EP0227699A1 - Foyer de chaudiere. - Google Patents

Foyer de chaudiere.

Info

Publication number
EP0227699A1
EP0227699A1 EP86903107A EP86903107A EP0227699A1 EP 0227699 A1 EP0227699 A1 EP 0227699A1 EP 86903107 A EP86903107 A EP 86903107A EP 86903107 A EP86903107 A EP 86903107A EP 0227699 A1 EP0227699 A1 EP 0227699A1
Authority
EP
European Patent Office
Prior art keywords
combustion chamber
firing device
prechamber
fuel
combustion
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
EP86903107A
Other languages
German (de)
English (en)
Other versions
EP0227699B1 (fr
Inventor
Georg Pletzer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Individual
Original Assignee
Individual
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Individual filed Critical Individual
Publication of EP0227699A1 publication Critical patent/EP0227699A1/fr
Application granted granted Critical
Publication of EP0227699B1 publication Critical patent/EP0227699B1/fr
Expired legal-status Critical Current

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Classifications

    • 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 container, with at least one combustion chamber for the 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 discharge device , and with supply lines for the fuel, for the air, the latter having a check valve arrangement formed at the entrance to a prechamber for a discontinuous air supply.
  • Such a device which is mainly used as a steam generator, is described in FR-A-1,023,114.
  • a steam generator which is mainly used as a steam generator.
  • several combustion chambers are arranged in parallel in a water boiler, on the one hand their prechambers equipped with aerodynamic non-return valves protrude into an air supply duct and on the other hand the ends of the exhaust pipes protrude into a gas discharge duct through which the boiler water supply line for the Preheating is performed. Steam escapes from the hottest part of the kettle. Any control option for pulsating combustion is lacking, as is a mixture formation zone, so that the quality of combustion is not particularly high.
  • the invention further relates, in accordance with FR-A-1,023,114, on the one hand to a firing device with the features mentioned at the outset, which additionally has a continuous fuel supply, the fuel being introduced under pressure via an inflow nozzle, and on the other hand to a firing device with the aforementioned items
  • a firing device with the features mentioned at the outset, which additionally has a continuous fuel supply, the fuel being introduced under pressure via an inflow nozzle
  • a firing device with the aforementioned items
  • 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.
  • a coordination with the resonance frequency of the combustion chamber is to be achieved in order to keep the noise development as low as possible.
  • WO-A-84 02 762 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 the cross-section of the antechamber is narrowed.
  • the mixture formation with the air entering around the injection nozzle thus 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 ensuring complete, optimal mixing. closes. There is also no possibility of regulation.
  • AT-B-170 522 shows a pulsation burner with a discontinuous air supply via a check valve into a prechamber in which the mixture is formed with gaseous fuel. This is also sucked in through a nozzle in every vacuum phase, so that the fuel supply is not continuous. Vortex formers are provided in the prechamber to create vortex cushions that reduce the impact of pressure peaks on the check valve. One way of regulating this only There is no provision for a burner for an air heater working with gaseous fuel.
  • EP-PS 11457 Another example is shown in EP-PS 11457, 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, whereby only gaseous fuel is 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 prechamber serves to form an air-gas mixture which is fed separately and has a flame holder.
  • a check valve arrangement with a plurality of plate valves is provided, each plate valve simultaneously blocking the air and gas supply.
  • a pressure regulating 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 essentially constant pressure conditions prevail.
  • 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 plate having a passage opening of smaller cross section. Separate supply lines for air and fuel, which are blocked by a common plate valve, open into the antechamber. 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.
  • This firing device also shows a prechamber which is separated from the combustion chamber by an orifice and in which a plate valve jointly blocks the separate feeds for air and gaseous fuel.
  • the invention has now set itself the task of adapting a firing device of the type mentioned at the outset, which is known to have a high degree of efficiency, specifically to conventional conventional space or central heating systems. Accordingly, low exhaust gas values which meet modern exhaust gas regulations are to be achieved, although not only conventional fuels, in particular heating oils, but also combustible waste materials, such as used oils from the automotive industry, and the like should be combustible. Furthermore, it is intended to replace both existing firing devices, such as oil firing systems, and at the new creation can be installed without changes to the components of the heating system being necessary. Another essential task is to maintain the usual control range of the heating system for these applications.
  • this object is now achieved in that the inflow nozzle for the fuel is arranged in the antechamber for use in a rough or central heating system, and in that in the transition area from the antechamber to the combustion chamber the cross-sectional area of the antechamber changes Element is provided which whirls the air / fuel mixture on its combustion chamber side.
  • the swirling of the fuel with the air before it is fed into the combustion zone of the combustion chamber optimizes the air-fuel mixture, and a simultaneous and uniform ignition in the combustion zone is achieved, which are the prerequisite for the excellent exhaust gas values mentioned later.
  • rough power regulation can be carried out by simply adjusting the oil pressure, the discontinuous air supply automatically adapting to the prevailing conditions via the air inlet valve arrangement.
  • the vortex-forming element can be formed by an aperture which narrows the cross-section of the antechamber and then widens it again, whereby it acts as a vortex-forming diffuser on the combustion chamber side.
  • the vortex-forming element can also be designed as a mere extension of the antechamber.
  • a venturi tube insert can also or additionally be provided as the swirl element. 6
  • the vortex element is arranged at a distance from the combustion chamber in the antechamber. This is preferably 10-20 mm from the bottom of the combustion chamber.
  • the performance control can be improved and refined by various other features. It can be provided that the distance of the swirl element or the additional screen to the combustion chamber floor is adjustable, and / or that the opening width of the swirl element is adjustable. Such a swirl element can be designed, for example, as a mechanically adjustable slip-cover.
  • a screen used as a swirl element also represents part of a flame holder, which contributes to the vaporization of liquid " fuels.
  • provision is made in particular for the fuel feed line to enter the prechamber axially and in the area of the swirl element This preferably results in an embodiment in which the inflow nozzle is designed to be adjustable between a front end position on the swirl element and a rear end position, which can be done mechanically, pneumatically or hydraulically.
  • the adjustable vortex element and / or the longitudinally displaceable inflow nozzle enable the mixture composition to be fine-tuned, so that an almost stoichiometric mixing ratio can be achieved for each power range, since the air passage annular gap between the vortex element and the inflow nozzle is changed, and the air requirement for the the amount of fuel required in each case, which depends on the nozzle size and the injection pressure, regulates itself.
  • a preferred adjustment range for the inlet nozzle lies between 10 and 20 mm in front of the vortex element. A much larger output range can thus be covered with one and the same burner.
  • the control range with adjustable inflow nozzle and adjustable swirl element is approximately three times the control range with non-adjustable parts.
  • 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 as a mixture of fuel and air at high speed. Due to the further diffuser effect of the combustion chamber, which is expanded compared to the prechamber, the input shooting fresh gas mixture and simultaneous pressure increase.
  • the fresh gas mixture is matched by the exhaust gas wave flowing back from the exhaust pipe.
  • the combustion products now not only shoot into the exhaust pipe, but also partially back into the prechamber, and the fuel particles which continue to flow in as well press into the antechamber. Only in the subsequent suction process does this mixture consisting of waste gas, fresh air and fuel get back into the
  • an inflow resistance is required, which in the past is represented by non-return valves, today usually 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 output low, but also the control range.
  • the inflow resistance is not formed by the air inlet valves, but by the air passage area between the inflow nozzle and the swirl element.
  • the total opening cross section of the air inlet valves can thus be of any size. This enables an embodiment in which the air supply line has two mouth branches which open laterally into the prechamber at an axial distance, at least one mouth branch being lockable.
  • the controllability of the firing device can be further improved in that the rear end position of the axially adjustable inflow nozzle lies between the two branches of the air supply line. A stratified charge of the combustion chamber is also effected in this way, since the first and the last layer are more air-rich, the middle layer is more fuel-rich.
  • Non-return valves with V-shaped valve seats are particularly suitable as air inlet valves
  • V-shaped valve caps Only according to the passage cross-section between the vortex element and the inflow nozzle, they are only minimally stressed in the case of oversized dimensions, so that they are largely
  • 15 are wear-free.
  • they consist of. Spring steel sheet, glass or carbon fiber reinforced plastic.
  • valves At rest, the valves have a small gap, which is referred to as a pre-opening and preferably
  • a pre-opening at the tip of the valve flaps should be between 0.1 and 0.3 mm. The pre-opening serves for the fact that when starting a small blower (starting blower) air with little resistance
  • valve 25 can be passed through the pre-opened valves to ventilate the combustion chamber and let in fresh air.
  • 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 when overpressure passes
  • valve flaps are flat leaflets which are relaxed in the pre-opening position and both in
  • the automatically variable opening of the V-valves is on 10 essential part of the infinitely variable controllability of the furnace.
  • the injection pressure and thus the amount of fuel is increased, the pressure fluctuations during combustion increase. The consequence of this is that a larger amount of air is sucked in during the intake time and the air speed has to increase, which can be handled without any problems owing 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.
  • check valve of the branch branch near the combustion chamber can have valve flaps with low bending strength in order to allow air-rich, then fuel-rich and finally air-rich mixture to flow into the combustion chamber.
  • the length of the antechamber should be about 1.5 to
  • the combustion chamber has a double jacket which encloses a compensating gap.
  • the inner jacket is thus only connected to the outer jacket on the combustion chamber base side, the combustion chamber base preferably being formed from two spaced-apart base plates, the inner of which forms a heat shield and the outer is connected to the carrier plate. This distance is preferably 8-10 mm. This also keeps the carrier plate relatively cool.
  • the heat shield forms an insertable, hot chamber with the inner jacket, which extends into the exhaust gas discharge device.
  • the compensating gap does not only create an expansion gap. zone is formed, but there are also those near the chamber
  • the inner jacket is made to glow and environmentally friendly exhaust gases with low CO values are achieved.
  • the hot heat shield also acts as an evaporator plate for the swirled fuel droplets and possibly forms part of the flame holder.
  • the compensation gap between the inner jacket and the outer jacket is preferably between 0.2 and 2 mm thick.
  • the gap should be so small that the inner jacket expands and the heat can be transferred to the heat exchange medium.
  • a gap that is too large would reduce the material service life on the one hand due to the excessive heating, and on the other hand the nitrogen oxide content of the exhaust gases would be unfavorably high, even though lower CO values would also result.
  • the gap is too small or there is no inner jacket, the combustion chamber remains too cool, which increases the CO values, while the nitrogen oxide content drops. Furthermore, this would lead to deposition 12 of coal and soot on the combustion chamber walls.
  • a favorable compromise is achieved in the specified gap range, ie low carbon monoxide and relatively low nitrogen oxide values with a high proportion of carbon dioxide, as can also be seen from the following measured value tables.
  • controllable fuel pressure and the automatically adjusted addition of air volume cause the adjustable swirl aperture, the adjustable position of the inflow nozzle and the hot combustion chamber over the entire control range of the firing device to produce a light blue, transparent flame and thus optimized combustion.
  • an embodiment in which the air supply line is divided into two branches provides that the branch branch of the air supply line near the combustion chamber opens at the narrowest point of the venturi tube insert of the antechamber, which is provided with through openings.
  • the exhaust gas temperature can be chosen to be as low as desired.
  • ⁇ m the meaning of as complete as possible exchange of the heat exchange region of the furnished ⁇ can Abgasabdies 2015 also have a length that is significantly greater than that length of the Aus ⁇ puffrohres which causes the periodic swing motion in the exhaust plume in the desired frequency. It is therefore preferably provided that a cross-sectional constricting diaphragm is inserted in the connecting pipe of the exhaust gas discharge device, which delimits the length of the pulsating exhaust gas column. Silencers, heat exchangers etc. of any type and size can be connected after this orifice without influencing the combustion processes.
  • the length of the pulsating exhaust gas column between the combustion chamber floor and the cross-sectional narrowing 13 aperture in the exhaust pipe or exhaust pipe preferably corresponds approximately to fifteen times the length of the prechamber.
  • Each muffler immersed in the heat exchange medium is preferably double-walled, the space 5 having a width of approximately 2 to 3 mm. This prevents condensation.
  • the combustion chamber has a cover plate on the end face opposite the combustion chamber floor, on which a vertebral body rises centrally, the connecting pipe being attached laterally, the vertebral body preferably being S-shaped.
  • This embodiment also increases the mixing of the gases contained in the combustion chamber.
  • the connecting pipes can open in a common intermediate container, whereby the possibility of shutting off a connecting pipe can also regulate the heat exchange surface of the firing device.
  • one of these connecting pipes ends as a lockable hot gas extraction line in the hottest zone of the combustion chamber and, contrary to the exhaust gas discharge device, leads it through the combustion chamber floor to the outside. This can be returned to the heat exchange tank and form an additional enlargement of the heat exchange surface, whereby it is again inserted, for example between two silencers, into the exhaust pipe.
  • a hot gas extraction line can, however, also be used for other purposes.
  • part of the hot gas extraction line forms a tubular heating element.
  • the tubular heating element can represent a room air heating element, but it could also be guided in helical windings and cooking zones form .
  • combustion chamber is arranged on the inside and the prechamber on the outside of a support plate which can be fastened to the heat exchange container, and the firing device forms a ready-to-install insert in the heat exchange container .
  • the firing device represents ⁇ a ⁇ urcn a prefabricated unit, which is inserted in the usual boiler or boiler in the case of a warm water heater, and in the oven, which may otherwise be heated with solid fuels, in the case of hot air heating.
  • 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 effect especially an improved power control '. It is therefore possible to equip the combustion chamber with several prechambers, which are optionally fed via separate fuel supply lines.
  • combustion device with a plurality of combustion chambers, the exhaust gas discharge devices of which lead into a common exhaust pipe.
  • a phase shift of the individual combustion chambers occurs automatically, so that a more uniform, lower noise development takes place.
  • the latter two versions allow a very large control range for the furnace.
  • the following tests were carried out with commercially available furnace heating oil, an orifice with a clear width of 26 mm was used in the prechamber as a vortex former and the fuel was continuously injected into the prechamber at a injection pressure of 18 bar via a 0.45 / 60 "nozzle The result was a burner output of approx. 26 kW.
  • 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 vortex-forming diaphragm with a clear width of 28 mm and a combustion chamber floor clearance of 12 mm was used in the prechamber.
  • 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 line injection pressure (burner output approx. 30 kW). The following measured values were obtained.
  • FIG. 1 shows a longitudinal section through a first embodiment of a furnace device according to the invention
  • FIG. 2 shows a section through the prechamber according to line II-II of FIG. 3
  • FIG. 3 shows a partial longitudinal section through the prechamber according to FIG Line III-III of FIG. 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 embodiment
  • FIG. 6 shows a section along line VI-VI of FIG 5
  • FIG. 7 shows a representation according to FIG. 3 of 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 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 liquid fuels.
  • the combustion chamber 5 is inserted into an opening in the carrier plate 2 and has a design
  • a prechamber 10 is also attached to the outside of the closure plate 25, 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.
  • An intake muffler 14, a blower 15 and control devices and other auxiliary devices complement the combustion 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 passing into the connecting pipe 8 (FIG. 1), while the inner jacket 22, leaving an air gap 23 of preferably 0.3 mm to the outer jacket 21 from the combustion chamber floor 19, extends over the conical end section 20 of the combustion chamber 5 into the connecting pipe 8 (FIGS. 1, 7 to 11).
  • the combustion chamber base 19 is also double-walled and has an inner heat shield 24 and the closure plate 25 on the outside. 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 formed, which is connected exclusively to the outer part via the screws 49.
  • the end of the pre-chamber 10 extends as far as the heat shield 24 through the closure plate 25 as part of a flame holder 26 at the same time an evaporator plate for the evaporation of the fuel mist, which is mixed and swirled in the region of the passage opening into the combustion chamber 5 together with the air by the diffuser action of a swirl element 27.
  • the vortex element 27 can be formed, for example, by an aperture inserted in the prechamber 10 (FIGS. 3, 4, 8-11), or it can consist of an extension 55 of the prechamber 10 according to FIG. 4, a venturi tube insert 35 is additionally assigned, and in the embodiment according to FIG. 7, an aperture 56 is inserted into the extension 55.
  • 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, at a pressure preferably between 10 and 25 bar, for example heating oils, waste oils, etc., is sprayed continuously into the combustion chamber 5.
  • the inflow nozzle 29 is preferably axially adjustable, as shown in dashed lines, and its foremost position is just behind the swirl element 27, leaving an air passage gap 53.
  • the dimensioning of the air passage gap is also important for the power control of the firing device 53 is decisive, since in this way an almost stoichiometric 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 swirl element 27 if it is designed as a diaphragm.
  • 2 shows this schematically, in which the diaphragm is formed by two slides inserted in recesses 54 of the closure plate 25. point and overlap each other, so that the aperture opening formed from the two recesses changes when sliding.
  • the adjustment of the aperture 56 in the extension 55 of the prechamber 10 parallel to the fuel supply line 12 is schematic. indicated.
  • the air supply line 11 branches laterally from the housing 13 of the prechamber 10 and is inserted into the check valves 30. are. These have a total passage area that is larger than the cross-sectional area of the antechamber 10.
  • the check valves 30 are V-shaped, preferably slightly convex
  • Valve seats 31 are provided, on 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 is therefore the valve 30 whose valve flaps 32 are softer, open earlier and the second only when more air is required.
  • the valve near the combustion chamber in the mouth branch 16 is provided 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 supply of fuel through the inflow nozzle 29 also contributing to cooling.
  • 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).
  • FIG. 4 there is also a cross-sectional constriction of the antechamber 5 through a venturi tube insert 35 which has through openings 36 through which the air enters from the mouth branch 16.
  • the adjustability of the inflow nozzle 29 a further refined control possibility of the firing device, since its two end positions lie in front of or behind the Venturi tube.
  • Carrier plate 2 mounted firing device is in turn designed as a container insert.
  • the combustion chamber 5 of this embodiment is pot-shaped and is closed on its end opposite the combustion chamber base by a cover plate 40, from which an approximately S-shaped vertebral body 41 rises centrally (FIG. 6).
  • Two connecting pipes 42, 43 branch out of the combustion chamber 5 laterally tangential, 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 from the combustion chamber 5 at opposite heights, 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 according to FIGS. 1 to 4 already described above. However, the possibility is also shown here that the prechamber 19 projects into the combustion chamber 5 and the swirl element 27 at the mouth of the Antechamber 10 is formed by this nozzle. The diffuser effect arises outside of the vortex element in the annular space towards the combustion chamber floor.
  • 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 removal device 6 can be referred to as an exhaust system.
  • the exhaust gases which pass through one or more silencers 9 can additionally drive a generator via a turbine wheel, which generates the fuel pump, the solenoid valve in the fuel supply line 12 and the one required to start the combustion system
  • Air blowers required electricity generated so that it 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 opposite to the main connection pipe 8 of the exhaust gas discharge device 6 through the combustion chamber floor 19 is led 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, a cooktop 52 as a spirally wound pipe.
  • 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 in to the constantly flowing fuel.
  • the vortex element 27 swirls the resulting mixture 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 flame holder 26 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 combustion quality, 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)
  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Heat-Pump Type And Storage Water Heaters (AREA)
  • Pressure-Spray And Ultrasonic-Wave- Spray Burners (AREA)
  • Polarising Elements (AREA)
  • Manufacture, Treatment Of Glass Fibers (AREA)
  • Tunnel Furnaces (AREA)

Abstract

Un récipient (1) d'échange de chaleur rempli de préférence d'eau, d'une installation de chauffage central ou individuel, est combiné avec un foyer muni d'une chambre de combustion (5) et utilisé pour la combustion pulsée de combustibles coulants, en particulier liquides. Ce foyer est monté sur une plaque de support fermant une ouverture du récipient (1). L'alimentation en air se fait de façon discontinue à travers des soupapes (30) et le combustible est injecté de façon continue et sous pression dans une chambre de précombustion (10) au moyen d'une buse (29) pouvant être déplacée axialement de façon que la pression d'injection et la position de la buse d'injection (29) constituent des variables essentielles. Un élément de turbulence est disposé dans la chambre de précombustion (10) près du fond de la chambre. Son ouverture est réglable et il sert à faire tourbillonner le mélange d'air combustible, ce qui donne une variable à régler supplémentaire. De préférence, la chambre de combustion (5) est pourvue de doubles parois, les doubles parois cylindriques renfermant un espace étroit permettant le transfert dechaleur et les parois du fond double étant séparées par un espace large isolant.
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 true EP0227699A1 (fr) 1987-07-08
EP0227699B1 EP0227699B1 (fr) 1989-01-04

Family

ID=3520111

Family Applications (2)

Application Number Title Priority Date Filing Date
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

Country Status (5)

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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Also Published As

Publication number Publication date
EP0307538A3 (fr) 1989-05-10
EP0227699B1 (fr) 1989-01-04
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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