EP0663056A1 - Mixing and heat-exchange system for condensing gas boilers - Google Patents

Mixing and heat-exchange system for condensing gas boilers

Info

Publication number
EP0663056A1
EP0663056A1 EP93921777A EP93921777A EP0663056A1 EP 0663056 A1 EP0663056 A1 EP 0663056A1 EP 93921777 A EP93921777 A EP 93921777A EP 93921777 A EP93921777 A EP 93921777A EP 0663056 A1 EP0663056 A1 EP 0663056A1
Authority
EP
European Patent Office
Prior art keywords
wall
mixing
mixer
supply
sector
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.)
Ceased
Application number
EP93921777A
Other languages
German (de)
French (fr)
Inventor
Hynek Mikusek
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.)
Individual
Original Assignee
Individual
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 Individual filed Critical Individual
Publication of EP0663056A1 publication Critical patent/EP0663056A1/en
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H9/00—Details
    • F24H9/0084—Combustion air preheating
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24H—FLUID HEATERS, e.g. WATER OR AIR HEATERS, HAVING HEAT-GENERATING MEANS, e.g. HEAT PUMPS, IN GENERAL
    • F24H8/00—Fluid heaters characterised by means for extracting latent heat from flue gases by means of condensation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02B—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO BUILDINGS, e.g. HOUSING, HOUSE APPLIANCES OR RELATED END-USER APPLICATIONS
    • Y02B30/00—Energy efficient heating, ventilation or air conditioning [HVAC]

Definitions

  • the invention is in the field of heating systems and is a device which heats up for water and other media and which consists of supply and other connection fittings, consisting of the combustion chamber with a flat gas burner and with mixing chamber components, one above the other. if the mixing chamber has a mixer in line with the peripheral chamber. A heat exchanger for cooling the combustion products and simultaneously reducing the flow of the combustion air is connected to the lower part of the combustion chamber.
  • the condensation units of this type used in particular for low-volume room heating, and a surface burner in various mold lead-throughs and room arrangements, have relatively high effectiveness and small pollutant emissions from the combustion process run, especially NO ⁇ , CO ⁇ and SO ⁇ ⁇ are realistic.
  • One of the conditions for satisfactory surface burner work is complete homogenization of the fuel mixture and uniform, continuous distribution of the heating mixture to the entire burner active area. After the combustion process is complete, hot combustion products pass through a combustion chamber, where water vapor condensation and heat transfer between the surfaces pass through the heat exchanger. Then cooling combustion products are leading into aggregate space, e.g. B. in chimney.
  • the solutions primarily include a mixing chamber in the form of a truncated pyramid, the subsurface of which is created by a surface gas burner. Air entering this mixing chamber is supplied with the fan, which is located vertically on the upper ground plane. There is a lamella in the mixing chamber in the vicinity of the inlet opening for air; it is parallel to the burner surface and introduces the gas that enters it into a turbulent barrel. The gas device to the opposite position tion to the air inlet.
  • Plain, large-area burner of ceramic with a flame is also suitable as a combustion chamber wall part if the combustion chamber is in a tabular cuboid shape;
  • the heating mixture is homogenized in the fan chamber and leads into the combustion chamber through an opening in the top level from the fan.
  • Another known construction which uses heating mixture homogenization up to the area of the combustion chamber with the cylindrical burners of refractory steel; on the burner surface the micro nozzles for the heating mixture passage are made and the combustion chamber also has a cylindrical shape, its inner surface creating a spiral pipe with heated media.
  • the above-mentioned deficiency eliminates the advantages of the mixing and heat exchange system of the condensing gas boiler according to the invention.
  • the essential part is that it consists of supply fittings, connecting fittings with the control, regulation and indication part, from the mixer with the mixing chamber and there is a surface gas burner.
  • the surface gas burner creates part of the surface of the combustion chamber part;
  • the heat exchanger is connected to the lower part of the combustion chamber, in which the combustion products are cooled and at the same time pre-heated by the combustion air.
  • the mixer is manufactured as a Venturi tube with an axial feed line for compressed (e.g. with the help of the fan) combustion air.
  • the peripheral chamber After the outer surface of the mixer, the peripheral chamber, with its inner surfaces, is profiled as a hollow rotary body and provides radial gas supply.
  • the interior of the mixer and the interior of the circumference are close to one another in the vicinity of the critical diameter with circumferential nozzles that pierce.
  • the circumferential nozzles are a minimum of three and symmetrically piercing all around.
  • a further feature of the invention is that the longitudinal axis of the peripheral nozzle shoots at an angle 15 * perpendicular to the longitudinal axis of the mixer after the air flow device, and furthermore the longitudinal axis of the peripheral nozzle with the straight line perpendicular to the longitudinal axis of the mixer and passing through the peripheral nozzle emitter Decided angles up to 13 * to 17 * after gas flow setup.
  • the mixing chamber inlet (eg with the connection fitting) is connected to the mixer outlet when the mixing chamber is stands from the passage sector and from the supply sector.
  • the supply sector is least comprised of a partial supply wall and at the same time it is approximately perpendicular to the horizontal plane of the supply sector and also to the direction of entry of the heating mixture.
  • At least the first one made of supply part walls is produced as a screen, if it can also have its flat figure with a total air tube surface of about 28%.
  • the supply line wall is the least coincident in height from the front wall of the mixing chamber with the heating mixture inlet and / or from the adjacent supply wall and / or from the section wall by horizontal length.
  • the number of supply walls in the mixing chamber is defined as the width / length of the surface gas burner ratio. Only one partial wall of the supply line, when this ratio is greater than 0.4, becomes quite sufficient; meanwhile the ratio is up to 0.4 to 0.17, the two additional walls will be sufficient.
  • the following advantage according to this invention can be expected if the plane of the compartment wall and the horizontal plane of the feed chamber form an angle 80 * or the smallest.
  • the penetration sector is made as an elongated prism with the vertical cross section of irregular polygons and the bottom of this penetration sector is formed by the surface burner, which also forms part of the upper surface of the combustion chamber.
  • the heat exchanger is made as a two-stage and forms it minimally a finned tube lying in the slack line, with the first end in the bottom of the combustion chamber and the second end of the finned tube in the base of the ascending channel with the siphon and the cascade of profiled fins.
  • the descending duct is created with a system of profiling ribs between at least one of the ascending duct and at least one outer peripheral wall of the combustion chamber.
  • the mouth of the descending end channel is linked to the axial feed line of the mixer (directly or indirectly - for example by mediating the connecting channel with a fan and ending with the connecting fitting).
  • condensation gas boiler there is above all improved operational safety, which is achieved by using the prescribed mixer with the peripheral chamber for heating mixture design, because this avoids the structural mixture formation in the interior of the unit cabinet, for example when the combustion system is switched off when the combustion system is switched off automatically Mastery of aggregates, especially combined with gas monitoring.
  • the entire gas residue from the interior of the boiler is sucked out through spontaneously ended diffusion.
  • Entire cabinet interior is best airtight and gas or heating mixture escaping through any leaks in the facility are back-venting back into the descending channel, from where they continued with fresh air in the mixer. Residual gas sealing also makes the cupboard heat escape lower, but this heat energy is intended for pre-heating the combustion air.
  • the mixing chamber solution allows substantial lowering of its height, which lowers demands on additional space and unburned heating mixture requirements.
  • Two-stage heat exchanger according to this invention at a heat turn of 70/50 * C makes maximum combustion product heat 55 * C possible.
  • FIG. 1 shows a condensation gas boiler diagram in a horizontal cross section without control, regulation and indication parts
  • 2 shows the mixer with the circumferential chamber in elevation with a horizontal section
  • Fig. 3 shows a transverse section through the mixer of Fig. 2
  • 4 vertical cross section through the lower combustion chamber part with the heat exchanger
  • FIG. 5 vertical cross section through the mixing chamber with the surface gas burner, and which have used the following reference numerals:
  • connection fitting 14 finned tube 3 circumferential chamber 15 ascent channel
  • the mixer JL is produced as a Venturi tube and is provided with an axial combustion air supply line with the connection fitting 2_.
  • the inner chamber is provided with its inner surfaces as profiling bodies of revolution and with a radial gas supply line.
  • the critical mixer inner diameter In the vicinity of the critical mixer inner diameter are three circumferential nozzles which penetrate symmetrically and all around, the length axes of which, with the flat axis of the mixer 1_ perpendicular to the length axis of the mixer, make an angle of 15 * according to the air flow direction.
  • Angle 15 * after the gas flow device is also between the longitudinal axes of all circumferential nozzles 5_ and between straight lines perpendicular to the longitudinal axes and passing through the circumferential nozzle centers.
  • the mixing chamber 6_ consists of the passage sector 1_ and the feed sector jB, which are separating with the department wall 100. Resolve the department wall 100 and horizontal centric plane of the supply sector angle 80 * and the department wall 100 as a sieve with a total air tube area generated 28%.
  • In the Supply sector 7. Are also two partial supply walls ⁇ 0 containing, perpendicular to the horizontal plane of the supply sector T_ and leading to the inlet device of the heating mixture.
  • the first partial feed wall _6 is remote from the adjacent partial feed wall 10 and from the end forest of the mixing chamber 6_ with the heating mixture inlet, and the second partial feed wall 1__ from the partial compartment wall 100 by the same horizontal length, which is its height.
  • the flat gas burner jLl. forms the bottom of the penetration sector J3 and a surface part of the combustion chamber part Y2__.
  • the combustion chamber 12 is basically tapered and narrowed and four rows of heated tubes 1_3 are included.
  • the divided combustion chamber base there is a row of slanting finned tubes 1_, if each of them is in the combustion chamber space with the first end and with the second end in the descending channel L5 with the siphon 1 ⁇ 9 and the inner cascade of profiled ribs lj ⁇ is out.
  • the descending duct L7 is created with a system of parallel profiling ribs ____.
  • the opening of the descending duct ⁇ 1_ to the axial feed line of the mixer 1_ is linked by means of the connecting duct ⁇ 2 to the electric fan 21_ and to the connecting fitting.
  • the upper mouth of the ascending channel _15 is closed for the discharge of combustion products.
  • Gas is fed into the space of the containment chamber 3_ into the outlet tube with the gas shut-off valve 2Q_; Combustion air for heating mixture formation with the fan 21 is operating.
  • Atmospheric air is exhausting through the inlet opening in cabinet 23, of which it enters descending channel 1 ⁇ 7.
  • this air is preheated and continues around heat exchange surfaces of finned tubes 1 and through the connecting duct 22 to the fan 21.
  • the air travels through the mixer 1, where it mixes with gas, diffusing through peripheral nozzles 5 ⁇ mediation with a screw-shaped barrel in the vicinity of the mixer interior surfaces. Resulting heating mixture is in the fitting j? leading up to the mixing chamber jS.
  • the heating mixture ignites and burns, continuing through the combustion chamber 12 leading to pipes J ⁇ 3 with heated media.
  • the main condensation zone in the combustion chamber is dependent on the media temperature, which is fed back through the return circuit in tubes 3. Usually it lies at the level of the first or second row of the combustion chamber floor. From the combustion chamber L2, partially cool the combustion products around the row of finned tubes, where the beginning condensation continues and a portion of the heat of the combustion product transits into the finned tube surface.
  • Condensation and the proportion of combustion product heat in the unit space according to the invention are terminated at profiling ribs 16 - of the descending end channel (15). Condensate flows back into siphon L9 and gas combustion products continue to lead outside, e.g. B. in chimney. Discharge heat gas combustion products with heat 70/50 * C most 55 * C does. Arrows in FIG. 1 show the flow directions in the condensing gas boiler according to the invention for clarity. The inner height of the mixing chamber J5 in leveling with other condensing gas boilers is 30% less. Mixer use for gas extraction and subsequent production of heating mixes in condensation gas boilers according to the invention makes reliable, uninterrupted operation possible even in conditions when this device for gas screen distribution with working pressure is imminent with a minimum usable value.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Incineration Of Waste (AREA)

Abstract

The invention pertains to a device consisting of a combustion chamber (12) and, situated at its upper surface, a mixing chamber (6), with a gas burner panel (11), and of a heat exchanger enclosed in the lower part of the combustion chamber. The mixer (1) is placed between gas and air feed lines and the mixing chamber (6) and made with a surrounding chamber (3), while near the critical inside diameter of the mixer there is a ring of at least three symetrically penetrating nozzles (5). The mixer feeds into the mixing chamber (6), which consists of the preparation sector (8) and the feed-line sector (7) comprising at least one feed partition (10) and a section wall (100). At the base of the combustion chamber there is at least one ribbed tube (14) with one end in the combustion chamber (12) and the other at the base of the descending channel (15). Between the descending channel wall and the combustion chamber wall there is a descending channel (17) linked with the mixer (1) via communication of the junction channel (22) with ventilator (21).

Description

MISCH- UND WARMETAUSCHSYSTEM AN KONDENSATIONSGASKESSELN MIXING AND WARM EXCHANGING SYSTEM ON CONDENSING GAS BOILERS
Technischer BereichTechnical part
Die Erfindung ist aus dem Bereich der Heizsystems und, wobei es sich um eine Einrichtung, die zum Wasser- und anderen Mediän¬ aufwärmen und die aus Zuleitungs- und anderen Verbindungsarmatu¬ ren, aus der Verbrennungskammer mit einem Flächengasbrenner und mit Mischkammerstandteilen übereinander beschaffende bestehend, wenn die Mischkammer ein Mischer mit der Umfangskammer voreinrei¬ hende hat. Zu unterem Verbrennungskammerteil ist ein Wärmeaus¬ tauscher zur Verbrennungsproduktenabkühlung und gleichzeitigen Vorlauf ärmen des Verbrennungsluft beigeschlossen.The invention is in the field of heating systems and is a device which heats up for water and other media and which consists of supply and other connection fittings, consisting of the combustion chamber with a flat gas burner and with mixing chamber components, one above the other. if the mixing chamber has a mixer in line with the peripheral chamber. A heat exchanger for cooling the combustion products and simultaneously reducing the flow of the combustion air is connected to the lower part of the combustion chamber.
Bisheriger Stand der TechnikCurrent state of the art
Die derartige Kondensationsaggregate, namentlich für tiefvo- lumender Räumenheizung benutzte, und ein Flächenbrenner in ver¬ schiedenen Formdurchführungen und Raumanordnungen haben, dem Re¬ lative hohe Wirksamkeit und kleine Schadstoffenemisionen von Ver¬ brennungsprozeßdurchlauf, vor allem NOχ, COχ und SOχ, charakte¬ ristische sind. Eine von Bedingungen für befriedigende Flächen¬ brennersarbeit bedarf vollständiger Brennmischunghomogenization und gleichmäßige, kontinuelle distribution der Heizmischung an ganze Brennersaktivflache ist. Nach dem Verbrennungsprozessab¬ schluß sind heiße Verbrennungsprodukte durch einen Verbrennungs¬ raum führende, wo Wasserdampfkondensation und Wärmetransit zwis¬ chen Flächen den wärmeaustatuschersder verlauft. Dann sind erküh¬ lende Verbrennungsprodukten führende in Aggregatausseraum, z. B. in Schornstein.The condensation units of this type, used in particular for low-volume room heating, and a surface burner in various mold lead-throughs and room arrangements, have relatively high effectiveness and small pollutant emissions from the combustion process run, especially NO χ , CO χ and SO χ ¬ are realistic. One of the conditions for satisfactory surface burner work is complete homogenization of the fuel mixture and uniform, continuous distribution of the heating mixture to the entire burner active area. After the combustion process is complete, hot combustion products pass through a combustion chamber, where water vapor condensation and heat transfer between the surfaces pass through the heat exchanger. Then cooling combustion products are leading into aggregate space, e.g. B. in chimney.
Zwischen Beispele den Lösungen vornähmlich eine Mischkammer in Gestalt zirka abgestumpfter Pyramide gehört, dessen Unter¬ grundebene ein Flächengasbrenner schafft. Eintrittende Luft ist in diese Mischkammer mit dem Ventilator liefert, der an Oben- grundebene senkrecht situierenden ist. In die Nähe der Eintritts¬ öffnung für Luft ist in der Mischkammer eine Lamelle; sie mit der Brennersfläche paralelle ist und eintrittenden Gas leitet in tur¬ bulenten Lauf ein. Der Gaseinricht an die gegenüberliegende Posi- tion zum Lufteintritt liegt.Between the examples, the solutions primarily include a mixing chamber in the form of a truncated pyramid, the subsurface of which is created by a surface gas burner. Air entering this mixing chamber is supplied with the fan, which is located vertically on the upper ground plane. There is a lamella in the mixing chamber in the vicinity of the inlet opening for air; it is parallel to the burner surface and introduces the gas that enters it into a turbulent barrel. The gas device to the opposite position tion to the air inlet.
Ebene, Großflächenbrenner von Keramik mit Fernflamme ist auch als Verbrennungskammerwandteil gelösend, wenn die Verbren- nungskammer in tafelförmigen Quadergestalt ist; Heizmischung ist in der Ventilatorskammer homogenisiert und in die Verbrennungs¬ kammer ist durch ein Öffnungen in Obengrundebene aus dem Ventila¬ tor führend.Plain, large-area burner of ceramic with a flame is also suitable as a combustion chamber wall part if the combustion chamber is in a tabular cuboid shape; The heating mixture is homogenized in the fan chamber and leads into the combustion chamber through an opening in the top level from the fan.
Weitere, bekannte Konstruktion, die Heizmischungshomogeniza- tion bis in Raum der Verbrennungskammer mit den zylindrischen Brenner von feuerfestem Stahl benutzt; an Brennerfläche die Mik- rodüsen für Heizmischungsdurchgang befertigen sind und die Ver¬ brennungskammer auch zylindrische Form hat, wobei ihre Innerflä- ehe Rohrspirale mit erwärmte Media schafft.Another known construction which uses heating mixture homogenization up to the area of the combustion chamber with the cylindrical burners of refractory steel; on the burner surface the micro nozzles for the heating mixture passage are made and the combustion chamber also has a cylindrical shape, its inner surface creating a spiral pipe with heated media.
Zwischen bekannte Lösungen auch Kreisförmigbrenner mit selb¬ ständigem Gaseintritt und mit selbständigem Verbrennungsl'_.ftein¬ tritt gehört; primäre Verbrennungsluft durch die selbständige Öffnungen in Brennersobenfläche ansaugend ist und dieser Brenner in Untergrundebene der Verbrenungskammer liegt. Sekundäre Ver¬ brennungsluft ist durch Öffnungen in Brenneraußenumfang geführend. An Seitenwandflache, welche dem Gas- und Lufteintritt gegenüber¬ liegende ist, der Flächenbrenner die Form der Zylinderabschnitt hat.Between known solutions also circular burners with independent gas entry and with independent combustion oil entry are heard; primary combustion air is sucked in through the independent openings in the upper surface of the burner and this burner lies in the underground level of the combustion chamber. Secondary combustion air is led through openings in the outer circumference of the burner. On the side wall surface, which is opposite the gas and air inlet, the surface burner has the shape of the cylinder section.
Tafelförmiger Quadergestalt mit konvexer Mittelverjüngung, wobei Achse von diesen Verjüngung zirka senkrechte zu Gas- undTabular cuboid shape with convex central taper, the axis of this taper being approximately perpendicular to gas and
Lufteinrichtungen in flauken Kammersinnerflächen; weitere Düsen mit Lamellen konkav engertem Kammersmittelteil ausschafende ist, bilden weitere bekannte Einrichtung.Air devices in flat interior areas of the chamber; further nozzles with lamellae concavely narrowed chamber middle part form further known device.
Beschriebene Konstruktionslösungen der Kondensationgaskes¬ seln haben mehrere typische Unzulänglichkeiten, wobei jede Ein- richtung minimal einen Nachteil aufweist. Derartige Kesseln haben relativ große Mischkammern und Heizmischungshomogenization hat überdauernte Mangeln; weitere Fehler ist relativ hohe tempera- tur der Verbrennungserzeugnisse, in Atmosphäre ausführenden und welche zirka an Niveau 80* C ist, was guter Beweis über weiteren möglichkeiten Wärmetauschverbesserungen bezeugt. Von dieser Wirk¬ lichkeit resultiert man, daß weitere Unzulänglichkeiten zur Eli¬ mination oder Erniedrigung existierenden Fehlern sind, z.B. Mö- glichkeiten in Erniedrigung der Schadstoffemisionen, in besserer Heizmischunghomogenisation, u.s.w.Described construction solutions of the condensation gas boilers have several typical shortcomings, each device having a minimal disadvantage. Such boilers have relatively large mixing chambers and heating mixture homogenization has persistent shortages; Another flaw is the relatively high temperature of the combustion products, which run in the atmosphere and which is around level 80 * C, which is good evidence of further possibilities for heat exchange improvements. The result of this reality is that there are further inadequacies for eliminating or lowering existing errors, for example possibilities for lowering pollutant emissions, better heating mixture homogenization, etc
Das Wessentliche des ErfindungsThe essence of invention
Die oben angeführten Mengel beseitigt durch Vorteile das Misch- und Wärmetauschsystem der Kondensationsgaskessel lt. Er¬ findung, das Wessentliche besteht darin, daß es aus Zuleitungsar¬ maturen, Verbindungsarmaturen mit dem Beherrschen-, Regulierungs¬ und Indikationsteil, aus der Mischer mit der Mischkammer und ei- nem Flächengasbrenner besteht. Der Flächengasbrenner schafft ei¬ nen Teil der Oberfläche der Verbrennungskammerteils; zu unteren Verbrennungskammerteil ist der Wärmeaustauscher beigeschlossen, in dessen ist Verbrennungproduktenabkühlung und gleichzeitigen Vorlaufwärmen des Verbrennungsluft vornehmen. Der Mischer ist als eine Venturi-Rohr mit axialen Zuleitung für komprimiertes ( z.B. mit Hilfe des Ventilatores ) Verbrennungsluft hergestellt. Nach der Außenfläche des Mischers ist die Umfangskammer mit ihrer In¬ nerflächen als ein hohl Rotaitionkörper profilierende und mit ra¬ dialer Gaszuleitung besorgende. Mischersinnerraum und Umfangsin- nerraum sind zueinander in die N he kritisches Durchmessers mit durchbohrende Umfangsdüsen vereinigen. Die Umfangsdüsen sind mi¬ nimal drei und ringsherum symetrisch durchbohrende.The above-mentioned deficiency eliminates the advantages of the mixing and heat exchange system of the condensing gas boiler according to the invention. The essential part is that it consists of supply fittings, connecting fittings with the control, regulation and indication part, from the mixer with the mixing chamber and there is a surface gas burner. The surface gas burner creates part of the surface of the combustion chamber part; The heat exchanger is connected to the lower part of the combustion chamber, in which the combustion products are cooled and at the same time pre-heated by the combustion air. The mixer is manufactured as a Venturi tube with an axial feed line for compressed (e.g. with the help of the fan) combustion air. After the outer surface of the mixer, the peripheral chamber, with its inner surfaces, is profiled as a hollow rotary body and provides radial gas supply. The interior of the mixer and the interior of the circumference are close to one another in the vicinity of the critical diameter with circumferential nozzles that pierce. The circumferential nozzles are a minimum of three and symmetrically piercing all around.
Weiteres Erfindungsmerkmal liegt darin, daß die Längenachse der Umfangsdüse mit zur Längenachse des Mischers lotrechtemFlach¬ land Winkel 15* groß nach der Luftströmeinrichtung enschießt und weiter darf Längenachse der Umfangsdüse mit der zur Längenach¬ se des Mischers senkrechte und durch die Umfangsdüsemitter hin- durchsgehende Gerade den Winkel bis 13* zu 17* nach der Gasstrom- einrichtung entschliesen.A further feature of the invention is that the longitudinal axis of the peripheral nozzle shoots at an angle 15 * perpendicular to the longitudinal axis of the mixer after the air flow device, and furthermore the longitudinal axis of the peripheral nozzle with the straight line perpendicular to the longitudinal axis of the mixer and passing through the peripheral nozzle emitter Decided angles up to 13 * to 17 * after gas flow setup.
Zum Mischeraustritt ist der Mischkammereintritt ( z.B. mit der Verbindungsarmatur ) angeschlossen, wenn die Mischkammer be- steht aus dem Durchtrittssektor und aus dem Zuleitungssektor Der Zuleitungssektor ist am wenigsten einer Zuleistungsteilwand beinhaltend und zugleich sie ist zirka senkrecht zu horizontaler Ebene des Zuleitungssektors und auch zur Eintritteirichtung der Heizmischung stiftende. Minimal die erste aus Zuleitunsteilwänden ist als ein Siebwerk erzeugt, wenn er kann auch ihre ebene Figur mit Totalluftröhrenflache zirka 28 % haben. Die Zuleitungsteil¬ wand ist von der Stirnwand der Mischkammer mit dem Heizmischungs- eintritt und/oder von benachbarter Zuleitungswand und/oder von der Abteilungswand um Horizontallänge am wenigsten übereinstim¬ mende ihre Höhe, einfernend. Die Zuleitungswändeanzahl in die Mischkammer ist als Breite/Länge des Flächengasbrenneryerhältnis definiert. Nur eine Zuleitungsteilwand wird in Zufall, wenn die¬ ser Verhältnis größer als 0,4 ist, ganz genügend; derweil Ver- hältnis bis 0,4 zu 0,17 ist, die zwei Zuleistungswände genügend werde .The mixing chamber inlet (eg with the connection fitting) is connected to the mixer outlet when the mixing chamber is stands from the passage sector and from the supply sector. The supply sector is least comprised of a partial supply wall and at the same time it is approximately perpendicular to the horizontal plane of the supply sector and also to the direction of entry of the heating mixture. At least the first one made of supply part walls is produced as a screen, if it can also have its flat figure with a total air tube surface of about 28%. The supply line wall is the least coincident in height from the front wall of the mixing chamber with the heating mixture inlet and / or from the adjacent supply wall and / or from the section wall by horizontal length. The number of supply walls in the mixing chamber is defined as the width / length of the surface gas burner ratio. Only one partial wall of the supply line, when this ratio is greater than 0.4, becomes quite sufficient; meanwhile the ratio is up to 0.4 to 0.17, the two additional walls will be sufficient.
Folgenden Vorteil nach diese Erfindung mann kann erwarten, wenn die Ebene der Abteilungswand und Horizontalebene des Zulei- tungskammer ein Winkel 80* oder kleinsten bilden. Der Durch- strittssektor ist als länhliches Prisma mit dem Vertikalquer¬ schnitt irreguläres Polygons ausgefertigt und der Boden dieses Durchstritssektors der Flächenbrenner bildet, welcher auch zu¬ gleich den Teil der Verbrennungskammerobenflache bildet.The following advantage according to this invention can be expected if the plane of the compartment wall and the horizontal plane of the feed chamber form an angle 80 * or the smallest. The penetration sector is made as an elongated prism with the vertical cross section of irregular polygons and the bottom of this penetration sector is formed by the surface burner, which also forms part of the upper surface of the combustion chamber.
Der Wärmeaustauscher ist als zweistufender ausgefertigt und bildet ihn minimal ein in die schliefe Linie liegende Rippenrohr, mit erstem Ende in Boden der Verbrennungskammer bettend und mit zweitem Ende des Rippenrohres in Grund des Aufsteigenkanals mit dem Siphon und mit dem Kaskade von Profilierenrippen wändet. Zwischen minimal einer des Aufsteigenkanals und minimal einer Außenumfangswand der Verbrennungskammer ist der Absteigendkanal mit System von Profilierenrippen erschaffen. Die Untermündung des Absteigendkanals ist zu axialem Zuleitung des Mischers ver- knüpft ( direkt oder indirekt - z.B. durch Vermitlung des Ver¬ bindungskanal mit einem Ventilator und mit der Verbindungsarmatur beendend ). Innerhalb Hauptvorteile des Kondensationsgaskessels lt. Er¬ findung vor allem beruht gebesserte Betriebssicherheit, die ist durch Benützung vorschreibenen Mischer mit der Ümfangskammer für Heizmischungsgestaltung erzielte, weil diese Konstruktionsverbin- düng der Knallgemengesbildung in Innerraum des Aggregatesschran- kes abwendet, z.B. bei Abschaltung des VerbrennungsSystems bei automatischem Aggregatsbeherrschung, besonders mit Gaseinwachtung vereinte. Nach dem Gasabsperrhahnschiebung in der Gaszuleitung ist ganzer Gasrest von Kesselsinnerraum durch spontan endete Di- fusion augesaugt. Ganzer Schranksinnerraum ist am besten luftdicht und Gas oder Heizmischung durch eventuelle Undichtheiten in der Einrichtung entweichende sind zurück in den Absteigendkanal zu- rückabsgauende, woher sie schritten weiter mit frischer Luft in Mischer fort. Gasrestabdichtung den Schrank Wärmeentkommen auch niedriger macht, dafür diese Wärmeeniergie ist für Vorlaufwärmen des Verbrennungsluft bezweckende.The heat exchanger is made as a two-stage and forms it minimally a finned tube lying in the slack line, with the first end in the bottom of the combustion chamber and the second end of the finned tube in the base of the ascending channel with the siphon and the cascade of profiled fins. The descending duct is created with a system of profiling ribs between at least one of the ascending duct and at least one outer peripheral wall of the combustion chamber. The mouth of the descending end channel is linked to the axial feed line of the mixer (directly or indirectly - for example by mediating the connecting channel with a fan and ending with the connecting fitting). Within the main advantages of the condensation gas boiler, according to the invention, there is above all improved operational safety, which is achieved by using the prescribed mixer with the peripheral chamber for heating mixture design, because this avoids the structural mixture formation in the interior of the unit cabinet, for example when the combustion system is switched off when the combustion system is switched off automatically Mastery of aggregates, especially combined with gas monitoring. After the gas shut-off valve has been pushed in the gas supply line, the entire gas residue from the interior of the boiler is sucked out through spontaneously ended diffusion. Entire cabinet interior is best airtight and gas or heating mixture escaping through any leaks in the facility are back-venting back into the descending channel, from where they continued with fresh air in the mixer. Residual gas sealing also makes the cupboard heat escape lower, but this heat energy is intended for pre-heating the combustion air.
Die Mischkammerlösung wessentliche erniedrigung ihrer Höhe erlaubt, was Ansprüche an angebauenden Raum und unverbrannten Heizmischungsbedarf erniedrigt.The mixing chamber solution allows substantial lowering of its height, which lowers demands on additional space and unburned heating mixture requirements.
Zweistufende Wärmeaustauscher nach dieser Erfindung bei wär- mewendung 70/50* C maximale Verbrennungsproduktenwärme 55* C mö¬ glicher macht. Der Wasserdämpfe kondenzierte bei volgerichtiger Verbrennungsproduktenabkühlung, Erfangung der relativ günstigen Kondensatsäuerwert und dessen Auslassen in Öffentlichkanalisation ohne vorherigen Bereitungen ( z.B. ohne Neutralisation ) zulaßt.Two-stage heat exchanger according to this invention at a heat turn of 70/50 * C makes maximum combustion product heat 55 * C possible. The water vapors condensed in the case of proper combustion product cooling, the acquisition of the relatively favorable condensate acid value and its discharge in the public sewer system without prior preparations (eg without neutralization).
Beispiel für den Ausführung der Erfindung und Beschreibung von AbbildungenExample of the implementation of the invention and description of illustrations
Mehrere Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden im folgenden näher erläutert. Es zeigen: Fig. 1 Kondensationsgaskesselschema in horizontalem Querschnitt ohne Beherrschen-, Regulierungs- und Indikationsteilen; Fig. 2 den Mischer mit der Ümfangskammer in Aufriß mit horizon¬ talem Schnitt; Fig. 3 transversalen Schnit durch den Mischer von Fig. 2; Fig. 4 vertikalen Querschnitt durch unteren Verbrennungskammer¬ teil mit den Wärmeaustauscher Fig. 5 vertikalen Querschnitt durch die Mischkammer mit dem Flä- chengasbrenner, und welche haben folgende Bezugszeichen herbeigezogen:Several embodiments of the invention are shown in the drawing and are explained in more detail below. 1 shows a condensation gas boiler diagram in a horizontal cross section without control, regulation and indication parts; 2 shows the mixer with the circumferential chamber in elevation with a horizontal section; Fig. 3 shows a transverse section through the mixer of Fig. 2; 4 vertical cross section through the lower combustion chamber part with the heat exchanger FIG. 5 vertical cross section through the mixing chamber with the surface gas burner, and which have used the following reference numerals:
1 Mischer 13 Rohr1 mixer 13 pipe
2 Verbindungsarmatur 14 Rippenrohr 3 Ümfangskammer 15 AufSteigenkanal2 connection fitting 14 finned tube 3 circumferential chamber 15 ascent channel
4 Gaszuleitung 16 Profilierenrippe4 Gas supply line 16 Profiling rib
5 Umfangsdüse 17 Absteigendkanal5 circumferential nozzle 17 descending channel
6 Mischkammer 18 Profilierenrippe6 Mixing chamber 18 Profiling rib
7 Zuleitungssektor 19 Siphon 8 Armatur 20 Gasabsperrhahn7 Supply sector 19 siphon 8 fitting 20 gas shut-off valve
9 Armatur 21 Ventilator9 fitting 21 fan
10 Zuleitungsteilwand 22 Verbindungskanal10 supply line wall 22 connecting channel
11 Flächengasbrenner 23 Schrank11 surface gas burner 23 cabinet
12 Verbrennungskammer 100 Abteilungswand12 combustion chamber 100 department wall
Der Mischer JL ist als Venturi-Rohr hergestellt und mit axia¬ lem Verbrennungsluftzuleitung mit der Verbindungsarmatur 2_ an¬ schaffend. Nach der Außenfläche des Mischers 1_ ist die Ümfangs¬ kammer mit ihrer Innerflächen als Rotationkörper profilierende und mit radialer Gaszuleitung besorgt. In die Nähe kritisches Mischerinnerdurchmessers sind drei ringsherum und symetrisch durchbohrende Umfangsdüsen, dessen Längenachsen mit zur Längen¬ achse des Mischers 1_ lotrechtem Flachland 15* Winkel nach der Luftströmenrichtung entschließen. Winkel 15* nach der Gasstrom- einrichtung ist auch zwischen Längenachsen aller Umfangsdüsen 5_ und zwischen zu Längenachsen senkrechten, durch die Umfangsdüsen- mittern hindurchsgegenden Geraden. Der Mischeraustritt durch die Armatur 9_ zum Eintritt der Mischkammer 6_ eingeordnet. Die Misch¬ kammer 6_ besteht aus dem Durchtrittssektor 1_ und aus dem Zulei- tungssektor jB, welche mit der Abteilungswand 100 separierende sind. Die Abteilungswand 100 und Horizontalzentrischebene des Zu¬ leitungssektors Winkel 80* entschließen und die Abteilungswand 100 als Siebwerk mit Totalluftröhrenflache 28 % erzeugte. In der Zuleitungssektor 7. sind auch zwei Zuleitungsteilwände ^0 beinhal¬ tende, senkrecht zu horizontaler Ebene des Zuleitungssektors T_ und zu Eintrittseinrichtung der Heizmischung stiftende. Erste Zu¬ leitungsteilwand _6 ist von benachtbarter Zuleitungsteilwand 10 und von der Stirnwald der Mischkammer 6_ mit dem Heizmischungsein- tritt und zweite Zuleitungsteilwand 1__ von der Abteilungsteilwand 100 um gleichartige Horizontallänge, welche als ihrer Höhen sind, fernliegende. Der Flächengasbrenner jLl. den Boden des Durchstritts- sektors J3 und einen Oberflächenteil des Verbrennungskammerteils Y2__ bildet. Die Verbrennungskammer 12 ist zur Grund konisch und geengerte und vier Reihen erwärmten Rohren 1_3 beinhaltet. In ge- gliderten Verbrennungskammergrund ist Reihe schief liegender Rip¬ penrohren 1 _, wenn jede von ihnen mit erstem ende in Verbren¬ nungskammerraum bettende ist und mit zweitem Ende in Grund des Absteigennkanals L5 mit dem Siphon 1^9 und rait der innerer Kaskade von Profilierenrippen ljϊ ausgemündet ist. Zwischen Außenumfangs- wand des AufSteigendkanals L5 und der Außenumfangswand der Ver¬ brennungskammer L2 der Absteigendkanal L7 mit System paraleller profilierenrippen ____ erschaffend ist. Die Untermündung des Ab- steigendkanals ±1_ zum Axialzuleitung des Mischers 1_ durch Vermit- lung des Verbindungskanals ^2 mit elektrischem Ventilator 21_ und mit der Verbindungsarmatur verknüpft ist. Die Obenmündung des Aufsteigenkanals _15 zur Verbrennungsproduktenableitung beige¬ schlossen ist. Gas in Raum der Ümfangskammer 3_ in die Austritt- röhr mit dem Gasabsperrhahn 2Q_ zugeführtend ist; Verbrennungsluft für Heizmischungbildung mit dem Ventilator 21 hineinbetriebende ist. Atmosphärische Luft ist durch Eintrittsöffnung in Schrank 23 ausaugende, wovon sie steigt in Absteigendkanal 1^7 ein. Hier ist diese Luft vorwärmt und weiter um Wärmantauschflächen von Rippen- röhren 1 und durch den Verbindungskanal 22 bis zum Ventilator 21 forsetzte ist. Die Luft durch der Mischer 1 verfahrt, wo sie mit Gas, difundierendem durch Umfangsdüsen 5^ Vermittlung bei schrau- benförmigten Lauf in der Nähe Mischersinnerflächen vermischt sich. Resultierende Heizmischung ist in die Armatur j? bis zur Mischkam- mer jS führende. Hier, in Zuleitungssektor und beim Zuleitungswän¬ dedurchgang ist restlose Homogenisation der Heizmischung und ihre gleichmäßige distribution nach ganze Gasbrennerfläche beendet. Nach Durchgang den Gasbrennersdüsen Heizmischung entzündet sich und brennt, wobei sie ist weiter durch die Verbrennungskammer 12 um Rohre J^3 mit erwärmte Media führende. Die Hauptkondensations¬ zone in der Verbrennungskammer ist von der Mediatemperatur, zu¬ rückführender durch Rückkreis in Rohren 3 vorhängig. Usuell sie auf Niveau der erste oder zweite Reihe von Verbrennungskammerboden liegt. Aus der Verbrennungskammer L2 teilweise abkühlende Ver¬ brennungsprodukte um Rippenrohrenreihe übersetzen, wo anfangende Kondensation weiter verlauft und ein Anteil von Verbrennungspro¬ duktenwarme in Rippenrohrenfl chentransitiert. Kondensation und Anteil von Verbrennungsproduktenwarme in Aggregatsraum nach der Erfindung sind an Profilierenrippen 16. ---- des Absteigendkanals ( 15 ) beendet. Kondensat flißt inSiphon L9 zurück und Gasver¬ brennungsprodukten sind weiter in Außerraum führende, z. B. in Schornstein. Austrittwärme GasVerbrennungsprodukten bei Wärmewen¬ dung 70/50* C am meisten 55* C tut. Pfeilen in Fig. 1 für über- sichtlichkeit die Strömungrichtungen in Kondensationsgaskessel nach der Erfindung zeigen. Die Innerhöhe der Mischkammer J5 im Ebnen mit anderen Kondensationsgaskesseln um 30 % mindere ist. Mischergebrauch zu Gasaussaugung und folgender Heizmizchungsfer- tigung in Kondensationsgaskessel lt. Erfindung zuverläßiger, si- eher un ununterbrochener Betrieb auch in Bedingungen möglich macht, wenn diese Vorrrichtung zu Gassiebverteilung mit Arbeits¬ druck bei minimalem Verwendbarwert bevorstehende ist. The mixer JL is produced as a Venturi tube and is provided with an axial combustion air supply line with the connection fitting 2_. After the outer surface of the mixer 1_, the inner chamber is provided with its inner surfaces as profiling bodies of revolution and with a radial gas supply line. In the vicinity of the critical mixer inner diameter are three circumferential nozzles which penetrate symmetrically and all around, the length axes of which, with the flat axis of the mixer 1_ perpendicular to the length axis of the mixer, make an angle of 15 * according to the air flow direction. Angle 15 * after the gas flow device is also between the longitudinal axes of all circumferential nozzles 5_ and between straight lines perpendicular to the longitudinal axes and passing through the circumferential nozzle centers. The mixer outlet through the fitting 9_ arranged for the entry of the mixing chamber 6_. The mixing chamber 6_ consists of the passage sector 1_ and the feed sector jB, which are separating with the department wall 100. Resolve the department wall 100 and horizontal centric plane of the supply sector angle 80 * and the department wall 100 as a sieve with a total air tube area generated 28%. In the Supply sector 7. Are also two partial supply walls ^ 0 containing, perpendicular to the horizontal plane of the supply sector T_ and leading to the inlet device of the heating mixture. The first partial feed wall _6 is remote from the adjacent partial feed wall 10 and from the end forest of the mixing chamber 6_ with the heating mixture inlet, and the second partial feed wall 1__ from the partial compartment wall 100 by the same horizontal length, which is its height. The flat gas burner jLl. forms the bottom of the penetration sector J3 and a surface part of the combustion chamber part Y2__. The combustion chamber 12 is basically tapered and narrowed and four rows of heated tubes 1_3 are included. In the divided combustion chamber base there is a row of slanting finned tubes 1_, if each of them is in the combustion chamber space with the first end and with the second end in the descending channel L5 with the siphon 1 ^ 9 and the inner cascade of profiled ribs ljϊ is out. Between the outer circumferential wall of the ascending duct L5 and the outer circumferential wall of the combustion chamber L2, the descending duct L7 is created with a system of parallel profiling ribs ____. The opening of the descending duct ± 1_ to the axial feed line of the mixer 1_ is linked by means of the connecting duct ^ 2 to the electric fan 21_ and to the connecting fitting. The upper mouth of the ascending channel _15 is closed for the discharge of combustion products. Gas is fed into the space of the containment chamber 3_ into the outlet tube with the gas shut-off valve 2Q_; Combustion air for heating mixture formation with the fan 21 is operating. Atmospheric air is exhausting through the inlet opening in cabinet 23, of which it enters descending channel 1 ^ 7. Here, this air is preheated and continues around heat exchange surfaces of finned tubes 1 and through the connecting duct 22 to the fan 21. The air travels through the mixer 1, where it mixes with gas, diffusing through peripheral nozzles 5 ^ mediation with a screw-shaped barrel in the vicinity of the mixer interior surfaces. Resulting heating mixture is in the fitting j? leading up to the mixing chamber jS. Here, in the supply sector and in the supply wall passage, complete homogenization of the heating mixture and its uniform distribution over the entire gas burner area has ended. After passage of the gas burner nozzle, the heating mixture ignites and burns, continuing through the combustion chamber 12 leading to pipes J ^ 3 with heated media. The main condensation zone in the combustion chamber is dependent on the media temperature, which is fed back through the return circuit in tubes 3. Usually it lies at the level of the first or second row of the combustion chamber floor. From the combustion chamber L2, partially cool the combustion products around the row of finned tubes, where the beginning condensation continues and a portion of the heat of the combustion product transits into the finned tube surface. Condensation and the proportion of combustion product heat in the unit space according to the invention are terminated at profiling ribs 16 - of the descending end channel (15). Condensate flows back into siphon L9 and gas combustion products continue to lead outside, e.g. B. in chimney. Discharge heat gas combustion products with heat 70/50 * C most 55 * C does. Arrows in FIG. 1 show the flow directions in the condensing gas boiler according to the invention for clarity. The inner height of the mixing chamber J5 in leveling with other condensing gas boilers is 30% less. Mixer use for gas extraction and subsequent production of heating mixes in condensation gas boilers according to the invention makes reliable, uninterrupted operation possible even in conditions when this device for gas screen distribution with working pressure is imminent with a minimum usable value.

Claims

P A T E N T A N S P R Ü C H EP A T E N T A N S P R Ü C H E
1. Misch- und Wärmetauschsystem der Kondensationsgaskessel, bestehend aus den Zuleitungs- und Verbindungsarmaturen, aus mini- mal eine Verbrennungskammer mit einem Flächengasbrenner und mit Mischkammerbestandteilen, übereinender beschaffende, und aus ei¬ nen", zu unterem Verbrennungskammerteil beigeschlossenen Wärmeaus¬ tauscher zur Verbrennungspoduktenabkühlung und gleichzeitigen Vorlaufwärmen des Verbrennungsluft, d a d u r c h g e k e n n - z e i c h n e t , daß zwischen den Gas- und Verbrennungsluftzu¬ leitungen und den Eintritt der Mischkammer ( 6 ) ist der Mischer ( 1 ) eingeordnet, welcher ist als Venturi-Rohr hergestellt und mit axialem Verbrennungszuleitung anschaffend, wenn nach der Au¬ ßenfläche des Mischers ( 1 ) ist die Ümfangskammer ( 3 ) mit ihr Innerflächen als ein hohl Rotationkörper profilierende und mit radialer Gaszuleitung ( 4 ) besorgende, derweil in die nähe kri¬ tisches Mischerinnerdurchmessers sind minimal drei ringsherum und symetrisch durchbohrende Umfangsdüsen ( 5 ) , wenn die Mischkammer ( 6 ) besteht aus dem Durchtrittssektor ( 8 ) und aus dem Zulei- tungssektor ( 7 ), beinhaltendem am wenigstem mit einer Zuleis- tungsteilwand ( 10 ), stiftendem zirka senkrecht zu horizontaler Ebene des Zuleitungssektors ( 7 ) und zur Entritteinrichtung der Heizmischung stiftende, wenn der DurchtrittsSektor ( 8 ) hat den Vertikalquerschnitt irreguläres Polygons und den Boden dieses Durchtrittssektors ( 8 ) bildet der Flächengasbrenner ( 11 ) und simultan der Zuleitungssektor ( 7 ) und der Durchtrittssektor ( 8 ) sind beiderseits mit dem Abteilungswand ( 100 ) separieren¬ de, und/oder der Wärmeaustauscher ist als zweistufender angefer¬ tigt und bildet ihn minimal ein in schiefe Linie liegende Rippen- röhr ( 14 ) mit erstem Ende in Boden der Verbrennungskammer ( 12 ) bettende und mit zweitem Ende des Rippenrohrs ( 14 ) in Grund des Aufsteigenkanals ( 15 ) mit dem Siphon ( 19 ) und mit Kaskade von Profilierenrippen ( 16 ) wändet, wenn zwischen minimal einer Außenumfangswand des Aufsteigenkanals ( 15 ) und minimal einer Außenumfangswand der Verbrenn ngska mer ( 12 ) ist der Abstei¬ gendkanal ( 17 ) mit System Profilierenrippen ( 18 ) erschaffen und wenn die Untermündung des Absteigendkanals ( 17 ) ist zum Axialzuleitung des Mischers ( 1 ) verknüpft, z. B. durch Vermit- lung des Verbindungskanal ( 22 ) mit einem Ventilator ( 21 ) und/oder mit der Verbindungsarmatur ( 2 ) , wenn Obenmündung des Aufsteigenkanals ( 15 ) ist zur Verbrennungsproduktenableitung beigeschlossen.1. Mixing and heat exchange system of the condensation gas boiler, consisting of the supplying and connecting fittings, of minimally a combustion chamber exchanger with a surface gas burner and mixing chamber components, agree procured, and from ei¬ nen ", appended to the lower combustion chamber part Wärmeaus¬ to Verbrennungspoduktenabkühlung and Simultaneous flow heating of the combustion air, characterized in that the mixer (1) is arranged between the gas and combustion air supply lines and the inlet of the mixing chamber (6), which is manufactured as a Venturi tube and with an axial combustion supply line, if necessary after the On the outside surface of the mixer (1), the circumferential chamber (3) with its inner surfaces is profiled as a hollow rotating body and provides radial gas feed line (4), meanwhile in the vicinity of the critical mixer inner diameter there are at least three circumferential and symmetrically piercing circumferences sen (5), if the mixing chamber (6) consists of the passage sector (8) and of the feeder sector (7), including least with a feeder part wall (10), donating approximately perpendicular to the horizontal plane of the feeder sector (7 ) and to the entry device of the heating mixture if the passage sector (8) has the vertical cross section of irregular polygons and the bottom of this passage sector (8) is formed by the surface gas burner (11) and simultaneously the supply sector (7) and the passage sector (8) are on both sides with the Department wall (100) separating, and / or the heat exchanger is made as a two-stage and forms it minimally a finned tube (14) lying in an oblique line with the first end in the bottom of the combustion chamber (12) and the second end of the bed Finned tube (14) in the base of the ascending channel (15) with the siphon (19) and with a cascade of profiling ribs (16) if between min The descending channel (17) is created with a system of profiled ribs (18) in an outer circumferential wall of the ascending channel (15) and at least one outer circumferential wall of the combustion chamber (12), and when the opening of the descending end channel (17) is for the axial feed of the mixer (1 ) linked, e.g. B. by means of tion of the connecting channel (22) with a fan (21) and / or with the connecting fitting (2) when the top of the ascending channel (15) is included for the discharge of combustion products.
2. Misch- und Wärmetauschsystem der Kondensationsgaskessel nach Anspruch 1, d a d u r c h g e k e n n z e i c h n e t , daß Längenachse der Umfangsdüse ( 5 ) mit zur Längenachse des Mi¬ schers ( 1 ) lotrechtem Flachland den Winkel den 15* nach der Luftströmmenrichtung enschließt.2. Mixing and heat exchange system of the condensing gas boiler according to claim 1, characterized in that the longitudinal axis of the peripheral nozzle (5) with the longitudinal axis of the mixer (1) perpendicular flat land closes the angle 15 * according to the air flow direction.
3. Misch- und Wärmetauschsystem der Kondensationsgaskessel nach Anspruch 1 oder 2, d a d u r c h g e k e n n z e i c h ¬ n e t , daß Längenachse der Umfangsdüse ( 5 ) mit der zur Längen- achse des Mischers ( 1 ) senkrechte und durch die Umfangsdüsemit- ter hindurchsgegende Gerade den Winkel bis 13* zu 17* nach der Gasströmeneinrichtung entschließt.3. Mixing and heat exchange system of the condensing gas boiler according to claim 1 or 2, characterized in that the longitudinal axis of the peripheral nozzle (5) with the line perpendicular to the longitudinal axis of the mixer (1) and through the peripheral nozzle center line up to 13 * resolved to 17 * after the gas flow facility.
4. Misch- und Wärmetauschsystem der Kondensationsgaskessel nach mindestens einem Ansprüche bis l zu 3, d a d u r c h g e ¬ k e n n z e i c h n e t , daß Ebene der Abteilungswand ( 100 ) und Horizontalzentrischebene des .Zuleitungssektors ( 7 ) ein Win¬ kel den 80* oder kleines entschließt.4. Mixing and heat exchange system of the condensing gas boiler according to at least one of claims up to 3, dadurchge ¬ indicates that level of the department wall (100) and horizontal centric plane of the .supply sector (7) decides an angle 80 * or small.
5. Misch- und Wärmetauschsystem der Kondensationsgaskessel nach mindestens einem Ansprüche bis l zu 4, d a d u r c h g e ¬ k e n n z e i c h n e t , daß minimal eine Zuleitungsteilwand ( 10 ) und/oder die Abteilungswand ( 100 ) ist als ein Siebwerk erzeugt und ist von der Stirnwand der Mischkammer ( 6 ) mit dem Heizmischungseintritt und/oder von benachbarter Zuleitungsteil¬ wand ( 10 ) und/oder von der Abteilungswand ( 100 ) um Horizon¬ tallänge am wenigsten übereinstimmende mit ihre Höhe einfernend.5. mixing and heat exchange system of the condensing gas boiler according to at least one of claims up to 4, dadurchge ¬ indicates that minimally a supply line wall (10) and / or the partition wall (100) is produced as a screen and is from the end wall of the mixing chamber (6 ) with the entry of the heating mixture and / or from the neighboring supply part wall (10) and / or from the department wall (100) least horizontally by their length.
6. Misch- und Wärmetauschsystem der Kondensationsgaskessel nach mindestens einem Ansprüche bis l zu 5, d a d u r c h g e ¬ k e n n z e i c h n e t , daß Zuleitungswändeanzahl ist ein Brei¬ te/Länge des Flächengasbrennersverhältnis definiert und dieses Verhältnis größer als 0,4 eine Zuleitungsteilwand ( 10 ) bestimmt. derweil Verhältnis bis 0,17 zu 0,4 diesel Anzahl als zwei dürfti¬ ge Zuleitungswände festgesetzt.6. Mixing and heat exchange system of the condensation gas boiler according to at least one of claims up to 5, dadurchge ¬ indicates that the number of supply walls is a width / length of the surface gas burner ratio defined and this ratio is greater than 0.4 a partial supply wall (10) determines. meanwhile ratio up to 0.17 to 0.4 diesel number as two poor supply walls.
8. Misch und Wärmetauschsystem der Kondensationsgaskessel nach mindestens einem Ansprüche bis l zu 7, d a d u r c h g e ¬ k e n n z e i c h n e t , daß nach Heizmischungdurchgang erste Zuleitungsteilwand ( 10 ) ist nach ebene Figur mit Totalluftröh- renflache zirka 28 %. 8. Mixing and heat exchange system of the condensing gas boiler according to at least one of claims up to 7, so that after heating mixture passage the first partial supply wall (10) is approximately 28% according to the flat figure with a total air tube.
EP93921777A 1992-10-09 1993-10-11 Mixing and heat-exchange system for condensing gas boilers Ceased EP0663056A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
CS923097A CZ278788B6 (en) 1992-10-09 1992-10-09 Combustion system of heating gas condensation sets
CS3097/92 1992-10-09
PCT/CZ1993/000025 WO1994009326A1 (en) 1992-10-09 1993-10-11 Mixing and heat-exchange system for condensing gas boilers

Publications (1)

Publication Number Publication Date
EP0663056A1 true EP0663056A1 (en) 1995-07-19

Family

ID=5370068

Family Applications (1)

Application Number Title Priority Date Filing Date
EP93921777A Ceased EP0663056A1 (en) 1992-10-09 1993-10-11 Mixing and heat-exchange system for condensing gas boilers

Country Status (4)

Country Link
EP (1) EP0663056A1 (en)
CZ (1) CZ278788B6 (en)
SK (1) SK309792A3 (en)
WO (1) WO1994009326A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT1288006B1 (en) * 1996-12-06 1998-09-10 Sit La Precisa Spa AIR-GAS MIXER DEVICE IN PARTICULAR FOR GAS BURNERS WITH FORCED VENTILATION.
DE19733767A1 (en) * 1997-08-05 1999-02-11 Dungs Karl Gmbh & Co Fuel gas introduction device for a gas premix burner
IT1295238B1 (en) * 1997-09-29 1999-05-04 Ferroli Spa PERFECTED PREMIXED CONDENSING BOILER, PARTICULARLY SUITABLE FOR THE PRODUCTION OF SANITARY WATER AND FOR HEATING
US7108838B2 (en) 2003-10-30 2006-09-19 Conocophillips Company Feed mixer for a partial oxidation reactor

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2700786C3 (en) * 1977-01-11 1980-05-14 Hermann Rappold & Co Gmbh, 5160 Dueren Ceramic gas burner for wind heaters
DE3312563C2 (en) * 1983-04-07 1986-01-16 Gosudarstvennyj proektnyj i naučno-issledovatel'skij institut nikelevo-kobal'tovoj promyšlennosti, Leningrad Device for burning fuel and for feeding the combustion products into a melt
NL8702303A (en) * 1987-09-25 1989-04-17 Wetering Gemeenschappelijk Bez HEATER.
GB2218787B (en) * 1988-05-20 1992-06-10 Northern Eng Ind Boilers
ATE66529T1 (en) * 1988-12-02 1991-09-15 Geminox Sa CONDENSING BOILER FOR HEATING WITH HEAT TRANSPORT LIQUID.
DE3926699A1 (en) * 1989-08-12 1991-02-14 Kloeckner Waermetechnik GAS BURNER
DE9213594U1 (en) * 1992-10-14 1993-03-18 Marek, Rudolf, 2000 Hamburg Burners for heaters and heating systems

Non-Patent Citations (8)

* Cited by examiner, † Cited by third party
Title
DE-A- 2 700 786 *
DE-A- 3 312 563 *
DE-A- 3 842 463 *
DE-U- 9 213 594 *
EP-A- 0 373 027 *
EP-A- 0 415 008 *
See also references of WO9409326A1 *
US-A- 4 998 508 *

Also Published As

Publication number Publication date
WO1994009326A1 (en) 1994-04-28
CZ278788B6 (en) 1994-06-15
SK277937B6 (en) 1995-08-09
SK309792A3 (en) 1995-08-09
CZ309792A3 (en) 1994-04-13

Similar Documents

Publication Publication Date Title
DE2519091C2 (en) Device for heating a room
DE112018003288T5 (en) Heater and method for heating air and water in a recreational vehicle and recreational vehicle
DE69315804T2 (en) Gas-fired device with an atmospheric burner
EP0125572A1 (en) Multi-fuel burner
EP0050788B1 (en) Heating plant with an absorption heat pump, and method of operating it
EP0663056A1 (en) Mixing and heat-exchange system for condensing gas boilers
DE2950901A1 (en) CENTRAL HEATING SYSTEM
DE10162952C2 (en) heat exchanger device
DE3308700C2 (en) Equipment for heating and ventilation
DE69929769T2 (en) Burner assembly and burner head for gas mixture combustion
DE3623103C2 (en)
DE10251816A1 (en) Gas burner for boiler has burner plate insulated from lower casing and elastically connected to it
WO1988003249A1 (en) Burner for the combustion of liquid fuel
DE2604784A1 (en) Vertical tubed water boiler - has heating tubes passed vertically between two ring tubes joined at tapered ends
DE4218754A1 (en) Method of providing low pollution combustion of gaseous or aerosol fuel - involves supplying fuel and combustion air to suction side of driven, bladed impeller
EP0162445A2 (en) Radiation burner
DE19819138C2 (en) furnace
EP1002993B1 (en) Boiler for liquid fuels
DE19947565A1 (en) Two-fluid mixer for any gas or liquid combination, includes polygon tube plane with offset, inclined, parallel and divergent walls, complemented by jet slots and impact baffles, producing uniform mixture across entire cross section
DE3102742A1 (en) Appliance heated by a gas-operated burner
DE3689076T2 (en) Burner operated with gaseous fuel.
CH671089A5 (en)
DE102019001348A1 (en) Exhaust gas control in the boiler
DE2454055A1 (en) Working fluid cooler used in power generating plant - has at least part of cooler constructed as plate-type heat exchangers in form of condensers
DE4329195A1 (en) Gas heating appliance and method for its operation

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19950508

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT DE

17Q First examination report despatched

Effective date: 19951206

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED

18R Application refused

Effective date: 19970601