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EP0243506A1 - Strahlungsrohrbrenner - Google Patents

Strahlungsrohrbrenner Download PDF

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Publication number
EP0243506A1
EP0243506A1 EP86906451A EP86906451A EP0243506A1 EP 0243506 A1 EP0243506 A1 EP 0243506A1 EP 86906451 A EP86906451 A EP 86906451A EP 86906451 A EP86906451 A EP 86906451A EP 0243506 A1 EP0243506 A1 EP 0243506A1
Authority
EP
European Patent Office
Prior art keywords
tube
burner
gas
combustion
water
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
EP86906451A
Other languages
English (en)
French (fr)
Other versions
EP0243506A4 (de
EP0243506B1 (de
Inventor
Yasushi Yoshida
Nobuyoshi Oomori
Kaneaki Hyodo
Kenji Atarashiya
Norihisa Shiraishi
Toshiyuki Hashime
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.)
JFE Steel Corp
Mitsubishi Heavy Industries Ltd
NIHON NENSHO SYSTEM KK
Original Assignee
Mitsubishi Heavy Industries Ltd
NIHON NENSHO SYSTEM KK
Kawasaki Steel Corp
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
Priority claimed from JP23701786A external-priority patent/JPS62242711A/ja
Priority claimed from JP23701686A external-priority patent/JPS62190311A/ja
Application filed by Mitsubishi Heavy Industries Ltd, NIHON NENSHO SYSTEM KK, Kawasaki Steel Corp filed Critical Mitsubishi Heavy Industries Ltd
Priority to AT86906451T priority Critical patent/ATE56520T1/de
Publication of EP0243506A1 publication Critical patent/EP0243506A1/de
Publication of EP0243506A4 publication Critical patent/EP0243506A4/de
Application granted granted Critical
Publication of EP0243506B1 publication Critical patent/EP0243506B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23D—BURNERS
    • F23D14/00—Burners for combustion of a gas, e.g. of a gas stored under pressure as a liquid
    • F23D14/20—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone
    • F23D14/22—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other
    • F23D14/24—Non-premix gas burners, i.e. in which gaseous fuel is mixed with combustion air on arrival at the combustion zone with separate air and gas feed ducts, e.g. with ducts running parallel or crossing each other at least one of the fluids being submitted to a swirling motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C6/00—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion
    • F23C6/04—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection
    • F23C6/045—Combustion apparatus characterised by the combination of two or more combustion chambers or combustion zones, e.g. for staged combustion in series connection with staged combustion in a single enclosure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C7/00—Combustion apparatus characterised by arrangements for air supply
    • F23C7/002—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion
    • F23C7/004—Combustion apparatus characterised by arrangements for air supply the air being submitted to a rotary or spinning motion using vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23C—METHODS OR APPARATUS FOR COMBUSTION USING FLUID FUEL OR SOLID FUEL SUSPENDED IN  A CARRIER GAS OR AIR 
    • F23C2203/00—Flame cooling methods otherwise than by staging or recirculation
    • F23C2203/30—Injection of tempering fluids

Definitions

  • This invention relates to a radiant tube burner in which a nozzle of a gas burner is coaxially placed in a combustion tube located in a radiant tube so that the burner can be moved in the axial direction, fuel gas issuing from the gas burner undergoes primary combustion by primary air supplied through the annular space between the gas burner and the combustion tube and further undergoes secondary combustion by secondary air supplied through the annular space between the combustion tube and the radiant tube and, more particularly to a radiant tube burner used for heat treatment furnaces or the like.
  • the newly invented burner is capable of reducing the amount of NOx contained in the exhaust gas discharged from the radiant tube.
  • a divergent flame type nozle is installed movably in the axial direction, while swirling vanes are provided on the outer periphery thereof and air dampers for adjusting the primary and the secondary air ratio is provided on the outside of a primary air supply tube.
  • Another object of the present invention is to provide a radiant tube burner in which the flame temperature is reduced by means of adding atomized water into the combustion flame, thereby making it possible to obtain low NOx, while high heat load combustion is going on in satisfactory and stable way owing to the two-stage combustion descirbed above.
  • a water spray nozzle is placed at the center of the divergent flame type nozzle, said nozzle being connected to an atomized water generator capable of supplying pressurized gas and additive water through an additive water transfer tube installed in the gas burner.
  • the atomized water generator is composed of a cylinder having a conical hole to be connected to the additive water transfer tube, a recessed disk having grooves for injecting pressurized gas and additive water thereinto and fitted to said cylinder and a housing for accommodating said cylinder and said disk.
  • the atomized water generator is connected to the exhaust gas pipe, while other parts remain the same as described in the second object.
  • low pressure fuel gas can be used as atomizing medium.
  • the water atomizer is connected to the fuel gas while other parts remain the same as described in the second object.
  • an exhaust gas introducing tube and a water out-flow nozzle are placed at the central portion of the divergent flame tube nozzle to utilize the velocity energy of low pressure exhaust gas to atomize the water supplied from the additive water transfer tube.
  • a gas burner 1 is coaxially placed with a combustion tube 2.
  • a divergent flame type nozzle 3a (see Figs. 2 and 3) is mounted at the end of the burner 1.
  • a primary air supply tube 5 joins the rear end of the combustion tube 2 to form an integral piece extending coaxially with the burner 1.
  • the primary air supply tube 5 has four rectangular ports 6 evenly spaced over the entire periphery thereof. The area of the inlet 6 can be changed by moving, with an operating rod 8 and a nut 9, a cylindrical air damper 7, into which the air supply tube 5 is loosely fitted.
  • Primary air swirling vanes 10 having an angle within the range from 15 to 60° are secured on a retaining tube 11 at the front end of said burner 1, as shown in Figs. 4 and 5.
  • the combustion tube 2 and the primary air supply tube 5 are coaxially housed in a radiant tube 12.
  • An air supply connection 13 is provided at the rear section of the radiant tube 12 in which the inlet ports 6 are located.
  • An end cover 14 closes rear ends of the primary air supply tube 5 and radiant tube 12.
  • the gas burner 1 is installed across said end cover 14 to extend rearward.
  • Reference numeral 15 designates a pilot burner.
  • the gas burner 1 extends movably through the end cover 14 in the axial direction within the range of the combustion tube 2 together with the pilot burner 15. Accordingly, the divergent flame type nozzle 3a is supported in the combustion tube 2 through the swirling vanes 10 so that the nozzle position is changeable.
  • the set position L of the divergent flame type nozzle 3a is changeable within the range from 100 to 500 mm.
  • the burner 1 is fixed by a bolt 16 attached on the end cover 14.
  • the gas supplied to the gas burner 1 through the connection 4 is ejected from the divergent flame type nozzle 3a into the combustion tube 2 at the maximum ejection angle of 60° and at the speed ranging from 10 to 100 m/sec.
  • the jetted fuel gas mixes with primary air C 1 which flows through the inlet 6 and is swirled by the swirling vanes 10 before being burnt in reduced primary combustion at the high heat load within the range from 500 x 10 4 kcal/m 3- h 1,000 x 10 4 kcal/m 3- h.
  • the primary combustion gas issues from the combustion tube 2 in the axial direction into the radiant tube 12 at the speed within the range from 10 to 30 m/sec.
  • Secondary air C 2 (90 to 50%) throttled by the air damper 7 to be at a required ratio with respect to the primary air C 1 (10 to 50%) is fed through the annular passage between the combustion tube 2 and the radiant tube 12 while cooling said combustion tube 2 at a speed slower than that of the primary combustion gas.
  • the secondary air C 2 flows along the inside of the radiant tube 12 due to the kinetic energy differential between the secondary air C 2 and the primary combustion gas, while making the secondary combustion occur in less concentrated way to prevent localized heating at the boundary against the primary combustion gas, thereby controlling the generation of NOx.
  • Test result with a 7 inch (17.5 cm) radiant tube burner according to the first embodiment of the present invention are as follows.
  • the heat rate was as much as 145,000 kcal/h while generally accepted limit had been 110,000 kcal/h with prior art.
  • NOx may be reduced to 80 through 150 ppm by changing the position of the nozzle 3a and the primary and the secondary air ratio.
  • tube temperature which is an important factor in the operation of radiant tube burners, it is possible to obtain uniform tube temperature due to the rotation of the flame, with the temperature change in the circumferential direction within 10°C. Further, the temperature difference in the axial direction between the maximum and the minimum in the furnace is made within 150°C, so that extended tube life can be expected.
  • Fig. 6 shows the maximum temperature of the radiant tube versus the amount of generation of NOx to explain the effect of NOx reduction according to the present invention. It is obvious that NOx can be reduced by approximately 30% compared with a prior art radiant tube burner.
  • Fig. 7 refer to the corresponding parts which are the same as illustrated in Fig. 1.
  • the gas burner 1 is placed coaxially with the combustion tube 2.
  • the divergent flame type nozzle 3a is mounted at the end of the burner 1.
  • the primary air supply tube 5 joins the rear end of the combustion tube 2 to form an integral piece extending coaxially with the burner 1.
  • the primary air supply tube 5 has four rectangular ports 6 evenly spaced over the entire periphery thereof.
  • the primary air swirling vanes 10 having an angle within the range from 15 to 60° are secured on a retaining tube (not shown) at the end of said burner 1.
  • the combustion tube 2 and the primary air supply tube 5 are coaxially housed in the radiant tube 12.
  • the primary air supply tube and the radiant tube are closed by the end cover through flanges respectively. Further, the gas burner 1 is installed across the end cover to extend rearward.
  • a water spray nozzle 18 communicating to an additive water transfer tube 17 placed in said gas burner 1 is provided at the center of the divergent flame type nozzle 3a and a multiple number of gas injection ports 14 communicating to the gas connection 4 are provided around said nozzle 18 as shown in Fig. 8. Further, an air supply connection 13 is connected to the rear section of the radiant tube 12. An atomized water generator 22 connected to the pressurized gas tube 20 and the additive water transfer tube 21 is at its rear end.
  • the atomized water generator 22 consists of a disk 24 having a circular recess 23 and a conical hole 25 with its diameter gradually decreasing from that corresponding to said recess. Further, a cylinder 26 having the same diameter as that of said disk 24 is coaxially fitted to said disk to form integrally with each other and then built in a housing 27. The disk 24 is surely pressed by a plug 28 and the cylinder 26 is connected to the additive water transfer tube 17. When the disk is fitted to the cylinder, an atomized water generating chamber 29 is formed.
  • Grooves 30 and 31 for introducing the pressurized gas and the additive water and communicating to said recess 23 in the tangential direction thereof are provided on one plain perpendicular to the center axis at the end face of the disk 24 near the cylinder 26. These grooves are connected to the pressurized gas supply tube 20 and the additive water supply tube 21_respectively.
  • the second embodiment of the present invention is a combination of the first embodiment and atomized water injection.
  • the fuel gas supplied to the gas burner 1 through the connection 4 is ejected from the divergent flame type nozzzle 3a into the combustion tube 2.
  • the jetted fuel gas mixes with the primary air C1 which flows through the inlet 6 and is swirled by the primary air swirling vanes 10 before being burnt in reduced primary combustion at the high heat load. Then, the primary combustion gas issues from the combustion tube 2 similarly to the first embodiment noted above.
  • the secondary air C 2 throttled by the air damper 7 as shown in Fig. 1 to be at a required ratio with respect to the primary air C 1 is fed through the annular passage between the combustion tube 2 and the radiant tube 12 while cooling said combustion tube 2 and then flows along the inside of the radiant tube.
  • the atomized water is obtained by the atomized water generator 18 as shown in Figs. 10 and 11, being injected from the water spray nozzle 18 located at the center of the divergent flame type nozzle 3a, thereby reducing the flame temperature to restrain the generation of NOx.
  • bubbles of the atomized water is sharply expanded to blow up through injection due to the differential pressure across the bubbles and the combustion tube. Since the thickness of the bubble is very thin, i.e., 0.1 ⁇ m or above, the pieces of the blown-up bubbles are very fine. Therefore, the fine water particles will quickly absorb the latent heat from the flame, thereby greatly reducing the generation of NOx due to the lowered flame temperature.
  • Figs. 12 and 13 refer to the corresponding parts which are the same as illustrated in Figs. 7 and 8. However, it differs from the second embodiment in such a point that the exhaust gas is ejected into the center of the fuel gas as atomizing medium while in the second embodiment water is used as atomizing medium.
  • the mechanism of the radiant tube burner in the third embodiment of the present invention is similar to that of the second embodiment with only such difference that the nozzle is constituted as a divergent flame type nozzle 3b, the description thereof will be omitted.
  • Fig. 14 shows a modification of the third embodiment of the present invention which is related to the atomizing system due to low pressure fuel gas.
  • the gas burner 1 is placed coaxially with the combustion tube 2.
  • the divergent flame type nozzle 3b is provided at the front end of the burner 1.
  • a water outflow nozzle 32 is provided at the center of the nozzle 3b.
  • gas swirling vanes 33 having an angle within the range from 15 to 40°.
  • the operating mechanism of the radiant tube burner of the modification of the third embodiment employing the atomizing system with low pressure fuel gas will be described in the following.
  • the gas G introduced into the gas burner 1 from the gas connection 4 is fed in the direction shown by the arrow to be swirled at high speed by the gas swirling vanes 33, while the water W introduced into the additive water transfer tube 17 (See Figs. 12 and 13) connected to an additive water connection port 36 is fed in the direction shown by an arrow to issue from the water outflow nozzle 32.
  • the water discharged from the water outflow nozzle is atomized by the velocity energy of the fuel gas.
  • the atomized water and fuel gas are sufficiently mixed with each other and the effect of water addition is greatly enhanced.
  • Figs. 14 and 15 show a modification of the third embodiment of the present invention which is related to the atomizing system with low pressure exhaust gas.
  • an exhaust gas introducing tube 34 for atomizing the water supplied from the water outflow nozzle 32 is placed at the center of the divergent flame type nozzle 3b.
  • the additive water transfer tube 17 is placed at the center of the introducing tube 34.
  • exhaust gas swirling vanes 35 having an angle within the range from 15 to 40°.
  • the exhaust gas G' is swirled at high speed by the exhaust gas swirling vanes 35 to atomize the water W discharged from the water outflow nozzle 32.
  • the atomized water is mixed with the fuel gas G (WG) supplied from the divergent flame type nozzle 3b by the high speed swirling flow of the exhaust gas. Therefore, the mixing of the exhaust gas and the fuel gas and that of the fuel gas and the atomized water occur rapidly to reduce the flame temperature by making the flame temperature uniform due to the combustion delay of the fuel gas and absorption of the latent heat by the atomized water, thereby greatly reducing the generation of NOx.
  • the radiant tube burner including two modifications of the third embodiment noted above has two ways of water atomizing system.
  • One is using pressurized gas (air, vapor and inert gas) within the range from 2 to 6 kg/cm 2 and the other is using low pressure gas (fuel gas, exhaust gas or the like) with the range from 300 to 1,000 mm AG.
  • NOx reduction rate by adding water in the radiant tube burner according to the present invention including the third and fourth embodiments is represented by the relation between the amount of additive water and the NOx reduction rate as shown in Fig. 16.
  • the radiant tube burner according to the present invention will give utmost effectiveness when used for a furnace in which direct exposure of workpieces to waste gas is not desirable. i.e., non-oxidation furnaces, heat treatment furnaces and the like utilizing atmospheric gas and indirect heating system in which workpieces and waste gas should not come in contact.
  • Applicable fields will include those industries such as metalworking industry, ceramics, glass industry, chemical industry, paper and fiber industry and food industry or the like.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Gas Burners (AREA)
EP86906451A 1985-10-31 1986-10-30 Strahlungsrohrbrenner Expired - Lifetime EP0243506B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86906451T ATE56520T1 (de) 1985-10-31 1986-10-30 Strahlungsrohrbrenner.

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP24293085 1985-10-31
JP242930/85 1985-10-31
JP26734885 1985-11-29
JP267348/85 1985-11-29
JP237017/86 1986-10-07
JP237016/86 1986-10-07
JP23701786A JPS62242711A (ja) 1985-11-29 1986-10-07 ラジアントチユ−ブバ−ナ
JP23701686A JPS62190311A (ja) 1985-10-31 1986-10-07 ラジアントチユ−ブバ−ナ

Publications (3)

Publication Number Publication Date
EP0243506A1 true EP0243506A1 (de) 1987-11-04
EP0243506A4 EP0243506A4 (de) 1989-01-24
EP0243506B1 EP0243506B1 (de) 1990-09-12

Family

ID=27477683

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86906451A Expired - Lifetime EP0243506B1 (de) 1985-10-31 1986-10-30 Strahlungsrohrbrenner

Country Status (4)

Country Link
EP (1) EP0243506B1 (de)
AU (1) AU573109B2 (de)
DE (1) DE3674198D1 (de)
WO (1) WO1987002756A1 (de)

Cited By (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0435735A1 (de) * 1989-12-28 1991-07-03 Institut Français du Pétrole Industriebrenner für flüssige Brennstoffe mit niedrigen Stickstoffoxidemissionen zum Erzeugen von mehreren elementaren Flammen und seine Anwendung
EP0455459A2 (de) * 1990-05-01 1991-11-06 General Electric Company Verbrennungsverfahren und -vorrichtung
WO1992005390A1 (en) * 1990-09-14 1992-04-02 Solar Turbines Incorporated A gaseous fuel injector
EP0543324A2 (de) * 1991-11-22 1993-05-26 Aichelin Gmbh Brenner für Industrieöfen
US5513981A (en) * 1991-11-22 1996-05-07 Aichelin Gmbh Burner with variable volume combination chamber
WO1998023901A1 (en) * 1996-11-26 1998-06-04 Teollisuuslämpö Oy Combustion apparatus for gases
EP0849526A3 (de) * 1996-12-20 1999-07-07 IPEG S.p.A. dell'Ing. Mauro Poppi Brenner mit hoher Wärmeabgabe
EP1422473A1 (de) * 2002-11-21 2004-05-26 Hauck Manufacturing Company U-Rohr Diffusionsflammen-Brenneranordnung mit einzigartiger Flammenstabilisierung
ITVE20110066A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.
ITVE20110067A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5560104A (en) * 1978-10-30 1980-05-07 Nippon Steel Corp Two-stage combustion burner for radiant tube
EP0117029A1 (de) * 1983-01-18 1984-08-29 W.B. Combustion Limited Einfach endendes Strahlungsheizrohr

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5218929B2 (de) * 1973-01-18 1977-05-25
JPS5070929A (de) * 1973-10-24 1975-06-12
JPS5240451B2 (de) * 1974-02-06 1977-10-12
JPS5229007B2 (de) * 1974-05-27 1977-07-29
JPS5156028A (ja) * 1974-11-12 1976-05-17 Nippon Kokan Kk Chitsusosankabutsuyokuseihoho
JPS5221036U (de) * 1975-08-02 1977-02-15
JPS5222132A (en) * 1975-08-07 1977-02-19 Daido Steel Co Ltd Burner combustion method and apparatus with addition of water
JPS57166410A (en) * 1981-04-03 1982-10-13 Maruzen Eng Kk Water injection combustion method and water injection combustion burner
JPS5942427U (ja) * 1982-09-10 1984-03-19 東京瓦斯株式会社 二重管式輻射管
JPS60218519A (ja) * 1984-04-13 1985-11-01 Nippon Nenshiyou Syst Kk 混焼用バ−ナ装置

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5560104A (en) * 1978-10-30 1980-05-07 Nippon Steel Corp Two-stage combustion burner for radiant tube
EP0117029A1 (de) * 1983-01-18 1984-08-29 W.B. Combustion Limited Einfach endendes Strahlungsheizrohr

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, vol. 4, no. 102 (M-22)[584], 22nd July 1980; & JP-A-55 060 104 (SHIN NIPPON SEITETSU K.K.) 07-05-1980 *
See also references of WO8702756A1 *

Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0435735A1 (de) * 1989-12-28 1991-07-03 Institut Français du Pétrole Industriebrenner für flüssige Brennstoffe mit niedrigen Stickstoffoxidemissionen zum Erzeugen von mehreren elementaren Flammen und seine Anwendung
FR2656676A1 (fr) * 1989-12-28 1991-07-05 Inst Francais Du Petrole Bruleur industriel a combustible liquide a faible emission d'oxyde d'azote, ledit bruleur generant plusieurs flammes elementaires et son utilisation.
EP0455459A2 (de) * 1990-05-01 1991-11-06 General Electric Company Verbrennungsverfahren und -vorrichtung
EP0455459A3 (en) * 1990-05-01 1992-04-08 General Electric Company Combustion method and apparatus
WO1992005390A1 (en) * 1990-09-14 1992-04-02 Solar Turbines Incorporated A gaseous fuel injector
EP0543324A3 (en) * 1991-11-22 1993-09-08 Aichelin Gmbh Burner for industrial furnaces
EP0543324A2 (de) * 1991-11-22 1993-05-26 Aichelin Gmbh Brenner für Industrieöfen
US5513981A (en) * 1991-11-22 1996-05-07 Aichelin Gmbh Burner with variable volume combination chamber
WO1998023901A1 (en) * 1996-11-26 1998-06-04 Teollisuuslämpö Oy Combustion apparatus for gases
EP0849526A3 (de) * 1996-12-20 1999-07-07 IPEG S.p.A. dell'Ing. Mauro Poppi Brenner mit hoher Wärmeabgabe
US6872070B2 (en) 2001-05-10 2005-03-29 Hauck Manufacturing Company U-tube diffusion flame burner assembly having unique flame stabilization
EP1422473A1 (de) * 2002-11-21 2004-05-26 Hauck Manufacturing Company U-Rohr Diffusionsflammen-Brenneranordnung mit einzigartiger Flammenstabilisierung
ITVE20110066A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.
ITVE20110067A1 (it) * 2011-10-06 2013-04-07 Foinox S P A Scambiatore di calore per apparecchi di cottura a gas.

Also Published As

Publication number Publication date
AU573109B2 (en) 1988-05-26
WO1987002756A1 (en) 1987-05-07
EP0243506A4 (de) 1989-01-24
AU6594086A (en) 1987-05-19
EP0243506B1 (de) 1990-09-12
DE3674198D1 (de) 1990-10-18

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