EP1387985B1 - Bruleurs a gaz a premelange sans condensation - Google Patents

Bruleurs a gaz a premelange sans condensation Download PDF

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Publication number
EP1387985B1
EP1387985B1 EP02732670A EP02732670A EP1387985B1 EP 1387985 B1 EP1387985 B1 EP 1387985B1 EP 02732670 A EP02732670 A EP 02732670A EP 02732670 A EP02732670 A EP 02732670A EP 1387985 B1 EP1387985 B1 EP 1387985B1
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EP
European Patent Office
Prior art keywords
premix
burner
gas
combustible gas
valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP02732670A
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German (de)
English (en)
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EP1387985A1 (fr
Inventor
Dirk Ten Hoeve
Arnold Van Wijk
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Bekaert Combustion Technology BV
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Bekaert Combustion Technology BV
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Priority to EP02732670A priority Critical patent/EP1387985B1/fr
Publication of EP1387985A1 publication Critical patent/EP1387985A1/fr
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    • 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
    • F24H9/0005—Details for water heaters
    • F24H9/0036—Dispositions against condensation of combustion products
    • 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
    • F23C7/02—Disposition of air supply not passing through burner
    • 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
    • F23D14/60—Devices for simultaneous control of gas and combustion air
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23L—SUPPLYING AIR OR NON-COMBUSTIBLE LIQUIDS OR GASES TO COMBUSTION APPARATUS IN GENERAL ; VALVES OR DAMPERS SPECIALLY ADAPTED FOR CONTROLLING AIR SUPPLY OR DRAUGHT IN COMBUSTION APPARATUS; INDUCING DRAUGHT IN COMBUSTION APPARATUS; TOPS FOR CHIMNEYS OR VENTILATING SHAFTS; TERMINALS FOR FLUES
    • F23L17/00—Inducing draught; Tops for chimneys or ventilating shafts; Terminals for flues
    • F23L17/16—Induction apparatus, e.g. steam jet, acting on combustion products beyond the fire
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F23—COMBUSTION APPARATUS; COMBUSTION PROCESSES
    • F23J—REMOVAL OR TREATMENT OF COMBUSTION PRODUCTS OR COMBUSTION RESIDUES; FLUES 
    • F23J2900/00—Special arrangements for conducting or purifying combustion fumes; Treatment of fumes or ashes
    • F23J2900/13001—Preventing or reducing corrosion in chimneys

Definitions

  • the present invention relates to non condensing premix gas burners and methods to operate non condensing premix gas burners.
  • Premix gas burners are well known in the art.
  • An advantage of premix burners is that low NOx and CO content is measured in the exhaust gasses and a relatively high efficiency may be obtained. The latter especially when the premix burner is fired using a lower firing load.
  • Pn the maximum firing load
  • the premix combustible gas mixture may be provided to the burner membrane in the premix burner in many different ways. Many improvements were made to the operation of such premix burners, e.g. to reduce the 'vibration' of the flame front by splitting the air stream in two parts, being separately conducted to the flame front as explained in US4752213 .
  • premix burners are that, when the firing load (or firing rate) is lower, the exhaust gasses are even more cooled, so the efficiency increases, when such premix burners are 'modulated' towards lower firing rates.
  • the exhaust gasses are cooled to a lower temperature when being fired at lower firing rates, the exhaust gasses may condense. Such condensation occurs depending on the firing rate and the temperature of the heat exchanging unit. Usually, condensation may occur at firing rates of less than 40%. Condensation may also occur in the exhaust system.
  • EP 0614045 as well as EP 0866270 , described that the dewing point of the flue gas can be lowered by delivery of cool air to the chimney of the boiler or to the burning zone, respectively.
  • US 4087962 describes a combustor wherein low NOx emissions are attained by cooling of the flame by mixing secondary air, which inevitably also lowers the dewing point of the flue gases.
  • the present invention has as an object to provide a method for operating non-condensing premix gas burners, firing premix combustible gas at lower firing rates, in the mean time reducing the dew point of the exhaust gas of the premix gas burner and obtaining an required efficiency at this firing rate, according to EN297, being more than 84+2*log(Pn) at full load Pn or "maximum firing rate” and preferably more than 84+3*log(Pn) at part load, being 30% of Pn according to EN 297. It is further an object of the present invention to provide a premix gas burner, being adapted to operated using such method of reducing the dew point of the exhaust gas.
  • a method for operating non-condensing premix gas burners comprises the step of draughting a total volume of exhaust gas Vtotal through the housing of the non-condensing premix gas burner.
  • a forced draught is to be provided.
  • a draughting device such as a fan or ventilator in the chimney or exhaust evacuation system of the burner provides this forced draught.
  • the air for both premix mixture and secondary air, is blown into the burner house by an air supply device in stead of a draughting device. The air is then supplied by e.g. a fan of ventilator.
  • the method further comprises the step of combusting an amount of premix combustible gas.
  • the amount is determined by the thermal energy, which is to be delivered by the non-condensing premix gas burner at that moment.
  • This combustion operation provides an amount of flue gas Vp, which is provided in the burner house and which will be cooled on the heat exchanging device installed inside this burner house, between the burner membrane, where the combustion takes place, and the exhaust evacuation system.
  • the volume Vp may vary between a maximum volume Vpmax and a minimum volume Vpmin.
  • the combustion is executed at a firing rate FR of 100%, or, in other words, at maximum firing rate FRmax or at full load Pn.
  • the ratio air/gas of the premix combustible gas is set to a fixed value. Usually, an air excess in the range of 10% to 40%, most usually 30% of air excess is set, independent from the volume of premix combustible gas which is combusted. Such a. fixed ratio of air/gas of the premix combustible gas applied provides a flue gas which has a set dew point Tdp at an operational pressure in the burner house.
  • FR1 is larger than FRmin, and usually larger than 40%. This means that for presently known premx burners, the firing rate is to be at least Frmin, thus usually more than 40% of the maximum firing rate FR max. Modulation at firing rates usually lower than 40% of the maximum firing rate, is not recommended due to the risk on condensing of the flue gas.
  • the premix combustible mixture used sets Tdp.
  • a combustible mixture comprising no air excess has a dew point of 58°C.
  • An air excess of 30% causes a dew point of 53°C, whereas air excess of 100% causes a dew point of 48°C.
  • a certain volume of secondary air Vs is introduced in the burner house. This is done in such a way that the main part of the secondary air does not take part in the combustion process. Vs and Vp are brought together to form the total exhaust gas volume Vtotal., said exhaust gas having a new dew point Tdtotal.
  • the introduction of relatively cold secondary air causes the dew point of Vtotal to be less than Tdp.
  • the method further comprises the step of determining the level of the new dew point Tdtotal by tuning the ratio Rsp, Rsp being Vs divided by Vp.
  • Vs The amount of Vs is adjusted in such a way that, for all applicable firing rates, the condensation of the exhaust gas is avoided at the surface of the heat exchanging unit, even when this heat exchanging unit is at its lowest temperature applicable. Since Vs does not take part in the combustion reaction, no major changes in Nox or CO production was noticed, as compared to operating without secondary air supply. One understands that Vtotal substantially equals Vp+Vs.
  • the volume of secondary air Vs added at a FR less than FR will be set in such a way that for FR ⁇ FR1, the exhaust gas volume Vtotal cannot be cooled to its dew point Tdtotal not even under the circumstance that the heat exchanging unit would be at its lowest temperature Tmin possible.
  • the lowest temperature to which the total exhaust gas volume is cooled by the heat exchanging unit is Tdtotal+20K.
  • the exhaust gas Vtotal may be cooled to a temperature Texhaust, which is higher than its dew point Tdtotal, but which is lower than the dew point Tdp.
  • Vs added at a FR less than FR1 will be restricted in such a way that the efficiency will be more than 84+2*log(Pn) or even more than 84+3*log(Pn).
  • An efficiency of more than 84+3*log(Pn) is preferred when FR is equal or smaller than 30% of the maximum firing rate FR (which is the equivalent of the part load of 30% of Pn according to EN279).
  • the ratio Rsp is to increase for decreasing FR in the range FRmin ⁇ FR ⁇ FR1.
  • the tuning of Rsp determines the dew point Tdtotal.
  • the method of firing a premix burner as subject of the invention enables to modulate a premix burner in a range which is larger as known in the art, still at an acceptable efficiency.
  • Vtotal1 Vp1+Vs1 over the heat exchanger.
  • This volume Vtotal1 will be cooled down, comparably as in the operating situation without secondary air.
  • the mixture of flue gas and secondary air will not condense yet, since the total amount of H2O in this volume is lower as compared to the water content of the flue gas when no secondary air was supplied.
  • relatively cold secondary air was added in the premix gas burner housing, the efficiency of the heat transfer of Vtotal on the heat exchanging unit was reduced to some extend. Depending on the ratio Rsp, this reduction of efficiency however is limited according to Rsp.
  • the Rsp decreases for increasing FR in the range FR ⁇ FR1.
  • FR> FR1 there is even no need for secondary air, since there is no risk for condensing the flue gasses.
  • Vs may even be 0 for this FR range.
  • FR is decreased to smaller firing rates of FR ⁇ FR1, e.g.
  • the Rsp is increased.
  • the Rsp changes gradually, with changing FR, in the range of 0 to 2.5.
  • the Rsp is preferably more than 1, e.g. more than 1.5 or even more than 2 such as 2.5.
  • the Rsp is preferably less than 1, or even lower than 0.5 such as 0.42.
  • a premix burner comprises a burner house, a burner membrane, a premix combustible gas inlet and a premix combustible gas mixing unit.
  • the premix combustible gas mixing unit provides premix combustible gas to the burner membrane via the premix combustible gas inlet.
  • a premix burner as subject of the invention being operated according to the present invention, comprising extra means to enable secondary air to enter the burner house, e.g. by calibrated apertures in the burner house and comprises means to adjust the Rsp according to the possible firing rates.
  • the means to provide secondary air to the premix gas burner are located sufficiently remote from the burner membrane, preferably a distance of more than 30mm is taken into account.
  • the means being apertures, these apertures are located substantially above the burner membrane, e.g. at a height, being more than 10mm or even more than 15mm above the burner membrane.
  • a barrier encircling the burner membrane and extending above the burner membrane is provided. This barrier preferably extends more than 10 mm or even more than 15mm above the burner membrane. The secondary air cannot flow directly from the apertures, which may be located closer tot he burner membrane, to the flame front at the burner membrane, but this secondary air has to flow above the barrier to meet the flue gas.
  • a premix burner as subject of the invention further comprises different elements.
  • a premix combustible gas mixing unit preferably a ventury system, is mounted to the premix combustible gas inlet.
  • the premix combustible gas is conducted to the burner membrane.
  • a mixing chamber and/or a gas diffuser system is present between premix combustible gas inlet and burner membrane.
  • the premix gas is combusted. This combustion side of the burner membrane is pointing inwards the burner house.
  • a draughting unit e.g. a fan or ventilator, may be mounted to the exhaust evacuation system and evacuates a certain amount of gas volume out of the burner house.
  • a heat exchanging unit is mounted between the exhaust evacuation system and the burner membrane.
  • the gas volume evacuated by the draughting device is forced to flow over or through the heat exchanging unit.
  • a premix burner further may comprise a certain number of slots or apertures in its burner house and a valve, installed in the premix combustible gas inlet, which can change the opening of the premix combustible gas inlet by opening or closing.
  • This valve is hereafter referred to as "premix valve”.
  • the dimensions of the apertures or slots are calibrated and defined, together with the closing characteristics of the premix valve, in such a way that the premix burner is operated according to the method as subject of the invention.
  • a first type of premix burner is equipped with a draughting device, of which the volume of draughted gas is adjusted according to the required firing rate at a certain moment.
  • a fan with adjustable motor speed may be used.
  • Due to the draughting device a depression is provided in the burner housing.
  • a premix valve is installed, which opens or closes according to the depression, which is applied at the downstream side of the valve.
  • the force, used to close the valve when the depression is decreased may be e.g. the gravity force or caused by a spring system.
  • a gas inlet duct is used to provide combustion gas to the premix combustible gas mixing unit, preferably a ventury system.
  • a valve controlling the amount of gas being supplied to the premix combustible gas mixing unit is used. This valve is hereafter referred to as "gas valve”.
  • This gas valve is controlled in such a way that, according to the volume passing through the premix combustible gas mixing inlet, an amount of gas is supplied to the premix combustible gas mixing unit to ensure the correct ratio air/gas of the premix combustible gas mixture. Usually, 30% of excess air is provided.
  • This volume Vtotal will be cooled on the heat exchanging unit, being at a temperature higher or equal to Tmin, to a temperature Texhaust.
  • An efficiency of more than 84+3*log(Pn) is preferred when FR is equal or smaller than 30% of the maximum firing rate FR .
  • a second type of premix burner is equipped with a draughting device, of which the volume of draughted gas is constant, independent to the required firing rate at a certain moment.
  • a fan with constant motor speed may be used. Due to the draughting device, a depression is provided in the burner housing.
  • a premix valve is installed, which opens or closes according to the required firing rate.
  • the force, used to control the valve when the depression is decreased, may be e.g. a stepper motor.
  • a gas inlet duct is used to provide combustion gas to the premix combustible gas mixing unit, preferably a ventury system.
  • a valve controlling the amount of gas being supplied to the premix combustible gas mixing unit is used.
  • This valve is hereafter referred to as "gas valve”.
  • This gas valve is controlled in such a way that, according to the volume of gas passing through the premix combustible gas mixing inlet, an amount of gas is supplied to the premix combustible gas mixing unit to ensure the correct ratio air/gas of the premix combustible gas mixture. Usually, 30% of excess air is provided.
  • the draughting device causing a certain depression in the burner house, draughts a volume Vtotal through the burner house.
  • the surface of the premix combustible gas mixing inlet will be set.
  • a certain amount of premix combustible gas mixture will be combusted providing Vp.
  • This volume Vtotal will be cooled on the heat exchanging unit, being at a temperature higher or equal to Tmin, to a temperature Texhaust.
  • An efficiency of more than 84+3*log(Pn) is preferred when FR is equal or smaller than 30% of the maximum firing rate FR .
  • the premix valve When a lower firing rate FR is required, the premix valve will close due to the changing in setting of the valve. The surface of the premix combustible gas mixing inlet decreases, while the surface of the additional apertures for secondary air supply stay constant. Therefor Vp will decrease proportionally whereas Vs, due to the increasing depression, will increase. As a result Rsp increases.
  • the Rsp is adjusted to the range of 1 to 1.5 .
  • the exhaust gas may be cooled to a temperature Texhaust ⁇ Tdp, Tdp being the dew point of the flue gas.
  • the premix valve may be adjusted directly depending on the firing load required, However, the valve may be adjusted indirectly, depending on a certain volume of gas, which is provided via the gas valve. This gas valve is adjusted according to the FR required. After the gas valve, or in the premix combustible gas inlet, the obtained pressure is measured. According to this pressure, the premix valve is opened, in order to provide a premix combustible gas mixture, having the correct ratio air/gas.
  • the premix valve may be controlled by e.g. a spring system or a stepper motor.
  • a control unit may control the opening or closing of the premix valve via this spring system or stepper motor.
  • An alternative premix gas burner uses the same elements as of a premix gas burner as described above, but the draughting device is not present.
  • the air for both premix mixture and secondary air, is blown into the burner house by an air supply device in stead of draughted into it by a draughting device.
  • the air is supplied by e.g. a fan of ventilator to the apertures or slots and to the gas mixing unit.
  • a premix burner as subject of the invention is schematically shown in FIGURE 1 .
  • a premix gas burner comprises a burner house 101, an exhaust evacuation system 102, in which a drafting device 103 is comprised, and a heat exchanging unit 104.
  • the premix gas burner further comprises a burner membrane 105, to which a premix combustible gas mixture is provided via a premix combustible gas inlet 106.
  • Premix combustible gas is mixed in the premix combustible gas mixing unit 107, being e.g. a ventury system.
  • a mixing and diffusion chamber 108 may be installed between premix combustible gas inlet 106 and burner membrane 105.
  • the burner house comprises apertures 109 and a premix valve 110.
  • the draughting device 103 forces a total volume of exhaust gas into the exhaust evacuation system 102 (as indicated with arrow 120), draughting this volume through the heat exchanging unit 104.
  • Controlling device 130 which e.g. controls the speed of the draughting device, in case the device is a fan, in function of the firing rate required, controls this volume the volume Vtotal is partially draught through the apertures 109, and partially through the premix combustible gas mixing unit 107.
  • a volume of secondary air Vs is draught through the apertures 109 as indicated with arrow 121.
  • the amount of air, draught through the premix combustible air mixing unit 107 (as indicated with arrow 122) requires a certain volume of gas, to be supplied and mixed with this air in order to provide the premix combustible gas.
  • This gas volume is provided via gas inlet 111.
  • this gas volume is controlled via a control device 112, e.g. a manometer, measuring the pressure in the premix combustible gas mixing unit at point 113.
  • the gas valve 114 is opened or closed.
  • the premix combustible gas mixture is provided to and burned at the burner membrane 105, providing a volume of flue gas Vp as indicated with arrow 123.
  • the volume of secondary air which main part does not take part in the combustion reaction, is brought together with the flue gas volmume Vp in the burner house reducing the dew point of the exhaust gas as compared to the dew point of the flue gas.
  • the premix valve 110 will open or close to a certain extend.
  • This premix valve may be closed by e.g. gravity force, or this force may be provided by e.g. a spring.the level of opening or closing of the premix valve 110 according to the volume Vtotal, controls the ratio Rsp, being Vs/Vp.
  • FIGURE 2 An alternative premix gas burner is shown in FIGURE 2 .
  • the burner functions in an identical way as shown in FIGURE 1 , except that this burner does not comprise a draughting device.
  • the burner comprises an air supply device 115, which provided a certain amount of air to apertures 109 and to the premix combustible gas mixing unit 107.
  • the amount of air is controlled by a control device 130, which controls the amount of air supplied to the burner as indicated with arrow 124.
  • FIGURE 3 An alternative premix gas burner is shown in FIGURE 3 .
  • the burner functions in an identical way as shown in FIGURE 1 , except that the draught device 103 constantly draughts the same volume of exhaust gas.
  • the gas valve 114 is controlled by a control device, which adjusts the opening of the gas valve according to the required firing rate.
  • a control device 116 e.g. a manometer, controls the setting of the premix valve 110.
  • the opening of the premix valve will control the ratio Rsp, being Vs/Vp.
  • FIGURE 4 Another alternative premix gas burner is shown in FIGURE 4 .
  • the burner functions in an identical way as shown in FIGURE 1 , except that the premix valve 110 is controlled directly by a control device 130 and that the draughting device draughts a constant exhaust gas volume.
  • the premix valve 110 is opened or closed according to the required firing rate, e.g. by using a stepper motor.
  • the opening of the premix valve will control the ratio Rsp, being VsIVp.
  • FIGURE 5 Another alternative premix gas burner as subject of the invention is shown in FIGURE 5 .
  • the apertures 109, providing secondary air to the premix gas burner, are located significantly remote and above the burner membrane at a height 501 of at least 15mm.
  • the secondary air which is flowing in the as indicated with arrow 121, does not take part in the combustion reaction.
  • FIGURE 6 Another alternative premix gas burner as subject of the invention is shown in FIGURE 6 .
  • the apertures 109, providing secondary air to the premix gas burner, are located closer to the burner membrane but around the burner membrane, a barrier 601 (e.g. a metal flange) is provided.
  • This barrier 601 extends at least over a height 602 of 15mm above the burner membrane 105.at the time the secondary air, flowing in as indicated with arrow 121, reaches the flue gas above the barrier, the combustion reaction has already been completed.

Claims (12)

  1. Procédé pour diminuer le point de rosée du gaz d'échappement d'un brûleur à prémélange, ledit procédé comprenant les étapes suivantes :
    - fournir un volume de gaz de fumée Vp en brûlant un mélange de gaz combustible de prémélange, ledit gaz de fumée ayant un point de rosée Tdp ;
    - introduire un volume d'air secondaire Vs dans le boîtier dudit brûleur, la majeure partie dudit air secondaire ne participant pas à la combustion dudit mélange de gaz combustible de prémélange ;
    - combiner ledit volume de gaz de fumée Vp et ledit volume d'air secondaire pour former un volume total de gaz d'échappement Vtotal, ledit gaz d'échappement ayant un nouveau point de rosée Tdtotal, qui est inférieur audit point de rosée Tdp dudit gaz de fumée,
    - déterminer le niveau dudit nouveau point de rosée Tdtotal en ajustant le rapport Rsp, Rsp étant Vs divisé par Vp.
  2. Procédé selon la revendication 1, comprenant en outre l'étape consistant à refroidir ledit gaz d'échappement sur une unité d'échange de chaleur.
  3. Procédé selon la revendication 2, dans lequel ledit refroidissement est effectué avec une efficacité de plus de 84+2*log(Pn), Pn étant la charge totale dudit brûleur à gaz à prémélange.
  4. Procédé selon la revendication 2 ou 3, dans lequel ledit refroidissement est effectué avec une efficacité de plus de 84+3*log(Pn), lorsque ledit brûleur à prémélange fonctionne à une charge de combustion de 30% de Pn.
  5. Procédé selon les revendications 2 à 4, dans lequel ledit gaz d'échappement est refroidi à une température T inférieure à Tdp, ladite T étant supérieure à Tdtotal.
  6. Brûleur à prémélange pour mettre en oeuvre un procédé de fonctionnement selon l'une quelconque des revendications précédentes, ledit brûleur comprenant un boîtier de brûleur (101), une membrane de brûleur (105), une entrée de gaz combustible de prémélange (106), et une unité de mélange de gaz combustible de prémélange (107), ladite unité de mélange de gaz combustible de prémélange (107) fournissant du gaz combustible de prémélange à ladite membrane de brûleur (105) par le biais de ladite entrée de gaz combustible de prémélange (106), ledit boîtier de brûleur (101) comprenant des ouvertures (109) pour introduire un volume d'air secondaire Vs, caractérisé en ce que ledit brûleur comprend une soupape de prémélange (110), ladite soupape de prémélange (110) étant installée entre l'unité de mélange de gaz combustible de prémélange (107) et l'entrée de gaz combustible de prémélange (106), ladite soupape de prémélange (110) contrôlant le rapport Rsp, ledit Rsp étant Vs divisé par Vp.
  7. Brûleur à prémélange selon la revendication 6, dans lequel ladite soupape de prémélange (110) est fermée par la force de gravité.
  8. Brûleur à prémélange selon la revendication 6, dans lequel ladite soupape de prémélange (110) est commandée par un système de ressort.
  9. Brûleur à prémélange selon la revendication 6, dans lequel ladite soupape de prémélange (110) est commandée par un moteur pas à pas.
  10. Brûleur à prémélange selon l'une quelconque des revendications 6 à 9, ledit brûleur comprenant une unité d'échange de chaleur (104).
  11. Brûleur à prémélange selon l'une quelconque des revendications 6 à 10, dans lequel ledit brûleur comprend un dispositif de ventilation (103).
  12. Brûleur à prémélange selon l'une quelconque des revendications 6 à 10, ledit brûleur comprenant un dispositif d'alimentation en air (115).
EP02732670A 2001-05-18 2002-04-17 Bruleurs a gaz a premelange sans condensation Expired - Lifetime EP1387985B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP02732670A EP1387985B1 (fr) 2001-05-18 2002-04-17 Bruleurs a gaz a premelange sans condensation

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
EP01201886 2001-05-18
EP01201886 2001-05-18
PCT/EP2002/004577 WO2002095294A1 (fr) 2001-05-18 2002-04-17 Bruleurs a gaz a premelange sans condensation
EP02732670A EP1387985B1 (fr) 2001-05-18 2002-04-17 Bruleurs a gaz a premelange sans condensation

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EP1387985A1 EP1387985A1 (fr) 2004-02-11
EP1387985B1 true EP1387985B1 (fr) 2009-10-07

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EP (1) EP1387985B1 (fr)
AT (1) ATE445126T1 (fr)
DE (1) DE60233937D1 (fr)
ES (1) ES2333411T3 (fr)
WO (1) WO2002095294A1 (fr)

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Publication number Priority date Publication date Assignee Title
US6945197B2 (en) * 2003-12-29 2005-09-20 Grand Hall Enterprise Co., Ltd. Water heater
AT414037B (de) * 2004-08-24 2006-08-15 Vaillant Gmbh Verfahren zur vermeidung der kondensation bei gebläseunterstützten brennstoffbetriebenen heizgeräten
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WO2002095294A1 (fr) 2002-11-28
EP1387985A1 (fr) 2004-02-11
ES2333411T3 (es) 2010-02-22
DE60233937D1 (de) 2009-11-19
ATE445126T1 (de) 2009-10-15

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