EP0227699B1 - Foyer de chaudiere - Google Patents

Foyer de chaudiere Download PDF

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Publication number
EP0227699B1
EP0227699B1 EP86903107A EP86903107A EP0227699B1 EP 0227699 B1 EP0227699 B1 EP 0227699B1 EP 86903107 A EP86903107 A EP 86903107A EP 86903107 A EP86903107 A EP 86903107A EP 0227699 B1 EP0227699 B1 EP 0227699B1
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EP
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Prior art keywords
combustion chamber
furnace system
air
chamber
fuel
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EP86903107A
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German (de)
English (en)
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EP0227699A1 (fr
Inventor
Georg Pletzer
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Individual
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Individual
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    • 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 
    • F23C15/00—Apparatus in which combustion takes place in pulses influenced by acoustic resonance in a gas mass

Definitions

  • the invention relates to a firing device for a system having a preferably water-filled heat exchange container, with at least one combustion chamber for pulsating combustion of flowable fuels, which is provided with an ignition device for the first ignition of the fuel and which passes into an exhaust gas guide device, with a prechamber which has a transition area into the combustion chamber, with a supply line for the fuel, which ends in an inflow nozzle arranged in the prechamber, with a supply line for air, which has a check valve arrangement formed at the entrance to the prechamber, through which the air is drawn by the pulling action, which in the Combustion chamber arises due to the expansion dynamics of the combustion products, is fed discontinuously into the prechamber, and with a swirl element arranged in the transition area, on the combustion chamber side of which the air-fuel mixture is swirled.
  • Such a firing device is shown in AT-B-170 522.
  • This pulsation burner for an air heater not only has a discontinuous air supply via the check valve into the prechamber, but also a discontinuous fuel supply.
  • the gaseous fuel is also sucked in through a nozzle in every vacuum phase.
  • Vortex builders in the prechamber create vortex cushions that reduce the impact of pressure peaks on the check valve.
  • a device that is mainly used as a steam generator is described in FR-A-1 023 114.
  • several combustion chambers are arranged in parallel in a water boiler, with their prechambers equipped with aerodynamic non-return valves in an air supply duct and the ends of the exhaust pipes in one Project gas discharge duct through which the boiler water supply line for preheating is led. Steam escapes from the hottest part of the kettle. Any control option for pulsating combustion is missing, as is a mixture formation zone, so that the quality of combustion is not particularly high.
  • DE-B-1 253 851 describes a firing device provided on a boiler, in which the fuel is fed directly into the combustion chamber via a piston pump, the pump frequency of which can be set. The air is supplied via check valves in several antechambers. By changing the fuel supply frequency, coordination with the resonance frequency of the combustion chamber is to be avoided in order to keep the noise level as low as possible.
  • WO-A-8 402 762 describes an air check valve for a pulsation burner which is provided with a prechamber.
  • An injection nozzle is arranged in the antechamber immediately before a cross-sectional constriction of the antechamber.
  • the mixture formation with the air entering around the injection nozzle therefore begins in the prechamber, but is only continued in the combustion chamber due to the accelerating effect of the narrowed prechamber, the usual operating frequency of the combustion chamber precluding complete, optimal mixing.
  • EP-B-11 457 Another example is shown in EP-B-11 457, according to which an embodiment made of prefabricated components, namely a base part and an exhaust gas chamber, a central part and a boiler in which the combustion chamber is inserted, and an upper part with an air and a gas compression chamber is composed, only gaseous fuel being used.
  • the combustion chamber is designed as an approximately spherical insert from which, at the location of the largest diameter, an exhaust gas connection pipe leads tangentially to an intermediate container, from which a plurality of coiled pipes guide the exhaust gases into the exhaust gas chamber.
  • a pre-chamber serves to form an air-gas mixture which is fed separately and has a flame holder.
  • a check valve arrangement with a plurality of poppet valves is provided, with each poppet valve simultaneously blocking the air and gas supply.
  • a pressure control device is used in the gas supply line, which regulates the pressure in the gas compression chamber as a function of the pressure in the air compression chamber, so that the pressure conditions are essentially constant.
  • the firing device according to US-A-4 449 484 is similarly constructed.
  • a prechamber in which the formation of the air / fuel mixture takes place, is separated from the combustion chamber by an orifice having a smaller cross section. Separate supply lines for air and fuel open into the prechamber and are blocked by a common poppet valve. With such a structure, only gaseous fuel can be used.
  • the entire furnace is designed as a boiler insert.
  • US-A-2 715 390 further describes a firing device, the combustion chamber of which is also inserted into a boiler.
  • a pre-chamber serves to form an air-fuel mixture, and a poppet valve closes the transfer opening from the pre-chamber into the combustion chamber.
  • DE-A-2 120 749 describes a portable spray or mist device in which the exhaust gases from a pulsation burner are used to atomize liquid to be sprayed, for example insecticides, etc., which are drawn in from an assigned tank.
  • the device is intended for the combustion of gasoline and has a mixing chamber located in front of the combustion chamber with a swirl element which mixes the air supplied via a check valve with the gasoline gasified by a carburetor and feeds it together to the combustion chamber.
  • the invention has now set itself the task of adapting a firing device of the type mentioned, which is known to have a high efficiency, especially to room or central heating systems of conventional design.
  • the usual extended operating range of the heating systems is to be retained, and low exhaust gas values which meet modern exhaust gas regulations are to be achieved, although not only gaseous fuels, but also heating oils, but in particular also combustible waste materials, such as used oils from the automotive industry, and the like are combustible should be.
  • it should both be able to replace existing firing equipment, such as oil firing systems, and be installable when new, without changes to the components of the heating system being necessary.
  • this object is now achieved in that the inflow nozzle, via which the fuel can be supplied under pressure, is arranged in the transition area, and in that a variable air passage opening between the antechamber and the combustion chamber is provided, with the aid of which the strength of the The air inflow resistance influencing the check valve arrangement into the combustion chamber can be adjusted.
  • an air inflow resistance is required, which was previously generated by non-return valves or by check valves. If the open valve area is too large, the firing device cannot be started or operated. If the open valve area is too small, not only is the performance low, but also its adjustment range.
  • the inflow resistance is not determined by the air inlet valves, but by the size of the air passage area of the actuating device.
  • the total opening cross section of the air inlet valves can be of any size, since with the help of the adjusting device the air passage area between the prechamber and the combustion chamber can be adjusted so that the air supply is optimized with regard to a stoichiometric mixture composition.
  • the adaptation of the air supply is achieved for every power range, since with every change in the fuel flow, in particular the injection pressure, a change in the inflow resistance can take place by adjusting the size of the air passage area.
  • the adjusting device comprises the inflow nozzle of the fuel supply line and an element which reduces the cross section of the transition area, which together limit an adjustable annular gap for the air passage.
  • a particularly fine adjustment of the air supply to the set amount of fuel is achieved in that the inflow nozzle is designed to be adjustable between a front end position near the cross-section-reducing element and a more distant rear end position.
  • the adjustment can be made mechanically, pneumatically or hydraulically.
  • a preferred adjustment range for the inflow nozzle is between 10 mm and 20 mm in front of the element that reduces the cross section.
  • the cross-section-reducing element is designed in particular as a ring diaphragm, a further adjustment of the air supply can be achieved when the opening width of the ring diaphragm is adjustable, such a cross-section-reducing element being able to be designed as a mechanically adjustable slip plate, and / or when the ring diaphragm is axially adjustable is so that their distance from the combustion chamber floor can be changed.
  • the swirl element Since in the transition area into the combustion chamber for swirling the fuel with the air before it is fed into the combustion zone of the combustion chamber, the swirl element is provided, which contributes to simultaneous and uniform ignition of the mixture in the combustion zone and is jointly responsible for the excellent exhaust gas values mentioned later
  • the swirl element which is arranged at a distance from the combustion chamber base of in particular 10 to 20 mm, is formed by the ring diaphragm.
  • the element which reduces the cross section of the air passage area and in particular is formed by the ring diaphragm can be arranged in the extension of the prechamber.
  • a preferred adjustment range for the inflow nozzle lies between 10 and 20 mm in front of the cross-section-changing element or the swirl element. With one and the same burner, a much larger power range can thus be covered, which is approximately three times the power range for non-adjustable parts with an adjustable inflow nozzle and an adjustable cross-section-reducing element.
  • a screen used as a swirl element also forms part of a flame holder, which promotes the rapid evaporation of liquid fuels.
  • the gases produced during combustion on the one hand shoot into a connecting pipe of the exhaust gas discharge device attached to the combustion chamber and on the other hand also press into the antechamber, whereby they Fuel particles that continue to flow also press into the prechamber. Due to the pressure increase, they seal the check valves, which are essentially already closed by their own spring force.
  • the gases contained in the prechamber which are a mixture of fuel and air mixed with waste gas, are pre-compressed.
  • the layer closest to the combustion chamber mainly contains combustion products with still existing, unburned fuel and a small amount of air.
  • the next layer consists of a fuel-air mist in which the fuel is abundant.
  • the last layer consists of a fuel-air mixture in which there is only a small amount of fuel, i.e.
  • the fuel is entrained by the fresh air that shoots in at high speed and is introduced into the combustion chamber at high speed as a mixture of fuel and air.
  • the incoming fresh gas mixture is slowed down and the pressure is simultaneously increased.
  • the fresh gas mixture is matched by the exhaust gas wave flowing back from the exhaust pipe.
  • the combustion products shoot into the exhaust pipe and back into the prechamber.
  • the suction process described is repeated and the mixture of waste gas, fresh air and fuel is sucked back into the combustion chamber.
  • the fuel is continuously fogged, despite the fact that the fuel mixture is introduced into the combustion chamber in accordance with the working rhythm of the device (for example 50 Hz).
  • the adaptation of the air supply to different performance ranges can be further improved if the rear end position of the inflow nozzle lies between two mouth branches of the air supply line, which open laterally into the roughly cylindrical prechamber, at least one branch branch separated is lockable.
  • V-shaped valve seats which are fitted with a pair of valve flaps, are particularly suitable as air inlet valves. Since the V-shaped valve flaps do not have to determine the air inflow resistance and are therefore oversized, they will only open slightly even with maximum air supply. As a result, they are only subjected to minimal stress and are largely free of closures. They consist, for example, of spring steel sheet, glass or carbon fiber reinforced plastic.
  • the valves In the idle state, the valves have a small gap, which is referred to as a pre-opening and is preferably achieved by a slight convex curvature of the valve seat.
  • a pre-opening at the tip of the valve flaps should be between 0.1 and 0.3 mm.
  • the pre-opening serves to allow air with low resistance to be led through the pre-opened valves by a small blower (starting blower) in order to ventilate the combustion chamber and admit fresh starting air.
  • starting blower starting blower
  • the valves open to a gap of 2 to 4 mm during operation.
  • the overpressure in the combustion chamber keeps them tightly closed, they go into the pre-opening position at the transition from overpressure to underpressure and are opened to the required cross-section by the fresh air drawn in.
  • valve flaps are flat leaflets which are relaxed in the pre-opening position and which are tensioned in both the closed and open positions.
  • the automatically variable opening of the V-valves is an essential part of the infinitely variable control of the combustion device.
  • the injection pressure and thus the amount of fuel is increased, the pressure fluctuations during combustion increase. The result of this is that a larger amount of air is sucked in during the suction time, and the air speed has to increase, which can be handled without any problems due to the oversized V-shaped valve flaps.
  • the infinitely variable controllability of the burner is created by changing the injection pressure, the fuel-air ratio being essentially stoichiometric over the entire control range.
  • valve flaps of the check valves are made of different materials, the check valve of the branch branch near the combustion chamber being able to have valve flaps with low flexural strength in order first to allow air-rich, then fuel-rich and finally air-rich mixture to flow into the combustion chamber, so that results in a stratified charge of the combustion chamber.
  • a design of the cross-section-reducing element as a venturi tube insert has proven particularly useful for this purpose, since if the air supply line is divided into two mouth branches, the mouth branch of the air supply line near the combustion chamber preferably opens at the narrowest point of the venturi tube insert, which is provided with through-openings.
  • a ratio of diameter to length of 1: 1.5 to 1: 2.5, preferably of 1: 2 is advantageous in the combustion chamber.
  • the length of the prechamber should correspond to about 1.5 to 3 times its diameter, which corresponds to about a thirtieth to a fiftieth of the distance of a first silencer of the exhaust gas discharge device from the combustion chamber floor. On the other hand, this distance is 40 to 60 times the diameter of the exhaust pipe between the combustion chamber and the first silencer.
  • the combustion chamber is provided with a double jacket which encloses a compensation gap in order to achieve particularly favorable exhaust gas values.
  • the inner jacket is only connected to the outer jacket on the combustion chamber bottom side, the inner base plate forming a heat shield and the outer one being connected to a carrier plate.
  • the expansion gap not only forms an expansion zone, but also the inner jacket is made to glow, which results in a hot combustion chamber with environmentally friendly exhaust gases, which can be seen in the following measurement tables.
  • the exhaust gas temperature can be chosen as low as desired.
  • the heat exchange area of the exhaust gas discharge device can also have a length which is substantially greater than the length of the exhaust pipe which causes the periodic oscillating movement in the exhaust gas column at the desired frequency. It is therefore preferably provided that a cross-sectional constricting diaphragm is used in the connecting pipe of the exhaust gas discharge device, which delimits the length of the pulsating exhaust gas column. Mufflers, heat exchangers etc. of any type and size can be connected after this cover without influencing the combustion processes.
  • the length of the pulsating exhaust gas column between the combustion chamber floor and the cross-sectional constricting orifice in the exhaust pipe or exhaust pipe preferably corresponds to approximately fifteen times the length of the prechamber.
  • Each muffler immersed in the heat exchange medium is preferably of double-walled design, the gap having a width of approximately 2-3 mm. This prevents condensation.
  • the combustion chamber has a cover plate on the end face opposite the combustion chamber base, on which a vertebral body stands up centrally, the connecting pipe being attached laterally and the vertebral body preferably being S-shaped.
  • This version also increases the mixing of the gases contained in the combustion chamber.
  • at least two connecting pipes are provided, preferably at different distances from the combustion chamber floor, at least one of which can be blocked. The connecting pipes can open into a common intermediate container, the heat exchange surface of the firing device also being able to be regulated by the possibility of shutting off a connecting pipe.
  • one of these connecting pipes ends as a lockable hot gas extraction line in the hottest zone of the combustion chamber, and that it leads outward through the combustion chamber floor opposite to the exhaust gas discharge device. This can be returned to the heat exchanger tank and form an additional enlargement of the heat exchange surface, whereby it is inserted again, for example between two mufflers, into the exhaust pipe.
  • a hot gas extraction line can, however, also be used in another way. It is provided in one embodiment that part of the hot gas extraction line forms a tubular heater.
  • the tubular heater can represent a room air heater, but it could also be guided in helical windings and form cooking areas.
  • combustion chamber is arranged on the inside and the prechamber on the outside of a support plate which can be fastened to the heat exchanger tank, and the firing device forms a ready-to-install insert in the heat exchanger tank.
  • the firing device thus represents a prefabricated unit which, in the case of hot water heating, is inserted into the usual boiler or boiler, and in the case of hot air heating into the furnace, which may otherwise be heated with solid fuels.
  • the heat exchange medium could also be a suitable storage mass, such as concrete or light metal, so that the firing device is part of a storage heater.
  • the double jacket combustion chamber with a gap width of 0.3 mm produced the most favorable exhaust gas values.
  • This combustion chamber was used for further experiments in which a cross-section-reducing and vortex-forming ring diaphragm with a clear width of 28 mm was used at a distance of 12 mm from the combustion chamber.
  • the tests were carried out once with 11 bar oil injection pressure (burner output approx. 14 kW) and on the other hand with 22 bar oil injection pressure (burner output approx. 30 kW). The following measured values were obtained, the low values of the residual 0 2 fraction being particularly noteworthy.
  • FIG. 1 shows a longitudinal section through a first embodiment of a firing device according to the invention
  • FIG. 2 shows a section through the prechamber according to line 11-11 of FIG. 3
  • FIG. 3 shows a partial longitudinal section through the prechamber according to line 111-III 2
  • FIG. 4 shows an illustration according to FIG. 3 of a variant of the prechamber
  • FIG. 5 shows a longitudinal section through a second exemplary embodiment
  • FIG. 6 shows a section along the line VI-VI of FIG. 5
  • FIG. 7 3 shows a second variant of the prechamber
  • FIGS. 8 to 11 schematically illustrate the operational sequence in the phases of intake, compression, combustion and exhaust.
  • a heat exchange container 1 in the exemplary embodiments shown as a boiler 3 of a central heating system 4 filled with water 3, is cylindrical in shape and closed by an upper end plate.
  • the upper end plate serves as a carrier plate 2 for a firing device with a combustion chamber 5 for pulsating combustion, in particular of liquid fuels.
  • the combustion chamber 5 is inserted into an opening in the carrier plate 2 and in the embodiment according to FIGS. 1 to 4 passes over a conical end section 20 into a connecting pipe 8.
  • this is guided through the heat exchange container 1 at multiple angles and opens into a double-walled silencer 9, from which an exhaust pipe 7 guides the combustion gases into the open.
  • the exhaust pipe 7 is provided with a lid flap 38, which avoids a draft and a too rapid cooling of the parked combustion system.
  • a lid flap 38 which avoids a draft and a too rapid cooling of the parked combustion system.
  • two to three silencers 9 are provided one behind the other.
  • In the connecting pipe 8 is a cross-section narrowing diaphragm 37 is inserted, the distance from the combustion chamber 5, the length of the pulsating exhaust gas column can be limited.
  • the combustion chamber 5 is fastened to a closure plate 25 (FIG. 3) and forms a container insert which is fastened to the carrier plate 2 and is inserted into the heat exchange container 1. This also makes it possible to convert existing heating systems in a simple manner.
  • a prechamber 10 is also attached on the outside, which is essentially cylindrical and into which the fuel supply line 12, which can be blocked, for example, by means of a solenoid valve, and laterally the air supply line 11 provided with a check valve arrangement 30 open out.
  • An intake muffler 14, a blower 15 and control devices and other auxiliary devices complement the firing device according to the invention to form a construction and assembly unit.
  • the combustion chamber 5 is double-walled, the outer jacket 21 being fastened to the carrier plate 2 by means of the closure plate 25 and merging into the connecting pipe 8 (FIG. 1), while the inner jacket 22 is left unchanged an air gap 23 of preferably 0.3 mm to the outer jacket 21 from the combustion chamber bottom 19 extends over the conical end portion 20 of the combustion chamber 5 into the connecting pipe 8 (Fig. 1, to 11).
  • the combustion chamber floor 19 is also double-walled and has an inner heat shield 24 and the outside of the closure plate 25.
  • the heat shield 24 and the closure plate 25 thus delimit a bottom-side gap 48, which is preferably 10 mm, so that a "hot" inner chamber is created, which is connected to the outer part exclusively by means of the screws 49.
  • a "hot" inner chamber is created, which is connected to the outer part exclusively by means of the screws 49.
  • the heat shield 24 simultaneously forms an evaporator plate for the evaporation of the fuel mist, which is mixed and swirled in the transition area into the combustion chamber 5 together with the air by the diffuser action of a swirl element 27.
  • the swirl element 27 serves as a cross-section-reducing element in the transition area and can be formed, for example, by an aperture inserted into the antechamber 10 (FIGS. 3, 4, 8-11).
  • the vortex element can also consist of an extension 55 of the prechamber 10, into which an annular screen 56 is additionally inserted as a cross-section-reducing element.
  • a venturi tube insert 35 is arranged in the transition area as a cross-section-reducing element.
  • a spark plug 18 protrudes through the combustion chamber floor 19 (FIG. 3) for the initial ignition of the firing device.
  • the fuel supply line 12 axially entering the prechamber 10 ends in an inflow nozzle 29, through which liquid fuel is continuously sprayed into the combustion chamber 5 under a pressure, preferably between 10 and 25 bar, for example heating oils, waste oils, etc.
  • the inflow nozzle 29 and the element arranged in the transition area and having a reduced passage cross section form an actuating device 26 which delimits an air passage gap 53. Since the swirl element 27 is preferably used as the element with a reduced passage cross section, the inflow nozzle 29 is axially adjustable, as shown in broken lines. The inlet nozzle 29 is in its foremost position just behind the swirl element 27, leaving the air passage gap 53.
  • the dimensioning of the air passage gap 53 by changing the adjusting device 26 is also decisive for the power setting of the firing device, so that an almost stoichiometric one in each position Air-fuel ratio for optimal combustion can be achieved.
  • the air passage gap 53 can now be changed by the aforementioned axial adjustment of the inflow nozzle 29, it can also be done by changing the opening width of the cross-section-reducing element or the swirl element 27 if it is designed as a diaphragm.
  • FIG. 2 shows this schematically, in which the diaphragm is formed by two slides inserted in recesses 54 of the closure plate 25, which have mutually directed recesses and overlap one another, so that the diaphragm opening formed from the two recesses changes when moved.
  • FIG. 7 the adjustment of the diaphragm 56 in the extension 55 of the prechamber 10 parallel to the fuel supply line 12 is indicated schematically for the change in the air passage gap 53.
  • an additional annular gap opens between the diaphragm 56 and the wall of the extension 55 (dashed arrows 58).
  • the measures listed for changing the air passage gap 53 can also be provided in combination. Their correct setting enables combustion with the blue flame color mentioned.
  • the check valves 30 are provided with V-shaped, preferably slightly convexly curved valve seats 31 (FIG. 2), to which flat valve flaps 32 are attached. Due to the oversized total cross-sectional area, the valve flaps 32 have a small opening angle, so that they are exposed to very low bending stresses.
  • the air supply line is divided into two outlet branches 16, 17, each with a check valve 30, each outlet branch 16, 17 being individually lockable by a flap 33, which further increases the controllability of the firing device.
  • the valve flaps 32 of the individual valves 30 preferably have different material properties, so that they have different bending strengths. It will therefore open that valve 30, the valve flaps of which are softer, earlier and the second only when there is a further need for air.
  • the valve near the combustion chamber is provided in the branch branch 16 with softer valve flaps 32, via which the shorter flow path also leads into the combustion chamber 5.
  • the valves 30 laid in the lateral branches are not directly exposed to the high temperatures in the combustion chamber 5, which can be up to 1200 ° C., the continuous fuel supply through the inflow nozzle 29 also contributing to cooling.
  • the mouth branches 16, 17 are further arranged so that in the most retracted position of the inflow nozzle 29 this comes to rest between the two mouth branches 16, 17.
  • a stratified charge of the combustion chamber 5 is also achieved in this way, because during the intake process first a lower-fuel air-fuel mixture (air via the branch branch 16), then a more fuel-rich, and finally a lower-fuel air-fuel mixture (air via the branch branch 17) into the combustion chamber 5 reached.
  • FIG. 6 a further embodiment is shown in which the firing device mounted on the carrier plate 2 is again designed as a container insert.
  • the combustion chamber 5 of this embodiment is pot-shaped and closed on its end opposite the combustion chamber bottom by a cover plate 40, from which an approximately S-shaped vertebral body 41 rises centrally (FIG. 6).
  • two connecting pipes 42, 43 branch off laterally tangentially, which open together into a chamber 39, through which the length and frequency of the pulsating exhaust gas columns are limited.
  • the two connecting pipes 42, 43 branch off opposite one another at different heights from the combustion chamber 5, the connecting pipe closer to the antechamber 10 being lockable by means of a closure 44 which can be actuated from the outside. This also enables control of the firing device.
  • the second connecting pipe 43 can also be blocked.
  • the remaining structure of the firing device corresponds essentially to the firing device already described above according to FIGS. 1 to 4. However, the possibility is also shown here that the prechamber 10 protrudes into the combustion chamber 5, and the cross-section-reducing vortex element 27 at the mouth of the prechamber 10 is formed by the projecting edge. The diffuser effect arises outside the vortex element in the annular space towards the combustion chamber floor 19, which in this embodiment is conical.
  • the exhaust gases cooled by the heat exchange with the heating medium of the room or central heating system do not require a chimney, so that the exhaust gas discharge device 6 can be referred to as an exhaust system.
  • the exhaust gases that pass through one or more silencers 9 can additionally drive a generator via a turbine wheel, which generates the electricity required for the fuel pump, the solenoid valve in the fuel supply line 12 and the air blower required to start the combustion system, so that they is independent of the supply of electrical energy for the auxiliary devices.
  • the electricity generated is stored in an accumulator, for example a motor vehicle battery.
  • connection pipe 50 which ends approximately in the hottest zone of the combustion chamber 5 and, in the opposite direction to the main connection pipe 8 of the exhaust gas discharge device 6, is led through the combustion chamber floor 19 to the outside.
  • This connecting pipe 50 represents a hot gas extraction line which, for example, can form a tubular heating element as an air heating source or, as indicated schematically, as a coiled pipe, for example a hotplate 52.
  • the connecting pipe 50 can be blocked via a valve 51 and leads back into the exhaust pipe 7.
  • This hot gas extraction line can also be used to increase an exhaust gas temperature in the exhaust pipe 7 which may be too low.
  • FIG. 8-11 show schematically individual phases in the combustion process. 8 there is negative pressure in the combustion chamber 5, in the connecting pipe 8 and in the prechamber 10 (denoted by lines 46), so that air is sucked into the constantly flowing fuel.
  • the vortex element 27 swirls the mixture formed in the annular gap between the vortex element 27 and the inflow nozzle 29 as mentioned, which is compressed according to FIG. 9 by the exhaust gas wave flowing back from the connecting pipe 8.
  • An overpressure (designated by crosses 47) builds up, the hot exhaust gases and the high temperature of the swirl element 27, which also serves as a flame holder, causing the automatic ignition, which is shown in FIG. 10.
  • FIG. 11 shows the exhaust phase in which the exhaust gases (arrows 45) are drawn off through the connecting pipe 8 and negative pressure is again generated in the combustion chamber 5 according to FIG. 8. Since fuel is sprayed continuously throughout the entire period, the finest atomization, evaporation and optimal mixing with the combustion air, which brings about the high quality of combustion, becomes clear.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Polarising Elements (AREA)
  • Manufacture, Treatment Of Glass Fibers (AREA)
  • Tunnel Furnaces (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)

Claims (21)

1. Foyer de chaudière pour une installation comportant un récipient d'échange de chaleur (1) de préférence rempli d'eau, le foyer comportant au moins une chambre de combustion (5) servant à la combustion pulsée de combustibles fluides, qui est pourvue d'un dispositif d'allumage (18) pour l'allumage initial du combustible et qui est prolongée par un dispositif d'évacuation de fumées (6), une préchambre (10), qui comporte une zone de transition avec la chambre de combustion (5), un conduit (12) d'admission du combustible, qui se termine dans une buse d'injection (29) disposée dans la préchambre (10), un conduit (11) d'admission d'air, qui comporte un dispositif formant soupape de retenue (30) placé à l'entrée de la préchambre (10) et par l'intermédiaire duquel l'air est introduit de façon discontinue dans la préchambre (10) sous l'effet du tirage qui est engendré dans la chambre de combustion (5) sous l'effet de la dynamique de détente des produits de combustion, ainsi qu'un élément de turbulence (27) disposé dans la zone de transition et sur le côté duquel, dirigé vers la chambre de combustion, le mélange d'air et de combustible est mis en turbulence, caractérisé en ce que la buse d'injection (29), par l'intermédiaire de laquelle le combustible peut être introduit sous pression, est disposée dans la zone de transition et en ce qu'il est prévu un dispositif de réglage (26) limitant une ouverture variable de passage d'air entre la préchambre (10) et la chambre de combustion (5) et à l'aide duquel est réglable une résistance à l'entrée de l'air dans la chambre de combustion (5), influençant la puissance du tirage sur le dispositif formant soupape de retenue (30).
2. Foyer de chaudière selon la revendication 1, caractérisé en ce que le dispositif de réglage (26) comporte la buse d'injection (29) du conduit d'admission de combustible (12) et un élément réduisant la section de la zone de transition, de manière à limiter en coopération un intervalle annulaire (53) de passage d'air dont la grandeur est réglable.
3. Foyer de chaudière selon la revendication 2, caractérisé en ce que la buse d'injection (29) est agencée de façon à pouvoir être déplacée entre une position limite avant proche de l'élément de réduction de section et une autre position limite arrière espacée.
4. Foyer de chaudière selon la revendication 2 ou 3, caractérisé en ce que l'élément de réduction de section est agencé comme un diaphragme annulaire et est placé à distance de la chambre de combustion (10).
5. Foyer de chaudière selon la revendication 4, caractérisé en ce que la largeur d'ouverture du diaphragme annulaire (56) est réglable.
6. Foyer de chaudière selon la revendication 4 ou 5, caractérisé en ce que le diaphragme annulaire est déplaçable en espacement par rapport à la chambre de combustion (10).
7. Foyer de chaudière selon une des revendications 4 à 6, caractérisé en ce que le diaphragme annulaire est constitué par l'élément de turbulence (27).
8. Foyer de chaudière selon la revendication 4 ou 5, caractérisé en ce que le diaphragme annulaire (56) est disposé dans un élargissement (55), formant l'élément de turbulence (27), de la préchambre (10) en étant espace de la chambre de combustion (5).
9. Foyer de chaudière selon la revendication 2 ou 3, caractérisé en ce que l'élément de réduction de section est agencé comme un organe inséré formant tube de Venturi (35).
10. Foyer de chaudière selon la revendication 3, caractérisé en ce que la position limite arrière de la buse d'injection (29) est située entre deux branches d'embouchure (16, 17) du conduit d'admission d'air (11), qui débouchent latéralement dans la préchambre (10) approximativement cylindrique, au moins une branche d'embouchure (16, 17) pouvant être obturée séparément.
11. Foyer de chaudière selon les revendications 9 et 10, caractérisé en ce que la branche d'embouchure (16), proche de la chambre de combustion, du conduit d'admission d'air (11) débouche dans la zone la plus rétrécie de l'organe inséré formant tube Venturi (35), qui est pourvu d'orifices de passage (36).
12. Foyer de chaudière selon la revendication 10 ou 11, caractérisé en ce que chaque branche d'embouchure (16,17) du conduit d'admission d'air (11) contient une soupape de retenue qui comporte un siège (31) conformé en forme de V et deux clapets de soupape (32), la section totale d'ouverture du dispositif formant soupape de retenue (30) étant supérieure à la section du conduit d'admission d'air (11).
13. Foyer de chaudière selon les revendications 10 et 12, caractérisé en ce que les clapets de soupape (32) des soupapes de retenue sont formés de matériaux différents, la soupape de retenue prévue dans la branche d'embouchure (16) proche de la chambre de combustion comportant des clapets de soupape (32) ayant une plus petite résistance à la flexion.
14. Foyer de chaudière selon la revendication 1, caractérisé en ce qu'il est prévu dans le dispositif de décharge de fumées (6) un diaphragme (37) qui limite la longueur de la colonne pulsée de fumées.
15. Foyer de chaudière selon les revendications 1 et 14, caractérisé en ce que la longueur de la préchambre (10) est à peu près égale à un quinzième de la longueur de la colonne pulsée de fumées entre le fond (19) de la chambre de combustion et le diaphragme (37) prévu dans le dispositif d'évacuation de fumées (6).
16. Foyer de chaudière selon la revendication 1 ou 15, caractérisé en ce que la chambre de combustion (5) comporte, sur le côté frontal opposé au fond (19) de la chambre de combustion, une plaque de recouvrement (40) de laquelle fait saillie verticalement au centre un corps de turbulence (41), auquel cas le tube de raccordement (42) est disposé latéralement.
17. Foyer de chaudière selon la revendication 16, caractérisé en ce que le corps de turbulence (41) a une forme de S.
18. Foyer de chaudière selon la revendication 1 ou 16, caractérisé en ce qu'il est prévu au moins deux tubes de raccordement (42, 43, 50) du dispositif d'évacuation de fumées (6) à des distances différentes du fond (19) de la chambre de combustion, au moins un des tubes de raccordement (42, 50) pouvant être obturé
19. Foyer de chaudière selon la revendication 18, caractérisé en ce qu'un tube de raccordement (50) obturable, servant de conduit d'extraction de gaz chauds, se termine dans la zone la plus chaude de la chambre de combustion (5) et est guidé vers l'extérieur à travers le fond (19) de la chambre de combustion.
20. Foyer de chaudière selon la revendication 19, caractérisé en ce qu'une partie du conduit (50) d'extraction de gaz chauds forme au moins un corps chauffant tubulaire. -
21. Foyer de chaudière selon l'une des revendications 1 à 20, caractérisé en ce que la chambre de combustion (5) est disposée sur le côté intérieur, et la préchambre (10) sur le côté extérieur, d'une plaque portante (2) pouvant être fixée sur le récipient d'échange de chaleur (1) et le foyer de chaudière forme un organe prêt au montage, rapporté dans le récipient d'échange de chaleur.
EP86903107A 1985-06-12 1986-06-04 Foyer de chaudiere Expired EP0227699B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
AT174685 1985-06-12
AT1746/85 1985-06-12

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP88106358A Division EP0307538A3 (fr) 1985-06-12 1986-06-04 Foyer de chaudière
EP88106358.0 Division-Into 1988-04-21

Publications (2)

Publication Number Publication Date
EP0227699A1 EP0227699A1 (fr) 1987-07-08
EP0227699B1 true EP0227699B1 (fr) 1989-01-04

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ID=3520111

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EP88106358A Withdrawn EP0307538A3 (fr) 1985-06-12 1986-06-04 Foyer de chaudière
EP86903107A Expired EP0227699B1 (fr) 1985-06-12 1986-06-04 Foyer de chaudiere

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP88106358A Withdrawn EP0307538A3 (fr) 1985-06-12 1986-06-04 Foyer de chaudière

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Country Link
US (1) US4759312A (fr)
EP (2) EP0307538A3 (fr)
AT (1) ATE39746T1 (fr)
DE (1) DE3661653D1 (fr)
WO (1) WO1986007435A1 (fr)

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WO2012069155A2 (fr) 2010-11-23 2012-05-31 Michael Seifert Générateur de vapeur à jet pulsé
DE102010052268B4 (de) * 2010-11-23 2015-07-02 Michael Seifert Pulsstrahl-Dampferzeuger

Also Published As

Publication number Publication date
EP0227699A1 (fr) 1987-07-08
EP0307538A3 (fr) 1989-05-10
EP0307538A2 (fr) 1989-03-22
WO1986007435A1 (fr) 1986-12-18
US4759312A (en) 1988-07-26
ATE39746T1 (de) 1989-01-15
DE3661653D1 (en) 1989-02-09

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