet wird, laufen und alternativ dazu mit einem zweiten Brennstoff berieben werden kann, welcher mit durch die Öffnungen (6'a, 6'b, 6'c) zugeführter Verbrennungsluft vermischt ist, und welcher vorzugweise mit einem Gemisch aus dem ersten Hauptbrennstoff und dem Zweitbrennstoff berieben werden kann.
  9. Brennerelement {1, 2} umfassend zwei Blechkörper {1, 2}, die übereinanderliegend und voneinander beabstandet angeordnet sind und entlang ihrer Kanten {4, 5} abgedichtet sind, um dazwischen einen Gang {3} zum Zuführen von Brennstoff zu bilden, wobei die Blechkörper {1, 2} mehrere Paare von Verbrennungsluftöffnungen {6} aufweise, jedes Paar eine Öffnung {6} in jedem Blechkörper hat und das jede Öffnung {6} jedes Paars umgebende Blech sich in einen rohrförmigen Vorsprung {7, 8} in Richtung auf einen rohrförmigen Vorsprung {8, 7} und zusammenpassend mit diesem ausdehnt, welcher Vorsprung {8, 7} sich von dem die andere Öffnung {6} jedes Paars umgebenden Material ausdehnt, jeder rohrförmige Vorsprung {7, 8} jedes Paars mit dem anderen Vorsprung {8} jedes Paars zwecks Bildung mehrerer Brennstoffausströmöffnungen für den Brennstoffstrom von dem Zuführgang {3} zusammenwirkt dadurch gekennzeichnet, daß ein Ring aus Verbrennungsluftöffnungen {6} einem Außenrand des Brennerelements {1, 2} dicht folgt.
EP91912132A 1990-06-15 1991-06-17 Brenner Expired - Lifetime EP0487700B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
GB909013368A GB9013368D0 (en) 1990-06-15 1990-06-15 Improvements in or relating to burners
GB9013368 1990-06-15
PCT/GB1991/000973 WO1991019942A1 (en) 1990-06-15 1991-06-17 Improvements in or relating to burners

Publications (2)

Publication Number Publication Date
EP0487700A1 EP0487700A1 (de) 1992-06-03
EP0487700B1 true EP0487700B1 (de) 1996-11-27

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EP91912132A Expired - Lifetime EP0487700B1 (de) 1990-06-15 1991-06-17 Brenner

Country Status (7)

Country Link
EP (1) EP0487700B1 (de)
AT (1) ATE145717T1 (de)
CA (1) CA2064799C (de)
DE (1) DE69123329T2 (de)
DK (1) DK0487700T3 (de)
GB (2) GB9013368D0 (de)
WO (1) WO1991019942A1 (de)

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EP3364105A1 (de) 2017-02-16 2018-08-22 Vysoké ucení Technické v Brne Brennerkopf für niederkalorische brennstoffe

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FR2771798B1 (fr) 1997-12-02 1999-12-31 Air Liquide Bruleur oxy-combustible
DE102006010375B4 (de) * 2006-03-03 2008-01-17 J. Eberspächer GmbH & Co. KG Wandstruktur für einen Brenner
DE102006046053B4 (de) * 2006-09-28 2008-11-20 Green Vision Holding B.V. Nicht vorgemischter Brenner
DE102008006067B4 (de) 2008-01-25 2013-07-04 Viessmann Werke Gmbh & Co Kg Vorrichtung mit einem Brennerkopf und Verfahren zum Betätigen eines Brenners
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EP0487700A1 (de) 1992-06-03
DK0487700T3 (da) 1997-05-12
DE69123329D1 (en) 1997-01-09
GB2245055B (en) 1994-05-25
DE69123329T2 (de) 1997-07-10
WO1991019942A1 (en) 1991-12-26
GB9013368D0 (en) 1990-08-08
CA2064799A1 (en) 1991-12-16
GB2245055A (en) 1991-12-18
GB9113056D0 (en) 1991-08-07
ATE145717T1 (de) 1996-12-15
CA2064799C (en) 2000-01-18

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