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WO1994009326A1 - Dispositif de melange et d'echange de chaleur monte sur des chaudieres a condensation - Google Patents

Dispositif de melange et d'echange de chaleur monte sur des chaudieres a condensation Download PDF

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Publication number
WO1994009326A1
WO1994009326A1 PCT/CZ1993/000025 CZ9300025W WO9409326A1 WO 1994009326 A1 WO1994009326 A1 WO 1994009326A1 CZ 9300025 W CZ9300025 W CZ 9300025W WO 9409326 A1 WO9409326 A1 WO 9409326A1
Authority
WO
WIPO (PCT)
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
PCT/CZ1993/000025
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German (de)
English (en)
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
Priority to EP93921777A priority Critical patent/EP0663056A1/fr
Publication of WO1994009326A1 publication Critical patent/WO1994009326A1/fr
Anticipated expiration legal-status Critical
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
    • 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.

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  • 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

L'invention concerne un dispositif composé d'une chambre de combustion (12) et d'une chambre de mélange (6) située sur sa surface supérieure, ainsi que d'un échangeur de chaleur adjoint à la partie inférieure de la chambre de combustion. Le mélangeur (1) est placé entre les conduites d'amené d'air et de gaz et la chambre de mélange (6) et est réalisé avec une chambre d'enceinte (3). Au moins trois tuyères périphériques (5) pénétrant de manière symétrique sont disposées en anneau à proximité du diamètre intérieur critique du mélangeur. L'entrée de la chambre de mélange (6) est raccordée à la sortie du mélangeur, la chambre de mélange étant composé du secteur de passage (8) et du secteur de conduite d'amenée (7), et comprenant au moins une paroi partielle d'alimentation (10) et une paroi de section (100). Un tuyau à ailettes (14), dont une extrémité se trouve dans la chambre de combustion (12) et dont l'autre se termine dans le fond du canal descendant (15), est situé dans le fond de la chambre de combustion (12). Un canal descendant (17) situé entre la paroi du canal ascendant et la paroi de la chambre de combustion est relié au mélangeur (1) par mise en communication du canal de jonction (22) avec un ventilateur (21).
PCT/CZ1993/000025 1992-10-09 1993-10-11 Dispositif de melange et d'echange de chaleur monte sur des chaudieres a condensation Ceased WO1994009326A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP93921777A EP0663056A1 (fr) 1992-10-09 1993-10-11 Dispositif de melange et d'echange de chaleur monte sur des chaudieres a condensation

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CS923097A CZ278788B6 (en) 1992-10-09 1992-10-09 Combustion system of heating gas condensation sets
CSPV3097-92 1992-10-09

Publications (1)

Publication Number Publication Date
WO1994009326A1 true WO1994009326A1 (fr) 1994-04-28

Family

ID=5370068

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/CZ1993/000025 Ceased WO1994009326A1 (fr) 1992-10-09 1993-10-11 Dispositif de melange et d'echange de chaleur monte sur des chaudieres a condensation

Country Status (4)

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

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0846916A3 (fr) * 1996-12-06 1999-02-10 SIT LA PRECISA S.r.l. Dispositif de mélange air-gaz notamment pour brûleurs à air soufflé
EP0896192A3 (fr) * 1997-08-05 1999-11-10 Karl Dungs GmbH & Co. Dispositif d'admission du gaz combustible pour un brûleur à prémélange
EP0905457A3 (fr) * 1997-09-29 2001-04-11 FERROLI S.p.A. Chaudière à condensation avec prémélange pour systèmes mixtes
US7108838B2 (en) 2003-10-30 2006-09-19 Conocophillips Company Feed mixer for a partial oxidation reactor

Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2700786A1 (de) * 1977-01-11 1978-07-20 Rappold & Co Gmbh Hermann Keramischer brenner, insbesondere brenner fuer winderhitzer
DE3312563A1 (de) * 1983-04-07 1984-10-11 Gosudarstvennyj proektnyj i naučno-issledovatel'skij institut nikelevo-kobal'tovoj promyšlennosti, Leningrad Vorrichtung zum verbrennen von brennstoff und zum zufuehren der verbrennungsprodukte in eine schmelze
EP0373027A1 (fr) * 1988-12-02 1990-06-13 GEMINOX, Société Anonyme Chaudière à condensation pour chauffage à fluide caloporteur
DE3842463A1 (de) * 1987-09-25 1990-06-21 Wetering Gemeenschappelijk Bez Heizgeraet
EP0415008A1 (fr) * 1989-08-12 1991-03-06 Klöckner Wärmetechnik Gmbh Zweigniederlassung Hechingen Procédé de combustion dans un brûleur à gaz
US4998508A (en) * 1988-05-20 1991-03-12 Northern Engineering Industries Plc Condensing type boilers
DE9213594U1 (de) * 1992-10-14 1993-03-18 Marek, Rudolf, 2000 Hamburg Brenner für Heizgeräte und Heizungsanlagen

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2700786A1 (de) * 1977-01-11 1978-07-20 Rappold & Co Gmbh Hermann Keramischer brenner, insbesondere brenner fuer winderhitzer
DE3312563A1 (de) * 1983-04-07 1984-10-11 Gosudarstvennyj proektnyj i naučno-issledovatel'skij institut nikelevo-kobal'tovoj promyšlennosti, Leningrad Vorrichtung zum verbrennen von brennstoff und zum zufuehren der verbrennungsprodukte in eine schmelze
DE3842463A1 (de) * 1987-09-25 1990-06-21 Wetering Gemeenschappelijk Bez Heizgeraet
US4998508A (en) * 1988-05-20 1991-03-12 Northern Engineering Industries Plc Condensing type boilers
EP0373027A1 (fr) * 1988-12-02 1990-06-13 GEMINOX, Société Anonyme Chaudière à condensation pour chauffage à fluide caloporteur
EP0415008A1 (fr) * 1989-08-12 1991-03-06 Klöckner Wärmetechnik Gmbh Zweigniederlassung Hechingen Procédé de combustion dans un brûleur à gaz
DE9213594U1 (de) * 1992-10-14 1993-03-18 Marek, Rudolf, 2000 Hamburg Brenner für Heizgeräte und Heizungsanlagen

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of EP0663056A1 *

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0846916A3 (fr) * 1996-12-06 1999-02-10 SIT LA PRECISA S.r.l. Dispositif de mélange air-gaz notamment pour brûleurs à air soufflé
EP0896192A3 (fr) * 1997-08-05 1999-11-10 Karl Dungs GmbH & Co. Dispositif d'admission du gaz combustible pour un brûleur à prémélange
EP0905457A3 (fr) * 1997-09-29 2001-04-11 FERROLI S.p.A. Chaudière à condensation avec prémélange pour systèmes mixtes
US7108838B2 (en) 2003-10-30 2006-09-19 Conocophillips Company Feed mixer for a partial oxidation reactor

Also Published As

Publication number Publication date
CZ278788B6 (en) 1994-06-15
SK277937B6 (en) 1995-08-09
CZ309792A3 (en) 1994-04-13
SK309792A3 (en) 1995-08-09
EP0663056A1 (fr) 1995-07-19

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