EP0865590A1 - Atmospheric-type burner - Google Patents

Atmospheric-type burner

Info

Publication number
EP0865590A1
EP0865590A1 EP97941865A EP97941865A EP0865590A1 EP 0865590 A1 EP0865590 A1 EP 0865590A1 EP 97941865 A EP97941865 A EP 97941865A EP 97941865 A EP97941865 A EP 97941865A EP 0865590 A1 EP0865590 A1 EP 0865590A1
Authority
EP
European Patent Office
Prior art keywords
gas burner
burner according
gas
injector arrangement
flow channel
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
EP97941865A
Other languages
German (de)
French (fr)
Other versions
EP0865590B1 (en
Inventor
Juergen Stoschek
Marcus Bienzle
Michael Jantzer
Beate Maucher
Thomas-Eckart Frieling
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.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0865590A1 publication Critical patent/EP0865590A1/en
Application granted granted Critical
Publication of EP0865590B1 publication Critical patent/EP0865590B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F23D14/02—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
    • F23D14/10—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 elongated tubular burner head
    • 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
    • F23D14/02—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
    • F23D14/045—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 a plurality of burner bars assembled together, e.g. in a grid-like arrangement
    • 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
    • F23D14/10—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 elongated tubular burner head
    • F23D14/105—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 elongated tubular burner head with injector axis parallel to the burner head axis
    • 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
    • F23D14/72—Safety devices, e.g. operative in case of failure of gas supply
    • F23D14/78—Cooling burner parts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D2203/00—Gaseous fuel burners
    • F23D2203/10—Flame diffusing means
    • F23D2203/108—Flame diffusing means with stacked sheets or strips forming the outlets

Definitions

  • the invention relates to an atmospheric gas burner for heating devices, in particular water heaters, according to the preamble of the main claim.
  • Gas burners operating according to this principle are known (FR-PS 2 199 853), the burner plate of which is made up of ribs, the ribs being penetrated by a pipe system through which coolant flows in order to reduce the burner plate temperature and flame temperature.
  • the arrangement according to the invention with the features of the main claim has the advantage that it is possible to produce a compact atmospheric gas burner with a low overall height, which at the same time has low pollutant emissions, in particular low NOx, due to flame cooling and complete superstoichiometric premixing (air ratio ⁇ > 1) of the fuel gas with the combustion air and CO values.
  • air ratio ⁇ > 1 air ratio of the fuel gas with the combustion air and CO values.
  • the overall height of a heater provided with this burner can be kept low overall.
  • cylindrical flow channels An advantageous alternative to cylindrical flow channels consists in the formation of elongated flow channels, to which several nozzles are assigned in the inlet area.
  • the injector arrangement consists only of an elongated flow channel, to which all the nozzles for the gas supply are assigned in the inlet area. This further reduces flow resistance, sensitivity to positioning tolerances and manufacturing costs.
  • the injector arrangement, deflection area and mixture distributor can be produced in one piece. Due to the surface-enlarging fins connected to a cooling pipe system, the temperatures on the burner plate are limited to values that allow the use of an elastic seal between the mixture distributor and the burner plate.
  • the tube carrying the coolant is made of copper, while the fins of the burner plate are preferably made of stainless steel due to the higher thermal load.
  • the pronounced structuring of the burner plate can be achieved by providing one or more set back or shortened set between two non-set back sheet metal ribs.
  • FIG. 1 shows a longitudinal section of the gas burner according to the invention
  • FIG. 2 shows a section of the gas burner along the line AA in FIG. 1
  • FIG. 3 shows an enlarged section of the burner plate
  • 4 shows a plan view of the burner plate
  • FIGS. 5 and 6 show two further embodiments of injectors.
  • FIG. 1 shows a gas burner 10 with a gas supply device 14 which has a nozzle 12 and is spaced apart in the flow direction from a horizontally oriented injector arrangement 16 of the gas burner 10 in such a way that the nozzles 12 are each cylindrical at a distance
  • Flow channel 18 is opposite, the nozzles 12 being arranged at the level of the central axes of the flow channels 18.
  • the central axes of the flow channels 18 run essentially in a straight line, the flow cross section except for an extension 20 in the form of an inlet
  • Inlet area is substantially constant.
  • the ratio length to diameter of the flow channels 18 arranged in the injector 16 is ⁇ 4: 1, deviating from known injector arrangements for gas burners, in which the factor is 10 to 12.
  • a 90 ° deflection region 22 adjoining the injector arrangement 16 in the flow direction of the fuel gas / air mixture merges into a mixture distributor 24 which is widened to the funnel shape and at the outlet of which a burner plate 26 which is sealed off from the mixture distributor 24 is arranged.
  • the burner plate 26, which is fixed with fastening means 28 with respect to the mixture distributor 24, is constructed with fins or ribs 30, 31 (FIG. 3) of different lengths, which are connected to one another by a cooling pipe coil 32 and between them channels or gaps 34 for the passage of the fuel gas Limit the air mixture that is flammable on the side of the burner plate 26 facing the combustion chamber.
  • the ribs 30, 31 made of stainless steel are in good heat-conducting contact with the copper existing cooling tube coils 32 and are connected by this to form a rigid structural unit.
  • the width a of the column 34 is smaller than the so-called extinguishing distance, so that flames cannot strike back into the burner plate 26 or into the mixture distribution zone in front of it.
  • the burner plate 26 is designed so that two shorter ribs 31 are each between two longer ribs 30.
  • the arrangement is such that the edges 36 of the shorter ribs 31 on the combustion chamber side are set back relative to the edges 38 of the longer ribs 30.
  • the burner plate 26 is closed off at the side by end lamellae 44, 46 which protrude into the combustion chamber and prevent the flame arising during combustion from flashing over.
  • FIG. 4 shows a plan view of the burner plate 26 and shows the course of the cooling tube coils.
  • the gas burner 10 operates in the following way:
  • Fuel gas is injected into the flow channels 18 of the injector arrangement 16 via the gas nozzles 12, ambient air being entrained by the fuel gas flow.
  • the entire burner system nozzle pressure, injectors, deflection area, burner plate, etc.
  • the extension 20 designed as an inlet at the inlet of the flow channels 18 enables a low-friction entry of the combustion air into the Flow channel 18.
  • the fuel gas-air mixture that forms in the flow channels 18 strikes the deflection area 22, where the fuel gas is further mixed with the combustion air by swirling. Due to the funnel-shaped mixture distributor 24 which adjoins the deflection region 22, homogenization takes place in addition to the distribution of the mixture; in addition, the reduction in speed converts a high proportion of the dynamic pressure into the static pressure required for combustion.
  • the mixture reacts between or at the downstream edges 36, 38 of the fins 30, 31 with the formation of flames, heat of reaction from the flame roots via the fins 30, 31 to the water to be heated arrives in the coil 32.
  • the flame roots are cooled particularly well here because they also have side contact with the wall regions 42 of the ribs 30.
  • the thermal conductivity of the ribs 30, 31 is by design and / or
  • the material selection is matched to the burner output so that its surface temperature is set to, for example, 400 ° C.
  • FIGS. 5 and 6 show two further injector arrangements in which the cylindrical flow channels 18 are replaced by elongated flow channels, the injector arrangement according to FIG. 6 having only one elongated flow channel 58. In the latter case, all nozzles 12 are then assigned to the flow channel 58.
  • a particularly cost-effective production of the burner is achieved if the injector arrangement (16), deflection area (22) and mixture distributor (24) are made from a die-cast part.

Landscapes

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

Abstract

The present invention relates to an atmospheric-type burner intended for use in heaters such as a hot water apparatus, with a) a gas supply device (14) comprising a) a plurality of flow nozzles (12), b) an injector unit (16) including at least one discharge pipe (18) for the air-gas mixture, c) a reversing area (22) connecting, in the direction of flow, with the injector unit and opening out into a mixture distributor (24) which tapers out (24), and d) a mixture distributor (4) outlet associated with blades (830, 31) through a cooling pipe system (32) and defining between them channels or slots (34) for the passage of the air-gas mixture, which is ignited on a burner plate (36) turned to the combustion chamber. Thus, a burner can be built which is compact, of a small height and with a low NOx and Co emission rate.

Description

Atmosphärischer GasbrennerAtmospheric gas burner
Stand der TechnikState of the art
Die Erfindung geht aus von einem atmosphärischen Gasbrenner für Heizgeräte, insbesondere Wassererhitzer, nach der Gattung des Hauptanspruchs. Es sind nach diesem Prinzip arbeitende Gasbrenner bekannt (FR-PS 2 199 853), deren Brennerplatte aus Rippen aufgebaut ist, wobei zur Reduzierung der Brennerplattentemperatur und Flammentemperatur die Rippen von einem von Kühlmittel durchflossenen Rohrsystem durchsetzt sind.The invention relates to an atmospheric gas burner for heating devices, in particular water heaters, according to the preamble of the main claim. Gas burners operating according to this principle are known (FR-PS 2 199 853), the burner plate of which is made up of ribs, the ribs being penetrated by a pipe system through which coolant flows in order to reduce the burner plate temperature and flame temperature.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Anordnung mit den Merkmalen des Hauptanspruchs hat den Vorteil, daß die Herstellung eines kompakten atmosphärischen Gasbrenners mit geringer Bauhöhe möglich ist, der gleichzeitig durch Flammenkühlung und vollständige überstöchiometrische Vormischung (Luftzahl λ > 1) des Brenngases mit der Verbrennungsluft niedrige Schadstoffemissionen, insbesondere niedrige NOx und CO- Werte, aufweist. In dem Umlenkbereich des Gasbrenners findet durch die Verwirbelung des Brenngas-Luft-Gemisches eine zusätzliche Durchmischung statt, so daß die Strömungskanäle in der Injektoranordnung entsprechend kürzer gewählt werden können . Durch die in den Unteransprüchen aufgeführten Merkmale sind vorteilhafte Ausgestaltungen der Anordnung nach dem Hauptanspruch möglich.The arrangement according to the invention with the features of the main claim has the advantage that it is possible to produce a compact atmospheric gas burner with a low overall height, which at the same time has low pollutant emissions, in particular low NOx, due to flame cooling and complete superstoichiometric premixing (air ratio λ> 1) of the fuel gas with the combustion air and CO values. In the deflection area of the gas burner, an additional mixing takes place due to the swirling of the fuel gas-air mixture, so that the flow channels in the injector arrangement can be chosen to be correspondingly shorter. The features listed in the subclaims allow advantageous configurations of the arrangement according to the main claim.
Durch die im wesentlichen horizontale Anordnung der Injektoren kann die Bauhöhe eines mit diesem Brenner versehenen Heizgerätes insgesamt niedrig gehalten werden.Due to the essentially horizontal arrangement of the injectors, the overall height of a heater provided with this burner can be kept low overall.
Wegen des strömungstechnisch einfachen Aufbau der Injektoren ist eine druckgußtechnische Herstellung ohne Nachbearbeitung möglich. Durch die in der Injektoranordnung eingebrachten geradlinig verlaufenden Strömungskanäle mit konstantem Querschnitt werden die Strömungswiderstände minimiert .Because of the fluidically simple structure of the injectors, die-casting manufacture is possible without post-processing. The flow resistances are minimized by the straight-line flow channels with a constant cross-section that are incorporated in the injector arrangement.
Durch die kurzen mit einem großen Durchmesser versehenen Strömungskanäle besteht eine geringe Empfindlichkeit gegenüber Toleranzen zwischen der Positionierung Düse- Strömungskanal, was wiederum die Montagekosten senkt.Due to the short, large-diameter flow channels, there is little sensitivity to tolerances between the nozzle-flow channel positioning, which in turn lowers assembly costs.
Eine vorteilhafte Alternative zu zylinderförmig ausgebildeten Strömungskanälen besteht in der Ausbildung von langlochförmigen Strömungskanälen, denen im Einlaßbereich mehrere Düsen zugeordnet sind. Im Extremfall besteht die Injektoranordnung nur aus einem langlochförmig ausgebildeten Strömungskanal, dem im Einlaßbereich sämtliche Düsen für die Gaszufuhr zugeordnet sind. Damit werden Strömungswiderstände, Empfindlichkeiten gegenüber Positionierungstoleranzen und die Fertigungskosten weiter reduziert .An advantageous alternative to cylindrical flow channels consists in the formation of elongated flow channels, to which several nozzles are assigned in the inlet area. In the extreme case, the injector arrangement consists only of an elongated flow channel, to which all the nozzles for the gas supply are assigned in the inlet area. This further reduces flow resistance, sensitivity to positioning tolerances and manufacturing costs.
Für eine kostengünstige Herstellung des Brenners ist es besonders vorteilhaft, wenn Injektoranordnung, Umlenkbereich und Gemischverteiler einteilig hergestellt werden können. Aufgrund der die Oberfläche vergrößernden, mit einem Kühlrohrsystem verbundenen Rippen sind die Temperaturen an der Brennerplatte auf Werte begrenzt, die den Einsatz einer elastischen Dichtung zwischen Gemischverteiler und Brennerplatte ermöglichen.For cost-effective production of the burner, it is particularly advantageous if the injector arrangement, deflection area and mixture distributor can be produced in one piece. Due to the surface-enlarging fins connected to a cooling pipe system, the temperatures on the burner plate are limited to values that allow the use of an elastic seal between the mixture distributor and the burner plate.
Eine gute Wärmeableitung wird erreicht, wenn das Kühlmittel führende Rohr aus Kupfer besteht, während die Rippen der Brennerplatte aufgrund der höheren Wärmebelastung vorzugsweise aus Edelstahl gebildet sind.Good heat dissipation is achieved if the tube carrying the coolant is made of copper, while the fins of the burner plate are preferably made of stainless steel due to the higher thermal load.
Bei der aus Rippen aufgebauten Brennerplatte hat es sich als vorteilhaft erwiesen, wenn die brennraumseitigen Ränder von bestimmten Rippen gegenüber den brennraumseitigen Rändern der anderen Rippen zurückversetzt sind. Dadurch wird eine besonders ausgeprägte Strukturierung der brennraumseitigen Wand der Brennerplatte erreicht, bei welcher die Flammenwurzeln über größere Seitenbereiche an benachbarten Blechrippen anliegen und daher besonders gut gekühlt werden.In the burner plate constructed from ribs, it has proven to be advantageous if the edges of certain ribs on the combustion chamber side are set back relative to the edges of the other ribs on the combustion chamber side. As a result, a particularly pronounced structuring of the wall of the burner plate on the combustion chamber side is achieved, in which the flame roots rest against adjacent sheet metal fins over larger side areas and are therefore cooled particularly well.
Die ausgeprägte Strukturierung der Brennerplatte kann dadurch erreicht werden, daß jeweils zwischen zwei nicht zurückversetzten Blechrippen eine oder mehrere zurückversetzte beziehungsweise gekürzte Rippe vorgesehen ist.The pronounced structuring of the burner plate can be achieved by providing one or more set back or shortened set between two non-set back sheet metal ribs.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der folgenden Beschreibung unter Angabe weiterer Vorteile näher erläutert. Es zeigen Figur 1 einen Längsschnitt des erfindungsgemäßen Gasbrenners, Figur 2 einen Schnitt des Gasbrenners nach der Linie A-A in Figur 1, Fig. 3 einen vergrößerten Ausschnitt der Brennerplatte, Fig. 4 eine Draufsicht auf die Brennerplatte und die Figuren 5 und 6 zwei weitere Ausführungsformen von Injektoren.An embodiment of the invention is shown in the drawing and explained in more detail in the following description with further advantages. 1 shows a longitudinal section of the gas burner according to the invention, FIG. 2 shows a section of the gas burner along the line AA in FIG. 1, FIG. 3 shows an enlarged section of the burner plate, 4 shows a plan view of the burner plate and FIGS. 5 and 6 show two further embodiments of injectors.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Figur 1 zeigt einen Gasbrenner 10, mit einer eine Düse 12 aufweisenden Gaszufuhreinrichtung 14, die gegenüber einer horizontal ausgerichteten Injektoranordnung 16 des Gasbrenners 10 in Strömungsrichtung so beabstandet ist, daß den Düsen 12 jeweils mit Abstand ein zylinderförmigerFIG. 1 shows a gas burner 10 with a gas supply device 14 which has a nozzle 12 and is spaced apart in the flow direction from a horizontally oriented injector arrangement 16 of the gas burner 10 in such a way that the nozzles 12 are each cylindrical at a distance
Strömungskanal 18 gegenüberliegt, wobei die Düsen 12 auf Höhe der Mittelachsen der Strömungskanäle 18 angeordnet sind. Die Mittelachsen der Strömungskanäle 18 verlaufen im wesentlichen geradlinig, wobei der Strömungsquerschnitt bis auf eine als Einlauf gestaltete Erweiterung 20 imFlow channel 18 is opposite, the nozzles 12 being arranged at the level of the central axes of the flow channels 18. The central axes of the flow channels 18 run essentially in a straight line, the flow cross section except for an extension 20 in the form of an inlet
Einlaßbereich im wesentlichen konstant ist. Das Verhältnis Länge zu Durchmesser der im Injektor 16 angeordneten Strömungskanäle 18 beträgt < 4:1, abweichend von bekannten Injektoranordnungen für Gasbrenner, bei denen der Faktor 10 bis 12 beträgt. Ein sich in Strömungsrichtung des Brenngas- Luft-Gemisches an die Injektoranordnung 16 anschließender 90° -Umlenkbereich 22 geht in einen nach einer Seite trichterförmig erweiterten Gemischverteiler 24 über, an dessen Auslaß eine gegenüber dem Gemischverteiler 24 abgedichtete Brennerplatte 26 angeordnet ist.Inlet area is substantially constant. The ratio length to diameter of the flow channels 18 arranged in the injector 16 is <4: 1, deviating from known injector arrangements for gas burners, in which the factor is 10 to 12. A 90 ° deflection region 22 adjoining the injector arrangement 16 in the flow direction of the fuel gas / air mixture merges into a mixture distributor 24 which is widened to the funnel shape and at the outlet of which a burner plate 26 which is sealed off from the mixture distributor 24 is arranged.
Die mit Befestigungsmitteln 28 gegenüber dem Gemischverteiler 24 fixierte Brennerplatte 26 ist mit unterschiedlich langen Lamellen bzw. Rippen 30, 31 (Fig. 3) aufgebaut, welche durch eine Kühlröhrschlänge 32 miteinander verbunden sind und zwischen sich Kanäle bzw. Spalte 34 für den Durchtritt des Brenngas-Luft-Gemisches begrenzen, das auf der dem Brennraum zugewandten Seite der Brennerplatte 26 entzündbar ist. Die aus Edelstahl bestehenden Rippen 30, 31 stehen in gut wärmeleitendem Kontakt mit der aus Kupfer bestehenden Kühlröhrschlänge 32 und sind durch diese zu einer starren Baueinheit verbunden. Die Breite a der Spalte 34 ist kleiner als der sogenannte Löschabstand bemessen, so daß Flammen nicht in die Brennerplatte 26 bzw. in die davor liegende Gemischverteilerzone zurückschlagen können.The burner plate 26, which is fixed with fastening means 28 with respect to the mixture distributor 24, is constructed with fins or ribs 30, 31 (FIG. 3) of different lengths, which are connected to one another by a cooling pipe coil 32 and between them channels or gaps 34 for the passage of the fuel gas Limit the air mixture that is flammable on the side of the burner plate 26 facing the combustion chamber. The ribs 30, 31 made of stainless steel are in good heat-conducting contact with the copper existing cooling tube coils 32 and are connected by this to form a rigid structural unit. The width a of the column 34 is smaller than the so-called extinguishing distance, so that flames cannot strike back into the burner plate 26 or into the mixture distribution zone in front of it.
Wie Fig. 3 zeigt, ist die Brennerplatte 26 so gestaltet, daß zwei kürzere Rippen 31 jeweils zwischen zwei längeren Rippen 30 stehen. Dabei ist die Anordnung so getroffen, daß die brennraumseitigen Ränder 36 der kürzeren Rippen 31 gegenüber den Rändern 38 der längeren Rippen 30 zurückgesetzt sind. Dadurch ergibt sich an der brennraumseitigen Wand der Brennerplatte 26 eine stark gestufte Oberflachenstrukturierung mit breiten Zwischenräumen 40, die seitlich durch Wandbereiche 42 der längeren Rippen 30 begrenzt sind. Die Brennerplatte 26 wird seitlich durch in den Brennraum ragende Endlamellen 44, 46 abgeschlossen, die ein Überschlagen der bei der Verbrennung entstehenden Flamme verhindern. Figur 4 zeigt eine Draufsicht auf die Brennerplatte 26 und läßt den Verlauf der Kühlröhrschlänge erkennen.3, the burner plate 26 is designed so that two shorter ribs 31 are each between two longer ribs 30. The arrangement is such that the edges 36 of the shorter ribs 31 on the combustion chamber side are set back relative to the edges 38 of the longer ribs 30. This results in a strongly stepped surface structuring on the combustion chamber side wall of the burner plate 26 with wide gaps 40 which are laterally delimited by wall regions 42 of the longer ribs 30. The burner plate 26 is closed off at the side by end lamellae 44, 46 which protrude into the combustion chamber and prevent the flame arising during combustion from flashing over. FIG. 4 shows a plan view of the burner plate 26 and shows the course of the cooling tube coils.
Der Gasbrenner 10 arbeitet auf folgende Art und Weise:The gas burner 10 operates in the following way:
Über die Gasdüsen 12 wird Brenngas in die Strömungskanäle 18 der Injektoranordnung 16 eingedüst, wobei durch den Brenngasstrom Umgebungsluft mitgerissen wird. Das gesamte Brennersystem (Düsendruck, Injektoren, Umlenkbereich, Brennerplatte etc.) ist so ausgelegt, daß die für eine Verbrennung mit Luftüberschuß (λ > 1) notwendige Verbrennungsluft bereits vollständig mit der Primärluftansaugung zur Verfügung gestellt wird (sogenanntes Vormischbrennerprinzip) . Die als Einlauf gestaltete Erweiterung 20 am Einlaß der Strömungskanäle 18 ermöglicht einen reibungsarmen Eintritt der Verbrennungsluft in den Strömungskanal 18. Das sich in den Strömungskanälen 18 bildende Brenngas-Luft-Gemisch trifft auf den Umlenkbereich 22, wo es durch Verwirbelung zu einer weiteren Durchmischung des Brenngases mit der Verbrennungsluft kommt. Durch den sich an den Umlenkbereich 22 anschließenden trichterförmig erweiternden Gemischverteiler 24 findet neben der Verteilung des Gemisches eine Homogenisierung statt; darüberhinaus wird durch die Geschwindigkeitsreduzierung ein hoher Anteil des dynamischen Drucks in für die Verbrennung notwendigen statischen Druck umgewandelt.Fuel gas is injected into the flow channels 18 of the injector arrangement 16 via the gas nozzles 12, ambient air being entrained by the fuel gas flow. The entire burner system (nozzle pressure, injectors, deflection area, burner plate, etc.) is designed in such a way that the combustion air required for combustion with excess air (λ> 1) is already completely provided with the primary air intake (so-called premix burner principle). The extension 20 designed as an inlet at the inlet of the flow channels 18 enables a low-friction entry of the combustion air into the Flow channel 18. The fuel gas-air mixture that forms in the flow channels 18 strikes the deflection area 22, where the fuel gas is further mixed with the combustion air by swirling. Due to the funnel-shaped mixture distributor 24 which adjoins the deflection region 22, homogenization takes place in addition to the distribution of the mixture; in addition, the reduction in speed converts a high proportion of the dynamic pressure into the static pressure required for combustion.
Nachdem das Brenngas-Luft-Gemisch die Brennerplatte 26 erreicht hat, reagiert das Gemisch zwischen bzw. an den stromab liegenden Rändern 36, 38 der Rippen 30, 31 unter Flammenbildung, wobei Reaktionswärme aus den Flammenwurzeln über die Rippen 30, 31 an das aufzuheizende Wasser in der Rohrschlange 32 gelangt. Die Flammenwurzeln werden hierbei besonders gut gekühlt, weil sie auch Seitenberührung mit den Wandbereichen 42 der Rippen 30 haben. Die Wärmeleitfähigkeit der Rippen 30, 31 ist durch Bemessung und/oderAfter the fuel gas-air mixture has reached the burner plate 26, the mixture reacts between or at the downstream edges 36, 38 of the fins 30, 31 with the formation of flames, heat of reaction from the flame roots via the fins 30, 31 to the water to be heated arrives in the coil 32. The flame roots are cooled particularly well here because they also have side contact with the wall regions 42 of the ribs 30. The thermal conductivity of the ribs 30, 31 is by design and / or
Werkstoffauswahl so auf die Brennerleistung abgestimmt, daß sich ihre Oberflächentemperatur auf zum Beispiel 400° C einstellt .The material selection is matched to the burner output so that its surface temperature is set to, for example, 400 ° C.
Die Figuren 5 und 6 zeigen zwei weitere Injektoranordnungen, bei denen die zylinderförmigen Strömungskanäle 18 durch langlochförmige Strömungskanäle ersetzt sind, wobei die Injektoranordnung nach Fig. 6 nur einen langlochförmigen Strömungskanal 58 aufweist. Im letztgenannten Fall sind dann alle Düsen 12 dem Strömungskanal 58 zugeordnet.FIGS. 5 and 6 show two further injector arrangements in which the cylindrical flow channels 18 are replaced by elongated flow channels, the injector arrangement according to FIG. 6 having only one elongated flow channel 58. In the latter case, all nozzles 12 are then assigned to the flow channel 58.
Eine besonders kostengünstige Herstellung des Brenners wird erreicht, wenn Injektoranordnung (16) , Umlenkbereich (22) und Gemischverteiler (24) aus einem Druckgußteil gefertigt werden. A particularly cost-effective production of the burner is achieved if the injector arrangement (16), deflection area (22) and mixture distributor (24) are made from a die-cast part.

Claims

Ansprüche Expectations
1. Atmosphärischer Gasbrenner für Heizgeräte, insbesondere Wassererhitzer, mit a) einer mehrere Düsen (12) aufweisenden Gaszufuhreinrichtung (14) , b) einer Injektoranordnung (16) mit mindestens einem Strömungskanal (18) für das Brenngas-Luft-Gemisch, c) einem sich in Strömungsrichtung an die Injektoranordnung (16) anschließenden Umlenkbereich (22) , der in einen sich erweiternden Gemischverteiler (24) übergeht, und mit d) einer am Auslaß des Gemischverteilers (24) angeordneten Brennerplatte (26), die mit Rippen (30, 31) aufgebaut ist, welche durch ein Kühlrohrsystem (32) miteinander verbunden sind und zwischen sich Kanäle bzw. Spalte (34) für den1. Atmospheric gas burner for heating devices, in particular water heaters, with a) a gas supply device (14) having a plurality of nozzles (12), b) an injector arrangement (16) with at least one flow channel (18) for the fuel gas / air mixture, c) one deflecting area (22) adjoining the injector arrangement (16) in the direction of flow, which merges into an expanding mixture distributor (24), and with d) a burner plate (26) arranged at the outlet of the mixture distributor (24), which has ribs (30, 31) is constructed, which are connected to one another by a cooling pipe system (32) and between them channels or gaps (34) for the
Durchtritt des Brenngas-Luft-Gemisches begrenzen, das auf einer dem Brennraum zugewandten Seite der Brennerplatte (26) entzündbar ist.Limit the passage of the fuel gas-air mixture, which is flammable on a side of the burner plate (26) facing the combustion chamber.
2. Gasbrenner nach Anspruch 1, dadurch gekennzeichnet, daß die Injektoranordnung (16) im wesentlichen horizontal ausgerichtet ist.2. Gas burner according to claim 1, characterized in that the injector arrangement (16) is aligned substantially horizontally.
3. Gasbrenner nach Anspruch 1 oder 2 , dadurch gekennzeichnet, daß der in der Injektoranordnung (16) ausgebildete Strömungskanal (18) einen im wesentlichen konstanten Strömungsquerschnitt aufweist, wobei die Mittelachse des Strömungskanals (18) im wesentlichen geradlinig verläuft. 3. Gas burner according to claim 1 or 2, characterized in that the flow channel (18) formed in the injector arrangement (16) has a substantially constant flow cross-section, the central axis of the flow channel (18) being essentially rectilinear.
4. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß das Verhältnis Länge zu Höhe des Strömungskanals (18) < 4:1 beträgt.4. Gas burner according to one of the preceding claims, characterized in that the length to height ratio of the flow channel (18) is <4: 1.
5. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Injektoranordnung (16) mehrere zylinderförmig ausgebildete Strömungskanäle (18) aufweist, denen im Einlaßbereich jeweils eine Düse (12) für die Gaszufuhr zugeordnet ist, wobei das Verhältnis Durchmesser - Strömungskanal (18) zu Außendurchmesser - Düse (12) mindestens 2:1 beträgt.5. Gas burner according to one of the preceding claims, characterized in that the injector arrangement (16) has a plurality of cylindrical flow channels (18), each of which is assigned a nozzle (12) for the gas supply in the inlet region, the ratio of diameter to flow channel (18 ) to the outside diameter - nozzle (12) is at least 2: 1.
6. Gasbrenner nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Injektoranordnung (16) mehrere langlochförmig ausgebildete Strömungskanäle (18) aufweist, wobei einem Strömungskanal (18) im Einlaßbereich mehrere Düsen (12) zugeordnet sind.6. Gas burner according to one of claims 1 to 3, characterized in that the injector arrangement (16) has a plurality of elongated hole-shaped flow channels (18), wherein a flow channel (18) in the inlet area are assigned a plurality of nozzles (12).
7. Gasbrenner nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die gesamte Injektoranordnung (16) nur einen langlochförmig ausgebildeten Strömungskanal (18) aufweist, dem im Einlaßbereich sämtliche Düsen (12) für die Gaszufuhr zugeordnet sind.7. Gas burner according to one of claims 1 to 3, characterized in that the entire injector arrangement (16) has only one slot-shaped flow channel (18) which in the inlet area all nozzles (12) for the gas supply are assigned.
8. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß Injektoranordnung (16) , Umlenkbereich (22) und Gemischverteiler (24) zu einer Baueinheit zusammengefaßt sind.8. Gas burner according to one of the preceding claims, characterized in that the injector arrangement (16), deflection area (22) and mixture distributor (24) are combined to form a structural unit.
9. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Brennerplatte (26) gegenüber dem Gemischverteiler (24) durch eine elastische Dichtung abgedichtet ist. 9. Gas burner according to one of the preceding claims, characterized in that the burner plate (26) is sealed with respect to the mixture distributor (24) by an elastic seal.
10. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die Rippen (30, 31) der Brennerplatte (26) aus Edelstahl bestehen, während das Kühlmittel führende Rohr (32) aus Kupfer besteht.10. Gas burner according to one of the preceding claims, characterized in that the ribs (30, 31) of the burner plate (26) consist of stainless steel, while the coolant pipe (32) consists of copper.
11. Gasbrenner nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß die brennraumseitigen Ränder (36) von bestimmten Blechrippen (31) gegenüber den brennraumseitigen Rändern (38) der anderen Blechrippen (30) zurückversetzt sind.11. Gas burner according to one of the preceding claims, characterized in that the combustion chamber side edges (36) of certain sheet metal ribs (31) with respect to the combustion chamber side edges (38) of the other sheet metal ribs (30) are set back.
12. Gasbrenner nach Anspruch 11, dadurch gekennzeichnet, daß jeweils zwischen zwei nicht zurückversetzten Blechrippen (30) zwei kürzere Blechrippen (31) nebeneinanderliegend angeordnet sind. 12. Gas burner according to claim 11, characterized in that between two non-recessed sheet metal ribs (30) two shorter sheet metal ribs (31) are arranged side by side.
EP97941865A 1996-10-04 1997-09-04 Atmospheric-type burner Expired - Lifetime EP0865590B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19641040 1996-10-04
DE19641040A DE19641040A1 (en) 1996-10-04 1996-10-04 Atmospheric gas burner
PCT/DE1997/001938 WO1998015781A1 (en) 1996-10-04 1997-09-04 Atmospheric-type burner

Publications (2)

Publication Number Publication Date
EP0865590A1 true EP0865590A1 (en) 1998-09-23
EP0865590B1 EP0865590B1 (en) 2002-05-22

Family

ID=7807918

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97941865A Expired - Lifetime EP0865590B1 (en) 1996-10-04 1997-09-04 Atmospheric-type burner

Country Status (6)

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EP (1) EP0865590B1 (en)
JP (1) JP2000502436A (en)
KR (1) KR19990071702A (en)
DE (2) DE19641040A1 (en)
ES (1) ES2178002T3 (en)
WO (1) WO1998015781A1 (en)

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DE19954811A1 (en) * 1999-11-13 2001-05-17 Bosch Gmbh Robert Lamella burner
DE10008549B4 (en) * 2000-02-24 2004-03-25 Robert Bosch Gmbh Burner head with metal plate and pipe sections for a coolant
DE20109170U1 (en) * 2001-06-05 2002-10-10 Viessmann Werke GmbH & Co., 35108 Allendorf Atmospheric gas burner
DE10213132B4 (en) * 2002-03-23 2005-06-02 Robert Bosch Gmbh gas burner
DE202007018472U1 (en) 2007-03-31 2008-08-21 Robert Bosch Gmbh Premixing gas burner
TWI611146B (en) * 2016-09-26 2018-01-11 Grand Mate Co Ltd burner

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NL6508630A (en) * 1965-07-05 1967-01-06
US3897198A (en) * 1972-04-17 1975-07-29 Radiation Ltd Gaseous fuel burners
DE8120009U1 (en) * 1981-07-09 1982-12-30 Robert Bosch Gmbh, 7000 Stuttgart ATMOSPHERIC ALLGAS BURNER, IN PARTICULAR FOR HOUSEHOLD APPLIANCES
NL8900030A (en) * 1989-01-06 1990-08-01 Remeha Fabrieken Bv NOX-POOR ATMOSPHERIC GAS BURNER.
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Also Published As

Publication number Publication date
KR19990071702A (en) 1999-09-27
DE19641040A1 (en) 1998-04-23
JP2000502436A (en) 2000-02-29
WO1998015781A1 (en) 1998-04-16
ES2178002T3 (en) 2002-12-16
DE59707327D1 (en) 2002-06-27
EP0865590B1 (en) 2002-05-22

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